US3873247A - Rotary piston machines - Google Patents

Rotary piston machines Download PDF

Info

Publication number
US3873247A
US3873247A US406307A US40630773A US3873247A US 3873247 A US3873247 A US 3873247A US 406307 A US406307 A US 406307A US 40630773 A US40630773 A US 40630773A US 3873247 A US3873247 A US 3873247A
Authority
US
United States
Prior art keywords
blades
shaft
quasi
machine
blade
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
US406307A
Other languages
English (en)
Inventor
Jean Boes
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
Application granted granted Critical
Publication of US3873247A publication Critical patent/US3873247A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01C1/063—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 with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/077—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 with coaxially-mounted members having continuously-changing circumferential spacing between them having toothed-gearing type drive

Definitions

  • Each flange is also provided with an opening in communica' tion with the hollow interior of the blade on which it is fixed.
  • the relative angular position of the blades on one shaft with respect to the blades on the other shaft is determined'by meshing quasi-elliptical gear wheel in cooperation with a differential gear which is provided for reducing the forces of inertia for given angular velocities.
  • the differential gear includes a differential wheel mounted for rotation with each of the shafts, star pinions,- and gear wheels for mounting the star pinions which transmit power between the machine and means external to the machine and having relatively slow speed variations.
  • the present invention relates to rotary piston machines.
  • Central axis rotary piston machines essentially comprise two concentric shafts mounted for rotation about the same axis, each shaft carrying a series of blades and rotated in the same direction at variable relative speeds which varies the angle between a blade carried on one shaft and a blade carried on the other shaft.
  • the blades are movable inside the same housing of revolution about the common axis of rotation and define chambers whose volumes vary as a function of the angle between the blades on the respective shafts. These variations in volume of the chambers are used to effect the induction or admission, compression, power and exhaust phases of the operating cycle which is common, namely, in internal combustion engines.
  • the thickness and shape of the blades vary according the proposed arrangement. A suitable choice of the variables enables the opening and closing of the admission (intake) port and the exhaust port formed in the wall of the housing at appropriate moments.
  • the sought-after result is obtained by alternately locking and unlocking each of the shafts against rotation:
  • the angular velocity of one of the shafts varies as follows:
  • the angular velocities of the shafts vary within relatively narrow ranges and never pass through a zero value
  • the velocities of a first shaft of such machines can be schematically described as follows:
  • quasielliptical gearing means gearing comprising two identical cooperating toothed wheels of generally elliptical shape, e.g., slightly modified along the major curved sides thereof. It is known that two identical ellipses each turning about the intersection of its major and minor axes or center forms rolling curves, i.e., they can turn on one another without sliding, the point of contact remaining fixed along the line joining the two centres of rotation. It is also known that the same ellipses, each turning about its center, are not rolling curves, however, the correctionrequired so that they are rolling curves is relatively small, if their elongation is moderate.
  • FIGS. 1 and 2 show theoretical diagrams of pseudoelliptical gearing
  • FIG. 3 shows a cross-sectional view of a motor according to a preferred embodiment of the invention
  • FIG. 4- shows an end view of the motor illustrated infigure 3
  • FIG. 5 is a simplified end view on a small scale of a gear train comprising quasi-elliptical gear wheels
  • FIG. 6 shows a position diagram indicating the various phases of operation of the motor
  • FIG. 7 shows a diagram illustrating the position of the sparking device, the admission means and the exhaust means for the same motor.
  • the construction of the blades is preferably as follows:
  • a pair of blades are arranged diametrically each other on each shaft.
  • the blades are sector-shaped, the angle between their radial sides being defined so that the ratio of the maximum and minimum volumes of the chambers defined by two consecutive blades a first blade on one shaft and a consecutive blade on the other shaft is equal to the desired degree of compression.
  • the angle 8 included between the sides of the blade and the angles a and B define the extreme relative positions of the center lines of the blades and the degree of compresslon t:
  • the maximum difference between the angular velocities of the quasi-ellipses is reached when an end of the major axis is in contact with an end of the minor axis of the other quasi-ellipse (FIG. 1), the ratio of the angular velocities is therefore: 11/); or b/a.
  • the angular velocity of the other quasiellipse varies between V X a/b and V X b/a.
  • the angular velocity varies between 2V and 5V.
  • An aim of the invention is to overcome this problem.
  • An aspect of the invention consists in coupling with a pair of quasi-elliptical gear wheels a conventional type of differential gear, each one of the shafts being fixed to one of the bevel or differential wheels.
  • this angular velocity V is the arithmetic mean of the angular velocities V and V of the bevel or differential wheels.
  • V V 2 V from which we find that V, varies between n l )V/2 and (n l) V/2n while V varies between (n l)V/2n and (n 1) W2, that is, with a ratio of maximum to minimum angular velocities of n and not H as in the case in which a differential gear is not used, and a ratio of n for the forces of inertia instead of n*.
  • FIG. 3 shows a gear train embodiment in which a quasi-elliptical gear wheel is fixed to one of the coaxial shafts and a circular gear wheel is fixed to the other coaxial shaft.
  • a second quasielliptical gear wheel and a second circular gear wheel identical to the first circular gear wheel are keyed to an auxiliary shaft.
  • the differential gear is arranged in a continuation of the coaxial shafts.
  • the gear train may have two or more quasielliptical gear wheels instead of one quasi-elliptical gear wheel and one circular gear wheel provided that the angular variations and the variations in the angular velocity-of the blades remain the same. In this case less elongated quasi-elliptical gear wheels are used which results in reduced machining costs.
  • differential gear may be positioned outside the axis of the blades for space considerations.
  • this reduction of the forces of inertia is used in part to improve the heat flow patterns in the blades.
  • the housing is divided into three sections: two lateral rotary flanges and a fixed enclosure.
  • a flange is fixed to each of two diametrically opposed blades fixed to the same shaft.
  • the flanges are formed as flat discs and the enclosure is formed as a cylinder, however, this arrangement is not obligatory.
  • The-blades thus transfer heat to the flanges, the external face of the flanges may be cooled by suitable known cooling means. It is also possible to provide a hollow blade communicating with the exterior through one or more apertures passing through the flange.
  • coolant may thus introduced inside the blade itself.
  • advantage of the particular construction of the housing is taken to provide slide valves in front of the admission and exhaust ports. It is thus possible to adapt simply, even during operation, the dimensions of the ports to the operating characteristics, e.g., rotational velocity, nature of fuel, temperature. In this case, the pollution caused by the exhaust fumes of the engine may be very substantially reduced by using the socalled Stratification technique.
  • FIGS. 3 and 4 illustrate a practical embodiment of the motor according to the invention.
  • An inner shaft 1 extends through the entire apparatus and is supported by bearings 31 and 32 at its respective ends.
  • An outer shaft 2 is supported by a bearing 33 and is coaxial with the inner shaft 1.
  • Blades 3 and 4 are fixed to the flanges 7 mounted for rotation with the inner shaft 1, and blades 5 and 6 are fixed to another flange 8 mounted for rotation with the outer shaft 2.
  • the blades 3-6 are annular sector-shaped with 53 angle 8 between the radial side thereof.
  • the blades are hollow and do not have a wall on the side facing the flange on which they are fixed.
  • the flanges have a corresponding opening 9,9' of substantially the same dimension as the interior of the blade thereby giving ample access to the ambient air ensuring the cooling of the blades.
  • the cylindrical enclosure closes the housing and is provided with a peripheral groove 11 for facilitating its cooling.
  • the sparking plug and the admission and exhaust ports (not shown in the drawings) are arranged in the enclosure.
  • a quasi-elliptical gear 12 is keyed to the outer shaft 2 and drives a similar quasi-elliptical gear 13 keyed to an auxiliary shaft 14 (FIG. 5).
  • a circular gear wheel 15 is keyed to the inner shaft 1 and'drives an identical gear wheel 16 keyed to the auxiliary shaft 14.
  • a differential or bevel wheel 17 is fixed to the outer shaft 2 for movement with the quasi-elliptical gear wheel 12
  • the other differential or bevel wheel 18 is fixed to the inner shaft 1 for movement with the circular gear wheel 15.
  • the gear wheel 19 carrying the star pinion 19 freely swivels on the inner shaft 1 and drives the output shaft.
  • the quasi-elliptical gear wheels 12 and 13 are sized so as to give a maximum angular separation 01 of l and a minimum angular separation B of 60 between the centre lines of consecutive blades on alternate shaft which approximately correspond to a value of 2 for the ratio a/b of the lengths of the axes of the ellipses.
  • POWER EXH
  • ADM ADM-Coupled Device
  • the sparking plugs B are arranged at 2630, the admission ports A are arranged between l5330 and 20630 and the exhaust ports E are arranged between.
  • a gear train including an auxiliary shaft, two quasielliptical gear wheels in engagement with each other and carried by said auxiliary shaft and one of said coaxial shafts, other gear wheels in engagement with each other and carried by said auxiliary shaft and the other of said coaxial shafts, and a differential gear including two differential wheels each mounted to be driven by one of said coaxial shafts, a start pinion in meshing engagement with the differential wheels and a gear wheel carrying the star pinion for transmitting power between the machine and means external to the machine and having relatively slow speed variations.
  • a machine according to claim 1, wherein the housing comprises a fixed enclosure and flanges mounted for rotation with the blades, the flanges having means for transferring heat from the blades to the surroundings during operation of the machine.
  • each blade is hollow, and said means for transferring heat includes its respective flange being provided with aperture means for enabling the circulation of a coolant between the hollowed interior of said one blade and the surroundings of the housing.
  • each series of blades comprises a pair of diametrically opposed sector-shaped blades, an angle 8 included between the radial sides of the sector-shapped blade being defined as a function of the angles or and B which define the extreme limit positions of the centre line of the blades and the degree of compression according to the formula:
  • a machine according to claim 1 wherein said differential gear is mounted between said quasi-elliptical gear wheel carried by said one coaxial shaft and that one of said other gear wheels carried by said other coaxial shaft.
  • a machine according to claim 1 wherein said differential gear is mounted between said quasi-elliptical gear wheel carried by said one coaxial shaft and that one of said other gear wheels carried by said other coaxial shaft, and in surrounding relation with respect to said other coaxial shaft adjacent an end of said one coaxial shaft.
  • a machine wherein said quasi-elliptical gear wheels are identical, and each quasi-elliptical gear wheel is modified along major POSITIONS OF VARIOUS POINTS STARTING FROM M 0 III IV AOB COD EOF GOH A B C D E F G H 2630 7 3330 8630 67 l5330 20630 7 2 l 330 26630 67 33330 POW ER EXH ADM COMP 8630 67 l5330 20630 7 2 1 330 26630 67 33330 2630 7 3330 EXH ADM COMP POWER 20630 7 2 l330 26630 67 33330 2630 7 3330 8630 67 l5330 ADM COMP POWER EXH 26630 67 33330 2630 7 3330 8630 67 l5330 206 30 7 2 l 330 COMP POWER EXH ADM 2630 7 3330 8630 67 l5330 7 2 1 330 2663O 67 tances from the centers 0 0 to a point of contact between said

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)
  • Rotary-Type Compressors (AREA)
  • Hydraulic Motors (AREA)
US406307A 1972-10-19 1973-10-15 Rotary piston machines Expired - Lifetime US3873247A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7237065A FR2204221A5 (ja) 1972-10-19 1972-10-19

Publications (1)

Publication Number Publication Date
US3873247A true US3873247A (en) 1975-03-25

Family

ID=9105896

Family Applications (1)

Application Number Title Priority Date Filing Date
US406307A Expired - Lifetime US3873247A (en) 1972-10-19 1973-10-15 Rotary piston machines

Country Status (6)

Country Link
US (1) US3873247A (ja)
JP (1) JPS5334641B2 (ja)
DE (2) DE2352231C3 (ja)
FR (1) FR2204221A5 (ja)
GB (1) GB1422678A (ja)
IT (1) IT994837B (ja)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3953157A (en) * 1975-05-28 1976-04-27 Huschang Sabet Rotary-piston internal-combustion engine with two output shafts
WO1999032760A1 (en) * 1997-12-22 1999-07-01 Esko Raikamo A power unit for use as a pressure-fluid-operated motor and/or a pressure fluid pump
US6158987A (en) * 1998-01-13 2000-12-12 Raikamo; Esko Power unit for use as a pressure-fluid operated motor and/or a pressure fluid pump
US20040187803A1 (en) * 2003-03-28 2004-09-30 Aron Regev Rotary vane motor
US20050016494A1 (en) * 2003-02-04 2005-01-27 Udy Joseph Dale 4-Cycle, rotary, electromagnetic, internal combustion engines
US20080276902A1 (en) * 2005-12-20 2008-11-13 Reinhard Manthey Rotary Piston Machine Comprising Two Piston Mounts Arranged on an Axle
CN101886572A (zh) * 2010-06-23 2010-11-17 袁锁林 行星式旋转内燃机
US20120080006A1 (en) * 2010-10-04 2012-04-05 Chun-Chiang Yeh Rotary modulation engine
CN106640367A (zh) * 2015-11-01 2017-05-10 蔡光源 一种具有弯筒或直筒形气缸的追逐转子型发动机结构
US11428156B2 (en) 2020-06-06 2022-08-30 Anatoli Stanetsky Rotary vane internal combustion engine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19753134A1 (de) * 1997-11-29 1999-06-10 Martin Sterk Kreiskolbenmotor
FR2835280B1 (fr) * 2002-01-29 2005-03-04 Pham Pascal Andre Georges Ha Moteur rotatif a combustion interne a deux palettes pilotees, et de construction bimodulaire

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1962408A (en) * 1931-11-07 1934-06-12 Powell Neal Rotary motor
US2342515A (en) * 1940-12-24 1944-02-22 Morgenstern Felix Internal combustion engine
US3294071A (en) * 1964-02-21 1966-12-27 Turco Jerome Internal combustion rotary piston engine
US3302625A (en) * 1964-05-15 1967-02-07 Cunningham Kelly Gore Engine
US3356079A (en) * 1966-11-29 1967-12-05 Virmel Corp Rotary internal combustion engine
US3398643A (en) * 1965-07-30 1968-08-27 Schudt Hans Rotary piston engine, pump or other machine
US3769946A (en) * 1969-07-14 1973-11-06 W Scherrer Rotary engines

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1962408A (en) * 1931-11-07 1934-06-12 Powell Neal Rotary motor
US2342515A (en) * 1940-12-24 1944-02-22 Morgenstern Felix Internal combustion engine
US3294071A (en) * 1964-02-21 1966-12-27 Turco Jerome Internal combustion rotary piston engine
US3302625A (en) * 1964-05-15 1967-02-07 Cunningham Kelly Gore Engine
US3398643A (en) * 1965-07-30 1968-08-27 Schudt Hans Rotary piston engine, pump or other machine
US3356079A (en) * 1966-11-29 1967-12-05 Virmel Corp Rotary internal combustion engine
US3769946A (en) * 1969-07-14 1973-11-06 W Scherrer Rotary engines

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3953157A (en) * 1975-05-28 1976-04-27 Huschang Sabet Rotary-piston internal-combustion engine with two output shafts
WO1999032760A1 (en) * 1997-12-22 1999-07-01 Esko Raikamo A power unit for use as a pressure-fluid-operated motor and/or a pressure fluid pump
US6158987A (en) * 1998-01-13 2000-12-12 Raikamo; Esko Power unit for use as a pressure-fluid operated motor and/or a pressure fluid pump
US6948473B2 (en) * 2003-02-04 2005-09-27 Joseph Dale Udy 4-cycle, rotary, electromagnetic, internal combustion engines
US20050016494A1 (en) * 2003-02-04 2005-01-27 Udy Joseph Dale 4-Cycle, rotary, electromagnetic, internal combustion engines
US20040187803A1 (en) * 2003-03-28 2004-09-30 Aron Regev Rotary vane motor
US6886527B2 (en) * 2003-03-28 2005-05-03 Rare Industries Inc. Rotary vane motor
US20080276902A1 (en) * 2005-12-20 2008-11-13 Reinhard Manthey Rotary Piston Machine Comprising Two Piston Mounts Arranged on an Axle
CN101886572A (zh) * 2010-06-23 2010-11-17 袁锁林 行星式旋转内燃机
CN101886572B (zh) * 2010-06-23 2013-04-10 袁锁林 行星式旋转内燃机
US20120080006A1 (en) * 2010-10-04 2012-04-05 Chun-Chiang Yeh Rotary modulation engine
CN106640367A (zh) * 2015-11-01 2017-05-10 蔡光源 一种具有弯筒或直筒形气缸的追逐转子型发动机结构
US11428156B2 (en) 2020-06-06 2022-08-30 Anatoli Stanetsky Rotary vane internal combustion engine

Also Published As

Publication number Publication date
DE2352231B2 (de) 1978-02-16
IT994837B (it) 1975-10-20
DE2352231A1 (de) 1974-05-02
JPS5334641B2 (ja) 1978-09-21
GB1422678A (en) 1976-01-28
DE2366073A1 (de) 1977-11-17
FR2204221A5 (ja) 1974-05-17
JPS4995204A (ja) 1974-09-10
DE2352231C3 (de) 1978-10-12

Similar Documents

Publication Publication Date Title
US3873247A (en) Rotary piston machines
US4047856A (en) Rotary steam engine
US3396632A (en) Volumetric maching suitable for operation as pump, engine, or motor pump
US4801255A (en) Internal axis single-rotation machine with intermeshing internal and external rotors
EP2233691B1 (en) Volume expansion rotary piston machine
US3215043A (en) Hydraulic torque motors
US3913408A (en) Apparatus for controlling epicyclic motion of a rotor in a rotary engine
EP1075595B1 (en) Improvements relating to rotary piston machines
US4010716A (en) Rotary engine
US3744940A (en) Rotary expansion engine of the wankel type
US2108385A (en) Rotary engine
US3207425A (en) Rolling body engine with multiple rotors
US2413589A (en) Rotary internal-combustion engine
US3955541A (en) Rotary internal combustion engine with uniformly rotating pistons cooperating with reaction elements having a varying speed of rotation
US1330629A (en) Internal-combustion engine
JPH05507536A (ja) ロータリピストン型内燃機関
US3364908A (en) Rotary cylinder swinging piston engine
US1946136A (en) Internal-combustion engine
US2211292A (en) Split cycle internal combustion engine
US3626911A (en) Rotary machines
US4373484A (en) Rotary piston mechanism
US2503894A (en) Valveless type rotary power unit
US3685928A (en) Rotary piston engine
KR100395080B1 (ko) 로터리내연엔진
US3994640A (en) Spherical rotary steam engine