US3183843A - Rotary fluid pressure pumps and motors of the eccentric vane type - Google Patents

Rotary fluid pressure pumps and motors of the eccentric vane type Download PDF

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US3183843A
US3183843A US274530A US27453063A US3183843A US 3183843 A US3183843 A US 3183843A US 274530 A US274530 A US 274530A US 27453063 A US27453063 A US 27453063A US 3183843 A US3183843 A US 3183843A
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pair
fingers
slipper
working chamber
rotor
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David H Cockburn
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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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Definitions

  • This invention relates to rotary fluid pressure pumps and motors of the eccentric vane type, such pumps or motors including a casing defining a substantially cylindrical working chamber having inlet and outlet passages leading to inlet and outlet ports, the chamber containing an eccentrically mounted rotor, said rotor carrying a series of substantially T shaped vane elements or slippers which move radially in relation to the rotor whilst r0tating therewith, their outer surfaces maintaining contact with the inner wall of the working chamber in a substantially fluid tight manner.
  • the present invention is virtually an improvement in or modification of that forming the subject of my prior U.S. Patent No. 2,778,317.
  • the chief object of the invention is to increase the capacity of such pumps and motors and particularly the pump or motor forming the subject of the above numbered patent and when operating as a motor to give an increased torque.
  • the present invention consists broadly in so constructing the slippers that the flanges of adjacent slippers overlap one another in a lateral direction. In this way the effective length of each flange is considerably increased and it is possible to increase the length of each stem, thus decreasing the risk of tilting and enabling the eccentricity of the rotor to be considerably increased over and above the construction previously proposed. Furthermore by employing flanges of greater length the hydraulic load between each slipper and the wall of the working chamber will be substantially decreased.
  • FIGURE 1 is a view, halt section and half elevation of a pump or motor fitted with slippers and a rotor in accordance with the present invention
  • FIGURE 2 is a section on the line A--A in FIGURE
  • FIGURE 3 is a section through the centre of the improved slipper
  • FIGURE 4 is a development illustrating how two of the slippers interengage
  • FIGURE 5 is a side elevation of one of the assembled helical and flat springs for urging the slipper outwardly into engagement with the circumferential wall of the working chamber;
  • FIGURE 6 is a plan view of the helical spring
  • FIGURE 7 is a plan view of the flat spring
  • FIGURE 8 is a half sectional, half eleva-tional view of the casing
  • FIGURE 9 is a half sectional plan
  • FIGURE 10 is a vertcial section on the line B-B in FIGURE 8;
  • FIGURE 11 is a section on the line CC in FIGURE 12 showing .the invention applied to a modified pump or motor of variable stroke;
  • FIGURE 12 is a half elevational, half sectional view of same.
  • the pump or motor comprises a casing 1 having an annular boring constituting the circumferential wall of the working chamber which is closed at its ends by end plates 2 and cover plates 3, the end plates carry-ing bearings 4 for .
  • a rotor shaft 5 carrying in splined connection a rotor 6 formed with for example five flat faces 7 separated by slots 8, the walls of which diverge radially inwardly.
  • the shaft is eccentrically mounted so that the rotor 6 rotates eccentrically within the working chamber.
  • the casing 1 is provided with inlet and outlet passages 9 for the working fluid communicating with the working chamber.
  • the rotor 6 carries for example five slippers 10 which are exteriorly curved to conform to the internal curved surface of the working chamber.
  • each slipper including a central stem 11 which enters one of the slots 8, the stem having a thickness such that it fits closely within the mouth of the slot, but is free to pivot therein during rotation of the rotor, the edges of each slot adjacent the mouth being radiused as shown in FIGURE 1.
  • Each slipper includes a pair of flanges of fork shape and each including a pair of tapering tines or fingers indicated by reference numerals 15 and 16.
  • Times 15 have parallel outer edges 17 and inclined inner edges 18.
  • Tines 1-6 have outer edges 19 inclined to correspond with the inclination of edges 18 so that adjacent slippers overlap laterally in the manner shown in FIGURE 4 leaving only a small working clearance between them.
  • the inner edges 20 of tines 16 are arranged in parallel relationship and allow the passage of the working fluid therebetween into and out of the working chamber.
  • Each fork is bevelled as at 21 to give increased lap relative to the inlet and outlet passages for the fluid and at the same time permit of uniform deflection of the tines under load conditions, the tines by virtue of their resilient construction making resilient engagement with the wall of the working chamber.
  • slippers may alternatively be bent up from sheet metal blanks, each slipper being constructed as two parts of substantially L shape, each including a half stem portion and a flange portion, the half stem portions being riveted or otherwise connected together back to back to form a complete stem.
  • each assembly consisting of a helically wound spring 12 and a flat spring 13, the latter having a pair of arms projecting in opposite directions from a central loop 14 for the reception of a rivet 15' passing through an end loop 16 on the helical spring whereby the two springs are secured together.
  • each assembly is mounted in the position shown in FIGURES 1 and 2, each helical spring being located in a recess 22 by a spigot portion 23, the flat spring bearing on the laterally overlapping tines of adjacent slippers to urge them radially outwardly into engagement with the wall of the working chamber. Only one such spring unit 12, 13 is shown in FIGS. 1 and 2.
  • the casing contains a pair of oppositely positioned arcuate shaped main ports 24 and two pairs of correspondingly shaped side ports 25, the latter being connected with inlet an outlet passages 9 by branch passages 26.
  • FIGURES 11 and 12 illustrate a construction of .pump or motor wherein the degree of eccentricity of the rotor and consequently the effective stroke of the slippers can be varied, to vary the effective capacity of the pump or motor and in the case of a motor to reverse its direction 'of rotation, and in the case of a pump reverse the direction of the flow of fluid.
  • the casing 1 is extended upwardly and downwardly to enclose the inlet and outlet pipes 9 and 9a, the casing 7 being pivotable about the axis of pipe fi through a limited angle in opposite directions from a central neutral position in which the rotor is concentrically positioned in the working chamber in which position there will be no displacement of the slippers and consequently no fluid displacement or in the case of a motor no rotation of the rotor.
  • a central neutral position in which the rotor is concentrically positioned in the working chamber in which position there will be no displacement of the slippers and consequently no fluid displacement or in the case of a motor no rotation of the rotor.
  • any suitable means may be used to move the casing about its pivot point whilst the pipe 9a enters the casing through an elongated hole 27, the pipes 9 and 9a being formed with a series of radial holes 28 in their walls through which the fluid can enter and leave the casing. It will be appreciated that only the casing will partake of the pivotal movement, the casing having a combined sliding and pivotal movement between the two fixed cover plates 2, the facesof the casing being formed with grooves containing sealing members 29, for preventing leakage of fluid between the ground faces of the casing and cover plates.
  • a hydraulic pump or motor of the type comprising a casing defining a substantially cylindrical working chamber with a circumferential wall and two end walls and a rotor mounted eccentrically within said casing, said rotor having a plurality of spaced grooves extending longitudinally and radially inwardly from the circumference thereof, the improvement comprising a series of slipper elements corresponding in number to the number of said spaced grooves and adapted to slidably engage the circumferential wall of the cylindrical working chamber,
  • each of said slipper elements having a stem portion slidably extending into its particular groove so as to move in and out of said groove
  • each of said slipper elements having a first pair of fingers curved to fit the contour of the cylindrical working chamber extending forwardly from said stern, and a second pair of fingers curved to fit the contour of said cylindrical working chamber extending to the rear of said stem,
  • spring means having one end thereof retained within said recess and the other end thereof pressing against the interfitting first and second fingers of two adjacent slipper elements.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Description

y 18, 1965 D. H. COCKBURN 3,133,843
ROTARY FLUID PRESSURE PUMPS AND MOTORS OF THE ECCENTRIC VANE TYPE Filed April 22, 1963 V 4 Sheets-Sheet 1 IN VE N TOR fin wp hnmLra/v COCKBURN A TTORNEY y 13, 1965 D. H. COCKBURN 3,183,343
ROTARY FLUID PRESSURE PUMPS AND MOTORS OF THE ECGENTRIC VANE TYPE Filed April 22, 1963 4 Sheets-Sheet 2 INVENTOR M MM ATTORNEY BURN 3,183,843 PUMPS AND MOTORS C VANE TYPE May 18, 1965 D. H. COCK ROTARY FLUID PRESSURE THE ECCENTRI 4 Sheets-Sheet 3 Filed April 22, 1963 IN VE N TOR fl/W/o Han/a0 [burs amv A TTORNE Y D. H. o BURN 3,183,843 ROTARY FLUID PRE S PUMPS AND MOTORS OF THE ECG IC VANE TYPE Filed April 22, 1963 May 18, 1965 4 Sheets-Sheet 4 IN 5 N TO}? 17/11/10 f/nmLravCocwz/xw A TTOP/Vf Y United States Patent 3,183,843 ROTARY FLUID PRESSURE PUMPS AND MOTORS OF THE ECCENTRIC VANE TYPE David H. Cockburn, 1 N. Park, Iver, Buckinghamshire, England Fiied Apr. 22, 1963, Ser. No. 274,530 4 Claims. (Cl. 103-136) This invention relates to rotary fluid pressure pumps and motors of the eccentric vane type, such pumps or motors including a casing defining a substantially cylindrical working chamber having inlet and outlet passages leading to inlet and outlet ports, the chamber containing an eccentrically mounted rotor, said rotor carrying a series of substantially T shaped vane elements or slippers which move radially in relation to the rotor whilst r0tating therewith, their outer surfaces maintaining contact with the inner wall of the working chamber in a substantially fluid tight manner.
The present invention is virtually an improvement in or modification of that forming the subject of my prior U.S. Patent No. 2,778,317.
The chief object of the invention is to increase the capacity of such pumps and motors and particularly the pump or motor forming the subject of the above numbered patent and when operating as a motor to give an increased torque.
In the earlier patent above referred to, the slippers converged towards one another over that part of the wall of the working chamber lying nearest to the axis of rotation of the rotor and consequently the length of the transverse portions or flanges of the T shaped slippers was limited and there was considerable spacing of the flanges, over that part of the chamber wall lying furthest from the axis of rotation. This limitation in the length of each flange limited the ratio between the length of each flange and the length of the intermediate inwardly directed stern and if this ratio was reduced to less than 2-1 there was risk tilting of the slippers occurring and the break ing down of the seal between the slippers and the wall of the working chamber.
The present invention consists broadly in so constructing the slippers that the flanges of adjacent slippers overlap one another in a lateral direction. In this way the effective length of each flange is considerably increased and it is possible to increase the length of each stem, thus decreasing the risk of tilting and enabling the eccentricity of the rotor to be considerably increased over and above the construction previously proposed. Furthermore by employing flanges of greater length the hydraulic load between each slipper and the wall of the working chamber will be substantially decreased.
Such an arrangement very materiallly increases the capacity of the pump or motor and in the case of a motor considerably increases the output torque available without adding to the friction and leakage losses thereby pro viding a considerable increase in overall efliciency.
Referring to the accompanying drawings:
FIGURE 1 is a view, halt section and half elevation of a pump or motor fitted with slippers and a rotor in accordance with the present invention;
FIGURE 2 is a section on the line A--A in FIGURE FIGURE 3 is a section through the centre of the improved slipper; and
FIGURE 4 is a development illustrating how two of the slippers interengage;
FIGURE 5 is a side elevation of one of the assembled helical and flat springs for urging the slipper outwardly into engagement with the circumferential wall of the working chamber;
FIGURE 6 is a plan view of the helical spring;
"Ice
FIGURE 7 is a plan view of the flat spring;
FIGURE 8 is a half sectional, half eleva-tional view of the casing;
FIGURE 9 is a half sectional plan;
FIGURE 10 is a vertcial section on the line B-B in FIGURE 8;
FIGURE 11 is a section on the line CC in FIGURE 12 showing .the invention applied to a modified pump or motor of variable stroke; and
FIGURE 12 is a half elevational, half sectional view of same.
Referring in the first case to FIGURES 1 and 2, the pump or motor comprises a casing 1 having an annular boring constituting the circumferential wall of the working chamber which is closed at its ends by end plates 2 and cover plates 3, the end plates carry-ing bearings 4 for .a rotor shaft 5 carrying in splined connection a rotor 6 formed with for example five flat faces 7 separated by slots 8, the walls of which diverge radially inwardly. The shaft is eccentrically mounted so that the rotor 6 rotates eccentrically within the working chamber.
The casing 1 is provided with inlet and outlet passages 9 for the working fluid communicating with the working chamber.
The rotor 6 carries for example five slippers 10 which are exteriorly curved to conform to the internal curved surface of the working chamber.
The general formation of the slippers is illustrated more clearly in FIGURES 3 and 4, each slipper including a central stem 11 which enters one of the slots 8, the stem having a thickness such that it fits closely within the mouth of the slot, but is free to pivot therein during rotation of the rotor, the edges of each slot adjacent the mouth being radiused as shown in FIGURE 1.
Each slipper includes a pair of flanges of fork shape and each including a pair of tapering tines or fingers indicated by reference numerals 15 and 16.
Times 15 have parallel outer edges 17 and inclined inner edges 18.
Tines 1-6 have outer edges 19 inclined to correspond with the inclination of edges 18 so that adjacent slippers overlap laterally in the manner shown in FIGURE 4 leaving only a small working clearance between them.
The inner edges 20 of tines 16 are arranged in parallel relationship and allow the passage of the working fluid therebetween into and out of the working chamber.
Each fork is bevelled as at 21 to give increased lap relative to the inlet and outlet passages for the fluid and at the same time permit of uniform deflection of the tines under load conditions, the tines by virtue of their resilient construction making resilient engagement with the wall of the working chamber.
Although it is preferred to construct the slippers as drop forgings they may alternatively be bent up from sheet metal blanks, each slipper being constructed as two parts of substantially L shape, each including a half stem portion and a flange portion, the half stem portions being riveted or otherwise connected together back to back to form a complete stem.
The slippers are maintained in working engagement with the wall of the working chamber by spring assemblies shown in FIGURES 5 to 7, each assembly consisting of a helically wound spring 12 and a flat spring 13, the latter having a pair of arms projecting in opposite directions from a central loop 14 for the reception of a rivet 15' passing through an end loop 16 on the helical spring whereby the two springs are secured together.
Each assembly is mounted in the position shown in FIGURES 1 and 2, each helical spring being located in a recess 22 by a spigot portion 23, the flat spring bearing on the laterally overlapping tines of adjacent slippers to urge them radially outwardly into engagement with the wall of the working chamber. Only one such spring unit 12, 13 is shown in FIGS. 1 and 2.
The positioning and shape of the ports leading from the working chamber to the inlet and outlet passages 9 is shown more clearly in FIGURES 8 to 10. The casing contains a pair of oppositely positioned arcuate shaped main ports 24 and two pairs of correspondingly shaped side ports 25, the latter being connected with inlet an outlet passages 9 by branch passages 26.
FIGURES 11 and 12 illustrate a construction of .pump or motor wherein the degree of eccentricity of the rotor and consequently the effective stroke of the slippers can be varied, to vary the effective capacity of the pump or motor and in the case of a motor to reverse its direction 'of rotation, and in the case of a pump reverse the direction of the flow of fluid.
The casing 1 is extended upwardly and downwardly to enclose the inlet and outlet pipes 9 and 9a, the casing 7 being pivotable about the axis of pipe fi through a limited angle in opposite directions from a central neutral position in which the rotor is concentrically positioned in the working chamber in which position there will be no displacement of the slippers and consequently no fluid displacement or in the case of a motor no rotation of the rotor. By moving the casing in one direction from the neutral position to its maximum angular position an infinitely variable output or in the case of a motor a variable rotor speed can be obtained, the direction of fluid flow or rotation of the rotor being reversed by moving the casing in the opposite direction.
Any suitable means may be used to move the casing about its pivot point whilst the pipe 9a enters the casing through an elongated hole 27, the pipes 9 and 9a being formed with a series of radial holes 28 in their walls through which the fluid can enter and leave the casing. It will be appreciated that only the casing will partake of the pivotal movement, the casing having a combined sliding and pivotal movement between the two fixed cover plates 2, the facesof the casing being formed with grooves containing sealing members 29, for preventing leakage of fluid between the ground faces of the casing and cover plates.
I claim: 1. In a hydraulic pump or motor of the type comprising a casing defining a substantially cylindrical working chamber with a circumferential wall and two end walls and a rotor mounted eccentrically within said casing, said rotor having a plurality of spaced grooves extending longitudinally and radially inwardly from the circumference thereof, the improvement comprising a series of slipper elements corresponding in number to the number of said spaced grooves and adapted to slidably engage the circumferential wall of the cylindrical working chamber,
each of said slipper elements having a stem portion slidably extending into its particular groove so as to move in and out of said groove,
each of said slipper elements having a first pair of fingers curved to fit the contour of the cylindrical working chamber extending forwardly from said stern, and a second pair of fingers curved to fit the contour of said cylindrical working chamber extending to the rear of said stem,
the second pair of fingers of any slipper element of said series interfitting with the first pair of fingers of the next adjacent slipper element while providing openings for the passage of fluid between said second pair of fingers.
2. The pump or motor as claimed in claim 1 wherein said first pair of fingers of each slipper element have parallel outer edges but diverge outwardly from their innerends to provide a diverging slot therebetween, said second pair of fingers having converging outer edges adapted to fit within the diverging slot between the first pair of fingers of the next adjacent slipper element.
3. The pump or motor as claimed in claim 1 wherein the connection between the stems of said slipper elements and the fingers thereof is tapered.
4. The pump or motor as claimed in claim 1 wherein said rotor contains at least one recess between adjacent spaced grooves,
spring means having one end thereof retained within said recess and the other end thereof pressing against the interfitting first and second fingers of two adjacent slipper elements.
References Cited by the Examiner UNITED STATES PATENTS 713,448 11/02 Kalbach 91-134 1,333,656 3/20 Eizerman 103135 2,336,580 12/43 Yeatman 103l17 2,778,317 1/57 Cockburn 103134 FOREIGN PATENTS 737,292 7/43 Germany.
JOSEPH H. BRANSON, JR., Primary Examiner.

Claims (1)

1. IN A HYDRUALIC PUMP OR MOTOR OF THE TYPE COMPRISING A CASING DEFINING A SUBSTANTIALLY CYLINDRICAL WORKING CHAMBER WITH A CIRCUMFERENTIALLY WALL AND TWO END WALLS AND A ROTOR MOUNTED ECCENTRICALLY WITHIN SAID CAING, SAID ROTOR HAVING A PLURALITY OF SPACED GROOVES EXTENDING LONGITUDINALLY AND RADIALLY INWARDLY FROM THE CIRCUMFERENCE THEREOF, THE IMPROVEMENT COMPRISING A SERIES OF SLIPPER ELEMENTS CORRESPONDING IN NUMBER TO THE NUMBER OF SAID SPACED GROOVES AND ADAPTED TO SLIDABLY ENAGAGE THE CIRCUMFERENTIAL WALL OF THE CYLINDRICAL WORKING CHAMBER, EACH OF SAID SLIPPER ELEMENTS HAVING A STEM PORTION SLIDABLY EXTENDING INTO ITS PARTICULAR GROOVE SO AS TO MOVE IN AND OUT OF SAID GROOVE, EACH OF SAID SLIPPER ELEMENTS HAVING FIRST PAIR OF FINGERS CURVED TO FIT THE CONTOUR OF THE CYLINDRICAL WORKING CHAMBER EXTENDING FORWARDLY FROM SAID STEM, AND A SECOND PAIR OF FINGERS CURVED TO FIT THE CONTOUR OF SAID CYLINDRICAL WORKING CHAMBR EXTENDING TO THE REAR OF SAID STEM, THE SECOND PAIR OF FINGERS OF ANY SLIPPER ELEMENT OF SAID SERIES INTERFITTING WITH THE FIRST PAIR OF FINGERS OF THE NEXT ADJACENT SLIPPER ELEMENT WHILE PROVIDING OPENINGS FOR THE PASSAGE OF FLUID BETWEEN SAID SECOND PAIR OF FINGERS.
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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3282222A (en) * 1964-10-13 1966-11-01 Itt Rotating vane machines
US4898524A (en) * 1989-01-27 1990-02-06 Snap-On Tools Corporation Fluid driven rotary motor
US6312243B1 (en) * 1997-12-08 2001-11-06 Van Doorne's Transmissie B.V. Roller vane pump having straight line segments on the rotor
US6325602B1 (en) * 1999-09-23 2001-12-04 John J. Rademacher Automotive vacuum pump
EP1209319A1 (en) * 1999-07-30 2002-05-29 Yoshikane Ikitake Reciprocating vane type rotary internal combustion engine
US20060201156A1 (en) * 2005-03-09 2006-09-14 Pekrul Merton W Plasma-vortex engine and method of operation therefor
US20110116958A1 (en) * 2005-03-09 2011-05-19 Pekrul Merton W Rotary engine expansion chamber apparatus and method of operation therefor
US20110142702A1 (en) * 2005-03-09 2011-06-16 Fibonacci International, Inc. Rotary engine vane conduits apparatus and method of operation therefor
US20110158837A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine vane apparatus and method of operation therefor
US20110155095A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine flow conduit apparatus and method of operation therefor
US20110155096A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine valving apparatus and method of operation therefor
US20110165007A1 (en) * 2005-03-09 2011-07-07 Fibonacci International, Inc. Rotary engine vane head method and apparatus
US20110171051A1 (en) * 2005-03-09 2011-07-14 Fibonacci International, Inc. Rotary engine swing vane apparatus and method of operation therefor
US20110176947A1 (en) * 2005-03-09 2011-07-21 Fibonacci International, Inc. Rotary engine vane cap apparatus and method of operation therefor
US20110200473A1 (en) * 2005-03-09 2011-08-18 Fibonacci International, Inc. Rotary engine lip-seal apparatus and method of operation therefor
US8360760B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine vane wing apparatus and method of operation therefor
US20130202470A1 (en) * 2012-02-08 2013-08-08 Shining Golden Yida Welding & Cutting Machinery Manufacture Ltd. Rotary Vane Air Motor with Improved Vanes and Other Improvements
US8800286B2 (en) 2005-03-09 2014-08-12 Merton W. Pekrul Rotary engine exhaust apparatus and method of operation therefor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US713448A (en) * 1902-08-05 1902-11-11 Morgan D Kalbach Rotary engine.
US1333656A (en) * 1918-08-05 1920-03-16 William H Eizerman Pump
DE737292C (en) * 1942-06-21 1943-07-10 Joachim Jenning Pistonless friction pump working with oil wedge effect
US2336580A (en) * 1941-12-08 1943-12-14 Walter C Yeatman Artery type rotary pump
US2778317A (en) * 1954-10-25 1957-01-22 Cockburn David Hamilton Rotary fluid pressure pumps and motors of the eccentric vane type

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US713448A (en) * 1902-08-05 1902-11-11 Morgan D Kalbach Rotary engine.
US1333656A (en) * 1918-08-05 1920-03-16 William H Eizerman Pump
US2336580A (en) * 1941-12-08 1943-12-14 Walter C Yeatman Artery type rotary pump
DE737292C (en) * 1942-06-21 1943-07-10 Joachim Jenning Pistonless friction pump working with oil wedge effect
US2778317A (en) * 1954-10-25 1957-01-22 Cockburn David Hamilton Rotary fluid pressure pumps and motors of the eccentric vane type

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3282222A (en) * 1964-10-13 1966-11-01 Itt Rotating vane machines
US4898524A (en) * 1989-01-27 1990-02-06 Snap-On Tools Corporation Fluid driven rotary motor
US6312243B1 (en) * 1997-12-08 2001-11-06 Van Doorne's Transmissie B.V. Roller vane pump having straight line segments on the rotor
EP1209319A1 (en) * 1999-07-30 2002-05-29 Yoshikane Ikitake Reciprocating vane type rotary internal combustion engine
EP1209319A4 (en) * 1999-07-30 2004-05-12 Yosikane Ikitake Reciprocating vane type rotary internal combustion engine
US6325602B1 (en) * 1999-09-23 2001-12-04 John J. Rademacher Automotive vacuum pump
US20110176947A1 (en) * 2005-03-09 2011-07-21 Fibonacci International, Inc. Rotary engine vane cap apparatus and method of operation therefor
US8360759B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine flow conduit apparatus and method of operation therefor
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