EP0229766A1 - Rotary engine - Google Patents

Rotary engine

Info

Publication number
EP0229766A1
EP0229766A1 EP86901857A EP86901857A EP0229766A1 EP 0229766 A1 EP0229766 A1 EP 0229766A1 EP 86901857 A EP86901857 A EP 86901857A EP 86901857 A EP86901857 A EP 86901857A EP 0229766 A1 EP0229766 A1 EP 0229766A1
Authority
EP
European Patent Office
Prior art keywords
spindle
gear
rotor assembly
elliptical
shaft
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Withdrawn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
EP86901857A
Other languages
German (de)
French (fr)
Inventor
Giacomo Venturelli
Giuseppe Soave
Giuseppe Ruzzenenti
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
Publication of EP0229766A1 publication Critical patent/EP0229766A1/en
Withdrawn legal-status Critical Current

Links

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

  • This invention relates to a rotary engine for use in combination with drives arranged to convert input pulsating power into uniform rotary motion.
  • An object of the present invention is to provide a rotary engine which is highly effective to yield improved engine output.
  • a rotary engine comprising a casing, a first and a second rotor assembly, mounted for rotation in the casing, each rotor assembly comprising at least one radially extending sector or jaw and a spindle, a spindle of one rotor assembly being axially aligned with the spindle of the other rotor assembly, two gear drives and an output shaft, each gear drive comprising two elliptical gears and being arranged to operatively connect a respective spindle to the said output shaft, thereby causing speed differentials between said first and second rotor assemblies.
  • Figure 1 shows a diagrammatic side section view of an engine according to the invention
  • Figure 2 shows a diagrammatic front section view of the engine of Figure 1 showing the rotor arrangement during its exhaust and intake strokes;
  • Figure 3 is a diagrammatic section view similar to Figure 2 showing the rotor arrangement during the power and end-of-exhaust stroke;
  • Figure 4 is an exploded perspective diagrammatic view showing the two rotor assemblies
  • Figure 5 is a diagrammatic view similar to Figure 1, illustrating another embodiment of the invention
  • Figure 6 is a left side view of the device of Figure 5.
  • Figure 7 is a right side view of the device of Figure 5.
  • reference numeral 1 generally indicates an internal combustion engine which comprises a cylinder or casing 2, and a rotor mounted for rotation in the casing 2 and comprising twin rotor components indicated at 3 and 4, respectively, and arranged to cooperate with one another.
  • Each rotor component is rigid in rotation with a respective shaft 5, 10, each of which are operatively connected to a respective drive generally indicated at 7 including two elliptical gears meshing with, and in opposition to, one another.
  • the rotor component 3 comprises a central cylindrical holder 8, from which two jaws 9 and 9' diametrically opposite jaws or sectors 9 and 9' axially extend so as to project from the body 8.
  • the rotor component 4 is provided with a central cylindrical holder 10 similar complementary to the holder 8 and with jaws or sectors 11 and 11', also diametrically opposite to one another and axially extending with respect to the holder 10.
  • the two rotor components 3 and 4 are assembled in such a way that the shaft 5 fits inside the hollow or tubular shaft or holder 10, with the overhanging portions of the jaws 9-9' and 11-11' matching with each other so that their respective holders 10 and 8 abut one against the other, thus forming two coaxial rotor assemblies.
  • the rotor assembly is accommodated free to rotate inside the cylinder or casing 2 and is also connected directly to the drives 7 through the shafts 5 and 10.
  • the rotor assembly delimits a series of chambers inside the casing 2.
  • Such chambers are inner spaces in which the cycle strokes of an end thermal gasoline engine, e.g. a four-stroke cycle engine, as shown in Figures 2 and 3, can occur.
  • the jaws or sectors 9-9' and 11-11' are arranged one relatively to the other as shown in Figure 3.
  • Fuel combustion causes the jaw 9 to move forward (clockwise direction) at an accelerated rate up to the end of the exhaust stroke.
  • the jaw 9' integral with it is subjected to the same acceleration throughout the compression stroke.
  • the assembly 4 experiences deceleration while the assembly 3 is being accelerated, whereas when the assembly 4 going through its power stroke, it will be accelerated and the assembly 3 decelerated accordingly.
  • This differential in the speed of rotation between assemblies 3 and 4 is due to the arrangement of the elliptical gear drive 7 which makes it possible, to obtain power, exhaust, intake, and compression chambers varying their capacity according to a specifio sequence which depends, among others, on the degree of eccentricity of the elliptical gears.
  • the hollow shaft 10 projects from the cylinder or casing 2 and is designed to drive a first gear train constituted by a circular gear wheel 14 keyed to the hollow shaft 10, a pinion gear 15 meshing with the gear wheel 14 and being journalled on a rotatable intermediate or auxiliary shaft 16 having its axis x-x parallel to the axis y-y of the shafts or spindles 5 and 10, a first elliptical gear 17 mounted for rotation on the shaft 16 and rigid in rotation with the pinion gear 15, and a second elliptical gear 18 keyed to an output shaft 19 having an axis z-z parallel to the axes x-x and y-y.
  • the spindle 5, which extends throughout the hollow shaft 10, projects from both the cylinder 2 and the shaft 10, and is arranged to drive a second gear train. If desired, the spindle
  • the second gear train comprises a circular gear wheel 20 rigid in rotation with the spindle 5, a pinion gear 21 meshing with the gear wheel 20 and being keyed to the intermediate or auxiliary rotating shaft 16, an elliptical gear 22 also keyed to the shaft 16, and a second elliptical gear 23 keyed to the shaft 19.
  • the elliptical gears 17 and 18 of the first gear train are identical with, and outphased by 180°, from the corresponding elliptical gears 22 and 23 of the second gear train, when aligned along their major axes.
  • the shaft 16 could also be a shaft 20 (i.e. a non-rotating shaft), in which case the gears 15, 17 and 21, 22 would be mounted for rotation on it, the gear 15 being rigid in rotation with the gear 17 and the 21 with the 22.
  • a drive 13 which has 1:2 drive ratio between the spur gears 14,15 and 20,21, for each full revolution through 360° of the output shaft 19, there occur a number of relative accelerations and decelerations of the rotors 3 and 4, which result in a corresponding number of volumetric changes between the jaws or sectors 9,9' and 11,11', thereby providing two complete intake, compression, power, and exhaust stroke cycles typical of a four-stroke cycle engine.
  • the number of engine cycles may be even higher than two, namely four, six, etc.
  • the rotary engine may be used as a compressor or a pump, since it effects one acceleration stroke and one deceleration stroke for each revolution. In other words, it can provide two instead of four strokes.
  • the shaft 19 would be the output shaft and the spindles 5 and 10 driven shaft, each designed to drive a rotor advantageously provided with one sector or jaw, 9 or 11.
  • the flare angles of the jaws 9,9' and 11,11' of the rotor assemblies are correlated directly to the degree of eccentricity of the elliptical gears, the eccentricity being in turn also related to the maximum torque of the engine 1.
  • each complete revolution through 360o results in the rotors (spindles 5 and 10) undergoing alternately four acceleration and four deceleration strokes, which results in a virtually continuous and uniform motion of the shaft 19.
  • the angles ⁇ and ⁇ cannot have the same value, because they would then have zero eccentricity, and accordingly, zero acceleration and deceleration (no relative out-phasing).
  • Figures 5-7 also show a specific peculiar design of the hollow spindle 10 which extends to a point close to the gear wheel 20, where it carries an end bush or bearing 25 for the spindle 5.
  • the jaws or segments 9,9' and 11,11' could have an annular or toric configuration, and fit in respective seats formed in the casing 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Gear Transmission (AREA)

Abstract

Un moteur rotatif comprend un carter, un agencement à deux rotors montés de façon rotative dans le carter et ayant deux mandrins co-axiaux qui font saillie sur le carter, une transmission à engrenages et un arbre secondaire. La transmission à engrenages comprend deux trains d'engrenages elliptiques dont chacun est agencé pour connecter de manière fonctionnelle un mandrin respectif à l'arbre secondaire.A rotary engine comprises a housing, a two-rotor arrangement rotatably mounted in the housing and having two co-axial chucks which project from the housing, a gear transmission and a secondary shaft. The gear transmission includes two elliptical gear trains each of which is arranged to operably connect a respective chuck to the secondary shaft.

Description

"ROTARY ENGINE" Technical Field
This invention relates to a rotary engine for use in combination with drives arranged to convert input pulsating power into uniform rotary motion.
An object of the present invention is to provide a rotary engine which is highly effective to yield improved engine output.
According to the invention there is provided a rotary engine comprising a casing, a first and a second rotor assembly, mounted for rotation in the casing, each rotor assembly comprising at least one radially extending sector or jaw and a spindle, a spindle of one rotor assembly being axially aligned with the spindle of the other rotor assembly, two gear drives and an output shaft, each gear drive comprising two elliptical gears and being arranged to operatively connect a respective spindle to the said output shaft, thereby causing speed differentials between said first and second rotor assemblies.
BRIEF DESCRIPTION OF THE DRAWINGS The invention will be more clearly understood from the following description of a few specific embodiments thereof, given herein by way of examples with reference to the accompanying drawings, in which:
Figure 1 shows a diagrammatic side section view of an engine according to the invention; Figure 2 shows a diagrammatic front section view of the engine of Figure 1 showing the rotor arrangement during its exhaust and intake strokes;
Figure 3 is a diagrammatic section view similar to Figure 2 showing the rotor arrangement during the power and end-of-exhaust stroke;
Figure 4 is an exploded perspective diagrammatic view showing the two rotor assemblies; Figure 5 is a diagrammatic view similar to Figure 1, illustrating another embodiment of the invention;
Figure 6 is a left side view of the device of Figure 5; and
Figure 7 is a right side view of the device of Figure 5.
WAYS OF CARRYING OUT THE INVENTION
With reference to the above figures, reference numeral 1 generally indicates an internal combustion engine which comprises a cylinder or casing 2, and a rotor mounted for rotation in the casing 2 and comprising twin rotor components indicated at 3 and 4, respectively, and arranged to cooperate with one another. Each rotor component is rigid in rotation with a respective shaft 5, 10, each of which are operatively connected to a respective drive generally indicated at 7 including two elliptical gears meshing with, and in opposition to, one another.
The rotor component 3 comprises a central cylindrical holder 8, from which two jaws 9 and 9' diametrically opposite jaws or sectors 9 and 9' axially extend so as to project from the body 8. Likewise, the rotor component 4 is provided with a central cylindrical holder 10 similar complementary to the holder 8 and with jaws or sectors 11 and 11', also diametrically opposite to one another and axially extending with respect to the holder 10.
The two rotor components 3 and 4 are assembled in such a way that the shaft 5 fits inside the hollow or tubular shaft or holder 10, with the overhanging portions of the jaws 9-9' and 11-11' matching with each other so that their respective holders 10 and 8 abut one against the other, thus forming two coaxial rotor assemblies.
The rotor assembly is accommodated free to rotate inside the cylinder or casing 2 and is also connected directly to the drives 7 through the shafts 5 and 10.
In the assembled condition, the rotor assembly delimits a series of chambers inside the casing 2. Such chambers are inner spaces in which the cycle strokes of an end thermal gasoline engine, e.g. a four-stroke cycle engine, as shown in Figures 2 and 3, can occur.
During a power stroke, the jaws or sectors 9-9' and 11-11' are arranged one relatively to the other as shown in Figure 3.
Fuel combustion causes the jaw 9 to move forward (clockwise direction) at an accelerated rate up to the end of the exhaust stroke. At the same time, the jaw 9' integral with it is subjected to the same acceleration throughout the compression stroke. Similarly, the assembly 4 experiences deceleration while the assembly 3 is being accelerated, whereas when the assembly 4 going through its power stroke, it will be accelerated and the assembly 3 decelerated accordingly. This differential in the speed of rotation between assemblies 3 and 4, is due to the arrangement of the elliptical gear drive 7 which makes it possible, to obtain power, exhaust, intake, and compression chambers varying their capacity according to a specifio sequence which depends, among others, on the degree of eccentricity of the elliptical gears. For each complete revolution of each rotor assembly, 3 and 4, four strokes occur i.e. intake, compression, power, and exhaust strokes, and one spark plug 12 is provided to prime fuel combustion. The embodiment shown in Figures 5,6 and 7 (where the same or similar parts to those of Figures 1 to
4 are identified with the same reference numerals) comprises a drive 13 comprising two identical gear trains. More specifically, the hollow shaft 10 projects from the cylinder or casing 2 and is designed to drive a first gear train constituted by a circular gear wheel 14 keyed to the hollow shaft 10, a pinion gear 15 meshing with the gear wheel 14 and being journalled on a rotatable intermediate or auxiliary shaft 16 having its axis x-x parallel to the axis y-y of the shafts or spindles 5 and 10, a first elliptical gear 17 mounted for rotation on the shaft 16 and rigid in rotation with the pinion gear 15, and a second elliptical gear 18 keyed to an output shaft 19 having an axis z-z parallel to the axes x-x and y-y. The spindle 5, which extends throughout the hollow shaft 10, projects from both the cylinder 2 and the shaft 10, and is arranged to drive a second gear train. If desired, the spindle
5 could project from the cylinder 2 at Its end far from the hollow shaft 10, while being in alignment thereto. In that case, the engine 1 would be located between the two gear trains.
The second gear train comprises a circular gear wheel 20 rigid in rotation with the spindle 5, a pinion gear 21 meshing with the gear wheel 20 and being keyed to the intermediate or auxiliary rotating shaft 16, an elliptical gear 22 also keyed to the shaft 16, and a second elliptical gear 23 keyed to the shaft 19. The elliptical gears 17 and 18 of the first gear train are identical with, and outphased by 180°, from the corresponding elliptical gears 22 and 23 of the second gear train, when aligned along their major axes.
The shaft 16 could also be a shaft 20 (i.e. a non-rotating shaft), in which case the gears 15, 17 and 21, 22 would be mounted for rotation on it, the gear 15 being rigid in rotation with the gear 17 and the 21 with the 22. With such a drive 13 which has 1:2 drive ratio between the spur gears 14,15 and 20,21, for each full revolution through 360° of the output shaft 19, there occur a number of relative accelerations and decelerations of the rotors 3 and 4, which result in a corresponding number of volumetric changes between the jaws or sectors 9,9' and 11,11', thereby providing two complete intake, compression, power, and exhaust stroke cycles typical of a four-stroke cycle engine. The number of engine cycles may be even higher than two, namely four, six, etc. (but in all cases an even number), if provided that drive connection between the spindles 5 and 10 and the elliptical gearings of course through two pairs of circular gears 14,15 and 20,21 having respective 1:4, 1:6, etc. drive ratios, and if the number of the rotor jaws or sectors 9,9' and 11,11' is correspondingly increased, e.g. 4,6, etc. By omitting the two pairs of spur gears, as in the embodiment of Figure 1, the rotary engine may be used as a compressor or a pump, since it effects one acceleration stroke and one deceleration stroke for each revolution. In other words, it can provide two instead of four strokes. In that case, the shaft 19 would be the output shaft and the spindles 5 and 10 driven shaft, each designed to drive a rotor advantageously provided with one sector or jaw, 9 or 11. The flare angles of the jaws 9,9' and 11,11' of the rotor assemblies are correlated directly to the degree of eccentricity of the elliptical gears, the eccentricity being in turn also related to the maximum torque of the engine 1. Thus, as an example, if α is the inner angle between two straight lines joining the centre of rotation of each elliptical gear to the points of intersection of its minor axis with its respective pitch ellipse, and β is the outer angle between those same lines (Figure 6), then the corresponding flare angles of the sectors or jaws 9,9' and 11,11' is α/2 and β/2 , respectively, if the drive ratio is 1:2, or α/4 and β/4 if that ratio is 1 :4, and so on.
At a 1:4 drive ratio, each complete revolution through 360º results in the rotors (spindles 5 and 10) undergoing alternately four acceleration and four deceleration strokes, which results in a virtually continuous and uniform motion of the shaft 19. The angles α and β cannot have the same value, because they would then have zero eccentricity, and accordingly, zero acceleration and deceleration (no relative out-phasing).
Figures 5-7 also show a specific peculiar design of the hollow spindle 10 which extends to a point close to the gear wheel 20, where it carries an end bush or bearing 25 for the spindle 5.
If desired, the jaws or segments 9,9' and 11,11' could have an annular or toric configuration, and fit in respective seats formed in the casing 2.

Claims

CLAIMS 1. A rotary engine comprising a casing, a first and a second rotor assembly, mounted for rotation in the casing, each rotor assembly comprising at least one radially extending sector or jaw and a spindle, a spindle of one rotor assembly being axially aligned with the spindle of the other rotor assembly, two gear drives and an output shaft, each gear drive comprising two elliptical gears and being arranged to operatively connect a respective spindle to the said output shaft thereby causing speed differentials between said first and second rotor assemblies. 2. A rotary engine as claimed in Claim 1, wherein the spindle of one rotor assembly is hollow and rotatably receives in it the spindle of the other rotor assembly. 3. A rotary engine as claimed in Claim 1 or 2, wherein each gear drive comprises an intermediate or auxiliary shaft extending parallel to the spindle and the output shaft, a pair of meshing spur gears for transmitting the motion between the spindles and the auxiliary shaft, and a pair of elliptical pair for transmitting the motion between the auxiliary shaft and the said output shaft, one elliptical gear being rigid in rotation with a βpαr gear, whereas the other elliptical gear is keyed to the said output shaft.
EP86901857A 1985-03-19 1986-03-10 Rotary engine Withdrawn EP0229766A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT8491685 1985-03-19
IT8584916A IT8584916A0 (en) 1985-03-19 1985-03-19 MOTOR-DEVICE, PREFERABLY APPLICABLE ON KINEMATICS SUITABLE FOR CONVERTING THE RECEIVED IMPULSE INTO UNIFORM ROTARY MOTION.

Publications (1)

Publication Number Publication Date
EP0229766A1 true EP0229766A1 (en) 1987-07-29

Family

ID=11325701

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86901857A Withdrawn EP0229766A1 (en) 1985-03-19 1986-03-10 Rotary engine

Country Status (6)

Country Link
EP (1) EP0229766A1 (en)
CN (1) CN86101810A (en)
AU (1) AU5622186A (en)
ES (1) ES8701897A1 (en)
IT (1) IT8584916A0 (en)
WO (1) WO1986005548A1 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1285896B1 (en) * 1996-02-14 1998-06-26 Roberto Manzini PUMP/COMPRESSOR/DEPRESSOR WITH TWO RIGID BLADES FIXED ON THEIR RESPECTIVE COAXIAL HUBS ROTATING AT VARIABLE SPEED INSIDE A
CN1102198C (en) * 1997-04-18 2003-02-26 李宏舟 Three-chamber dual rotors I. C. engine
CN1102199C (en) * 1998-05-28 2003-02-26 聂再安 Differential rotary piston engine
GB2384028A (en) * 2002-01-09 2003-07-16 Chahe Kaloustian Rotary piston internal combustion engine
US6886527B2 (en) * 2003-03-28 2005-05-03 Rare Industries Inc. Rotary vane motor
CN100458118C (en) * 2003-03-29 2009-02-04 孟良吉 Interactive speed variable double rotor engine
WO2011106989A1 (en) * 2010-03-03 2011-09-09 Duan Fangquan Dual-rotating four-circulating piston-type double-shaft internal combustion engine, pressure fluid driving machine and pump
CN102297018B (en) * 2011-07-24 2013-05-22 王震 Rotary engine
NO336578B1 (en) * 2013-01-21 2015-09-28 Otechos As Device by displacement type machine
CN103508221B (en) * 2013-09-25 2015-10-07 马钢(集团)控股有限公司 The defining method of a kind of pendulum-type leather belt material distributing device and elliptic gear case gear size thereof
CN106640367A (en) * 2015-11-01 2017-05-10 蔡光源 Rotor-following type engine structure with curved or straight cylindrical cylinders

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1068170A (en) * 1963-01-22 1967-05-10 Aero Commerce G M B H Rotary piston machines
US3398643A (en) * 1965-07-30 1968-08-27 Schudt Hans Rotary piston engine, pump or other machine
FR1585421A (en) * 1968-07-11 1970-01-23
ZA776719B (en) * 1977-11-10 1979-04-25 Griffenthal Pty Ltd Rotary engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8605548A1 *

Also Published As

Publication number Publication date
AU5622186A (en) 1986-10-13
CN86101810A (en) 1986-10-01
ES553621A0 (en) 1986-12-01
WO1986005548A1 (en) 1986-09-25
ES8701897A1 (en) 1986-12-01
IT8584916A0 (en) 1985-03-19

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