US1676211A - Transmission for rotary engines - Google Patents

Transmission for rotary engines Download PDF

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Publication number
US1676211A
US1676211A US643095A US64309523A US1676211A US 1676211 A US1676211 A US 1676211A US 643095 A US643095 A US 643095A US 64309523 A US64309523 A US 64309523A US 1676211 A US1676211 A US 1676211A
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United States
Prior art keywords
piston
crank
pistons
shafts
shaft
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Expired - Lifetime
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US643095A
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Frank A Bullington
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BULLINGTON MOTORS
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BULLINGTON MOTORS
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Priority to US643095A priority Critical patent/US1676211A/en
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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
    • 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
    • F01C1/07—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 crankshaft-and-connecting-rod type drive

Definitions

  • This invention relates to prime movers for generating power and particularly to a motor in which expansible motive fluid is employed to impart motion to pistons which 6 rotate about a common axis.
  • the invention is shown as applied to a gas engine in which the pistons are arranged in pairs, the pistons of each pair being rigidly connected to a rotor at diametrically oppositely located points so that a movement of a piston of one pair will induce a corresponding movement of the other piston in that pair.
  • the rotors carrying the pairs of pistons are so controlled that first one set of pistons and then the other becomes the accelerated pistons and vice versa in alternate relation throughout the repeated cycles of the motor.
  • Fig. 1 is a sectional view taken through the cylinder of the engine on the line 11 of Fig. 3 and a section through the crank case on the line 1 -1 of Fig. 3.
  • Fig. 2 is a detail perspective view of the 1923. Serial No. 643,095.
  • crank shaft carrier and power delivering member crank shaft carrier and power delivering member.
  • Fig. 3 is a sectional view on the line 3-3 of Fig. 1. a
  • Fig. 4 is a diagrammatic view of the pistons and linkage therefor, showing the dead center position of the parts with pistons A and B ready to receive the force of the explosion of the charge.
  • Fig. 5 is a similar view showing the pis- 00 tons A and B after they have moved their full working strokes with piston B now the acceleration piston in position to co-operate with piston A to complete another working stroke.
  • the stator is shown. as consisting of two members 1 and 2, which may be fastened together by suitable means; for example, bolts 3, to provide a circumferential cylinder or piston chamber 4.
  • the member 2 has 10 an extension or hub portion 5 projecting from the wall 6 thereof, the hub portion 5 carrying part of the piston-controlling linkage as will be apparent hereinafter.
  • crank case 7 76 Fastened to the wall 6 is a crank case 7 76 having a hub or bearing portion 8 for the power transmitting shaft 9.
  • the member 1 has a hub or bearing portion 10.
  • the hub portions 5 and 10 are connected to the cylinder portions of the webs 11 and 12 and to- 30 gether they form a rotor chamber 13 in which are located the rotors 14 and 15.
  • the rotor 14 is fixed on the shaft 16, one end of which is mounted in the hub or bearing 10, the other end being mounted in the bearing recess 17 in the crank carrier 18 and concentric with the shaft 9.
  • the rotor 15 carries a hub portion 19 sleeved on the shaft 16.
  • the hub portion 19 is really a hollow shaft which extends through the hub portion 5 to carry one of the piston arms, as
  • the crank carrier member '18 includes an end plate in which is located the recess 17 and it has inwardly extending webs or spacing walls 20 and 21 provided with outstand- 1w ing flanges 22 and 23 which may be fastened to the end plate 24 by suitable fastemng devices assing through the openings 25 in the end p ate 24 and through the openings 26 in the respective flanges 22 and 23.
  • the end plate 24 has a bearing collar or hub 27 which is mounted on the hub extension 5 so that when the members 18 and 24 are secured together, the crank carrier is supported by the shaft 9 and by the hub 5.
  • the plate 24 has diametrically oppositely 10 cated crank bearings 28 and 29 which, when the members 18 and 24 are secured together, align with complementary bearings 30 and 30 in the member 18.
  • the bearings 28 and 30 support a one-pin crank shaft 31 and the bearings 29 and 30' support a similar crank shaft 32.
  • On the inner ends of the respective crank shafts 31 and 32 are pinion gears 33 and 34 which mesh with a. gear 35 fixed to the hub portion 5; that is, the gears 33 and 34 planet-ate about the axis of a gear 35.
  • crank pins 38 and 39 carry connecting rods 40 and 41, which are connected to the pins 42 and 43 of the piston arms 44 and ter-balance weights 46 and 47
  • the piston arms 44 and carry counter balance weights 48 and 49.
  • the piston arm 44 1s rigidly connected to the shaft 16 and the piston arm 45 is rigidly connected to the hollow shaft 19. Therefore, it will be apparent that when the pistons are in the position shown in Fig. 4 and an explosion takes place between pistons A and B, the piston A will be the accelerated piston and the piston B will be the retarded piston, moving in the direction of the arrow.
  • the piston movement will be such that the parts will assume the position shown in Fig. 5 at the end of the power stroke of the pistons A and B, at which time the piston B will be in position to become the accelerated piston and the piston A, a complementary to the piston A, will be the retarded piston.
  • the piston A will then move over to the position occupied by the piston B in Fig. 5 and piston B will assume the position occupied by piston A in Fig. 5.
  • this will result in moving piston A to the position occupied by piston B in Fig. 5 and the linkage mechanism will change from the position shown in Fig. 5 to the positon shown in Fig. 4 due to the fact that the crank pins are 180 degrees apart but the linkage for shafts 16 and 19 are in transposed relation.
  • connecting rods 40 and 41 will maintain parallelismat any period of the operating mechanism during a complete cycle to asslst in maintaining .with the piston crank pins so that parallelism between the connecting rods40 and 41 will be maintained throughout the operating cycle of the engine.
  • the piston arms are balanced and since there 1s a fixed gear on the cylinder end of the crank case about which the crank shafts'31 and 32 planetate due to the gears 33 and 34 and since the crank shafts 31 and 32 carry individual fly wheels 36 and 37, it will be ap arent that these, together with the crank s aft carrier mounted on the cylinder end of the crank case all assist and co-operate 1n producing a balanced linkage mechanism be tween the pistons and, the power delivery shaft and insure balanced uniform operation of the power elements during the working period of the motor. 45.
  • crank shafts 31 and 32 carry coun- By placing the separate fly wheels on the .separate crank shafts, I am enabled to maintain uniform operation of the pistons with relation to each other, to bring about uniform rotation of the crank shafts and as a result maintain uniform pressure contact.
  • a rotary combustion motor In a rotary combustion motor, a fixed annular cylinder casing, and a fixed crank case at one side of the cylinder in axial alignment with the cylinder, pairs of pistons in the cylinder rotatable about a common axis, the pistons of one pair opposed to those of the other pair, to form working chambers between them and having relative movement to compress fuel charges to combustible pressures, means for igniting the compressed charges, two piston shafts, one concentric with the other, piston arms carried by the piston shafts, oppositely disposed single pin crank shafts, one for each pair of pistons,-

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)

Description

July 3, 1928. 1,676,211
F. A. BULLINGTON I TRANSMISSION FOR ROTARY ENGINES Filed June 2, 1923 2 Sheets-Sheet l 50 IN VL'NTOR A TTORNE'Y July 3, 1928. 1,676,211
F. A. BULLINGTON TRANSMISSION FOR ROTARY ENGINES Filed June 2, 1925 2 Sheets-Sheet 2 1w VENTOR I ATTORNEY Patented July 3, 1928.
UNITED STATES PATENT OFFICE.
- FRANK A. IBIILLINGTON, OF KANSAS CITY, MISSOURI, ASSIGNOR TO BULIJINGTON MOTORS, OF KANSAS CITY, MISSOURI, A COMMON-LAW TRUST CONSISTING OF SOLOMON STODDARD, ERNEST E. HOWARD, AND FRANK A. BULLINGTON.
' TRANSMISSION FOR ROTARY ENGINES.
Application filed June 2,
This invention relates to prime movers for generating power and particularly to a motor in which expansible motive fluid is employed to impart motion to pistons which 6 rotate about a common axis.
The invention is shown as applied to a gas engine in which the pistons are arranged in pairs, the pistons of each pair being rigidly connected to a rotor at diametrically oppositely located points so that a movement of a piston of one pair will induce a corresponding movement of the other piston in that pair. The rotors carrying the pairs of pistons are so controlled that first one set of pistons and then the other becomes the accelerated pistons and vice versa in alternate relation throughout the repeated cycles of the motor.
Devices of the same generic principle as illustrated in the drawings have been provided heretofore but in so faras I am aware, they have proved unsatisfactory because the mechanism for controlling the pistons had certain inherent defects. One
of the primary causes of failure of this type of engine is, I believe due to the fact that a proper linkage or controlling mechanism has not been provided for connecting the rotors to the driven shaft or power shaft of the motor. In some of my previous applications, I have devised novel forms of connecting mechanism, the present invention being a later development of some of the generic conceptions indicated in such former application and particularly in Letters Patent No. 1,579,207 issued to me April 6, 1926, and the present invention relates to novel balanced linkage mechanism for connecting up the movable parts so as to provide balanced operation during the working period of the motor.
The specific adaptation of my invention will be referred to hereinafter, reference being had to the accompanying drawings, in
which:
Fig. 1 is a sectional view taken through the cylinder of the engine on the line 11 of Fig. 3 and a section through the crank case on the line 1 -1 of Fig. 3.
Fig. 2 is a detail perspective view of the 1923. Serial No. 643,095.
crank shaft carrier and power delivering member.
Fig. 3 is a sectional view on the line 3-3 of Fig. 1. a
Fig. 4 is a diagrammatic view of the pistons and linkage therefor, showing the dead center position of the parts with pistons A and B ready to receive the force of the explosion of the charge.
Fig. 5 is a similar view showing the pis- 00 tons A and B after they have moved their full working strokes with piston B now the acceleration piston in position to co-operate with piston A to complete another working stroke.
The stator is shown. as consisting of two members 1 and 2, which may be fastened together by suitable means; for example, bolts 3, to provide a circumferential cylinder or piston chamber 4. The member 2 has 10 an extension or hub portion 5 projecting from the wall 6 thereof, the hub portion 5 carrying part of the piston-controlling linkage as will be apparent hereinafter.
Fastened to the wall 6 is a crank case 7 76 having a hub or bearing portion 8 for the power transmitting shaft 9. The member 1 has a hub or bearing portion 10. The hub portions 5 and 10 are connected to the cylinder portions of the webs 11 and 12 and to- 30 gether they form a rotor chamber 13 in which are located the rotors 14 and 15.
The rotor 14 is fixed on the shaft 16, one end of which is mounted in the hub or bearing 10, the other end being mounted in the bearing recess 17 in the crank carrier 18 and concentric with the shaft 9. The rotor 15 carries a hub portion 19 sleeved on the shaft 16. The hub portion 19 is really a hollow shaft which extends through the hub portion 5 to carry one of the piston arms, as
will be explained hereinafter.
The method of packing thepistons, rotors and cylinder forms no part of the present invention so no reference will be made thereto.
The crank carrier member '18 includes an end plate in which is located the recess 17 and it has inwardly extending webs or spacing walls 20 and 21 provided with outstand- 1w ing flanges 22 and 23 which may be fastened to the end plate 24 by suitable fastemng devices assing through the openings 25 in the end p ate 24 and through the openings 26 in the respective flanges 22 and 23. The end plate 24 has a bearing collar or hub 27 which is mounted on the hub extension 5 so that when the members 18 and 24 are secured together, the crank carrier is supported by the shaft 9 and by the hub 5. The plate 24 has diametrically oppositely 10 cated crank bearings 28 and 29 which, when the members 18 and 24 are secured together, align with complementary bearings 30 and 30 in the member 18. The bearings 28 and 30 support a one-pin crank shaft 31 and the bearings 29 and 30' support a similar crank shaft 32. On the inner ends of the respective crank shafts 31 and 32 are pinion gears 33 and 34 which mesh with a. gear 35 fixed to the hub portion 5; that is, the gears 33 and 34 planet-ate about the axis of a gear 35. The outer ends of the cranks 31 and 32 - carry fly wheels 36 and 37.
The crank pins 38 and 39 carry connecting rods 40 and 41, which are connected to the pins 42 and 43 of the piston arms 44 and ter- balance weights 46 and 47 The piston arms 44 and carry counter balance weights 48 and 49. The piston arm 44 1s rigidly connected to the shaft 16 and the piston arm 45 is rigidly connected to the hollow shaft 19. Therefore, it will be apparent that when the pistons are in the position shown in Fig. 4 and an explosion takes place between pistons A and B, the piston A will be the accelerated piston and the piston B will be the retarded piston, moving in the direction of the arrow.
The piston movement will be such that the parts will assume the position shown in Fig. 5 at the end of the power stroke of the pistons A and B, at which time the piston B will be in position to become the accelerated piston and the piston A, a complementary to the piston A, will be the retarded piston. When the second explosion has taken place and the pistons B and A have the full power stroke, the piston A will then move over to the position occupied by the piston B in Fig. 5 and piston B will assume the position occupied by piston A in Fig. 5. Of course, this will result in moving piston A to the position occupied by piston B in Fig. 5 and the linkage mechanism will change from the position shown in Fig. 5 to the positon shown in Fig. 4 due to the fact that the crank pins are 180 degrees apart but the linkage for shafts 16 and 19 are in transposed relation.
It will be apparent that the connecting rods 40 and 41 will maintain parallelismat any period of the operating mechanism during a complete cycle to asslst in maintaining .with the piston crank pins so that parallelism between the connecting rods40 and 41 will be maintained throughout the operating cycle of the engine. Furthermore, the piston arms are balanced and since there 1s a fixed gear on the cylinder end of the crank case about which the crank shafts'31 and 32 planetate due to the gears 33 and 34 and since the crank shafts 31 and 32 carry individual fly wheels 36 and 37, it will be ap arent that these, together with the crank s aft carrier mounted on the cylinder end of the crank case all assist and co-operate 1n producing a balanced linkage mechanism be tween the pistons and, the power delivery shaft and insure balanced uniform operation of the power elements during the working period of the motor. 45. The crank shafts 31 and 32 carry coun- By placing the separate fly wheels on the .separate crank shafts, I am enabled to maintain uniform operation of the pistons with relation to each other, to bring about uniform rotation of the crank shafts and as a result maintain uniform pressure contact.
between the teeth of the pinions and the teeth of the fixed gear, thus insuring uniform rotation of the engine.
Balanced rotation of the engine is maintained by the dispositon of the crank shafts, counter Weights on the crank shafts, and counter weights on the piston arms providing a construction which insures balanced rotation of the assembly; but, of course, any suitable means can be provided for igniting the charge; for example, I have shown a spark plug 50, in Fig. 1.
What I claim and desire to secure by Letters-Patent is:
In a rotary combustion motor, a fixed annular cylinder casing, and a fixed crank case at one side of the cylinder in axial alignment with the cylinder, pairs of pistons in the cylinder rotatable about a common axis, the pistons of one pair opposed to those of the other pair, to form working chambers between them and having relative movement to compress fuel charges to combustible pressures, means for igniting the compressed charges, two piston shafts, one concentric with the other, piston arms carried by the piston shafts, oppositely disposed single pin crank shafts, one for each pair of pistons,-
ton shafts, connecting rods between the pisgreater distance from the axes of the piston ton arms and the crank pins, the crank pins shafts than the other, the connecting rods being so disposed that when they are on on dead center positions and parallel one to 10 dead center positions they are at equal anguthe other. 5 lar distances on one side of a plane passlng In testimony whereof I aflix my signature.
through the axes of the crank shafts and of the piston shafts, with one crank pin a FRANK A. BULLINGTON.
US643095A 1923-06-02 1923-06-02 Transmission for rotary engines Expired - Lifetime US1676211A (en)

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221716A (en) * 1961-07-28 1965-12-07 Careddu Orazio Four strokes, four pistons, i.c. engine with toric cylinder
US3356079A (en) * 1966-11-29 1967-12-05 Virmel Corp Rotary internal combustion engine
US3736080A (en) * 1970-05-02 1973-05-29 H Sabet Rotary-piston internal-combustion engine
US4716870A (en) * 1986-06-25 1988-01-05 Wilson Clifford E Rotary internal combustion engine
US4799868A (en) * 1986-06-25 1989-01-24 Wilson Clifford E Compressor/pump
WO1992014036A1 (en) * 1991-02-08 1992-08-20 Schadeck Mathew A Pressurized vapor driven rotary engine
US5433179A (en) * 1993-12-02 1995-07-18 Wittry; David B. Rotary engine with variable compression ratio
WO1999027233A1 (en) * 1997-11-20 1999-06-03 Valery Rassin Internal combustion rotary engine
WO2005026498A1 (en) * 2003-09-15 2005-03-24 Vyacheslav Ivanovich Kovalenko Rotary internal combustion engine
US20060150949A1 (en) * 2003-09-15 2006-07-13 Kovalenko Vyacheslav I Rotary internal combustion engine
ES2312243A1 (en) * 2006-01-25 2009-02-16 Jordi Amell Amell Rotary engine. (Machine-translation by Google Translate, not legally binding)
US20120195782A1 (en) * 2009-10-02 2012-08-02 Hugo Julio Kopelowicz System for construction of compressors and rotary engine, with volumetric displacement and compression rate dynamically variable
RU2464432C2 (en) * 2009-01-21 2012-10-20 Геннадий Константинович Холодный Operating method of rotary engine, and rotary engine by kholodny
US20180283514A1 (en) * 2017-03-29 2018-10-04 Girish Jayashankara Aradhya Malligere Two or Three Dimensional Oscillatory Motion to Rotary Motion Converter
IT201900005532A1 (en) * 2019-04-10 2020-10-10 Antonio Cadore IMPROVED ROTARY COMBUSTION MACHINE

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221716A (en) * 1961-07-28 1965-12-07 Careddu Orazio Four strokes, four pistons, i.c. engine with toric cylinder
US3356079A (en) * 1966-11-29 1967-12-05 Virmel Corp Rotary internal combustion engine
US3736080A (en) * 1970-05-02 1973-05-29 H Sabet Rotary-piston internal-combustion engine
US4716870A (en) * 1986-06-25 1988-01-05 Wilson Clifford E Rotary internal combustion engine
US4799868A (en) * 1986-06-25 1989-01-24 Wilson Clifford E Compressor/pump
WO1992014036A1 (en) * 1991-02-08 1992-08-20 Schadeck Mathew A Pressurized vapor driven rotary engine
US5147191A (en) * 1991-02-08 1992-09-15 Schadeck Mathew A Pressurized vapor driven rotary engine
US5527165A (en) * 1991-02-08 1996-06-18 Magnitude Technologies, Inc. Pressurized vapor driven rotary engine
US5433179A (en) * 1993-12-02 1995-07-18 Wittry; David B. Rotary engine with variable compression ratio
US5622149A (en) * 1993-12-02 1997-04-22 Wittry; David B. High-power rotary engine with varaiable compression ratio
WO1999027233A1 (en) * 1997-11-20 1999-06-03 Valery Rassin Internal combustion rotary engine
US6210135B1 (en) 1997-11-20 2001-04-03 Valery Rassin Internal combustion rotary engine
WO2005026498A1 (en) * 2003-09-15 2005-03-24 Vyacheslav Ivanovich Kovalenko Rotary internal combustion engine
US20060150949A1 (en) * 2003-09-15 2006-07-13 Kovalenko Vyacheslav I Rotary internal combustion engine
US7255086B2 (en) 2003-09-15 2007-08-14 Kovalenko Vyacheslav I Rotary internal combustion engine
ES2312243A1 (en) * 2006-01-25 2009-02-16 Jordi Amell Amell Rotary engine. (Machine-translation by Google Translate, not legally binding)
RU2464432C2 (en) * 2009-01-21 2012-10-20 Геннадий Константинович Холодный Operating method of rotary engine, and rotary engine by kholodny
US20120195782A1 (en) * 2009-10-02 2012-08-02 Hugo Julio Kopelowicz System for construction of compressors and rotary engine, with volumetric displacement and compression rate dynamically variable
US20180283514A1 (en) * 2017-03-29 2018-10-04 Girish Jayashankara Aradhya Malligere Two or Three Dimensional Oscillatory Motion to Rotary Motion Converter
IT201900005532A1 (en) * 2019-04-10 2020-10-10 Antonio Cadore IMPROVED ROTARY COMBUSTION MACHINE
WO2020208567A1 (en) * 2019-04-10 2020-10-15 Antonio Cadore Improved rotating combustion machine

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