WO1984000993A1 - Machine rotative - Google Patents

Machine rotative Download PDF

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Publication number
WO1984000993A1
WO1984000993A1 PCT/US1983/001244 US8301244W WO8400993A1 WO 1984000993 A1 WO1984000993 A1 WO 1984000993A1 US 8301244 W US8301244 W US 8301244W WO 8400993 A1 WO8400993 A1 WO 8400993A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
chamber
rotors
sealing
rotary machine
Prior art date
Application number
PCT/US1983/001244
Other languages
English (en)
Inventor
Edward Charles Mendler Iii
Original Assignee
Edward Charles Mendler Iii
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 Edward Charles Mendler Iii filed Critical Edward Charles Mendler Iii
Priority to AU19460/83A priority Critical patent/AU1946083A/en
Publication of WO1984000993A1 publication Critical patent/WO1984000993A1/fr
Priority to PCT/US1984/000873 priority patent/WO1984004943A1/fr
Priority to EP19840902419 priority patent/EP0146612A4/fr

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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/16—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
    • 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
    • F01C1/24—Rotary-piston machines or engines of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions
    • F01C1/28—Rotary-piston machines or engines of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions of other than internal-axis type
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to rotary machines that have a fluid chamber of changing volume, as in an engine or a pump.
  • Rotary machines of this type employ a rotating surface to have a working relationship with a fluid, e.g. compression or expansion. In the case of an engine, the machine also generates shaft energy as where a compressed gas and fuel mixture is ignited for explosive expansion within the chamber of the machine.
  • Prior rotary machines have typically employed one eccentric rotor or multiple adjacent rotors that turn in opposite directions so that adjacent rotor surfaces move in the same direction; however, machines having rotors turning in the same direction have been suggested.
  • the invention applies to a rotary machine that cyclically defines a chamber of progressively changing volume by means of a pair of co-acting rotors.
  • the rotors are mounted for dependent rotation on parallel axes of adjacent cylindrical bores formed in a block, the axes being spaced apart a ⁇ istance less than the sum of the radii of the bores.
  • the rotors have surfaces adapted to provide a progressive rotor-to-rotor seal while each rotor also forms a rotor-to-bore-wall seal and face-to-end-closing surface seals, the rotor surfaces in cooperation with the other surfaces of the machine defining the chamber of changing volume.
  • CMFI CMFI
  • the rotors rotate in the same direction
  • a cylindrical surface of the first rotor of radius substantially equal to the radius of its bore and having substantial arcuate extent, is arranged in sealing relationship with its bore wall and with a surface of the second rotor, at least part of the surface of the second rotor exposed to this chamber has a progressively changing ra ⁇ ius to cause the chamber volume to progressively change during rotation, and the rotor surfaces are constructed to avoid interfering contact.
  • the cylindrical surface of the first rotor ends at an apex adapted to form the seal with the chamber-sounding surface of the second rotor
  • the second rotor defines a transition surface which extends from the point of minimum radius at which the apex portion forms a seal therewith, through a curve of increasing radius, to a point having radius corresponding substantially to the radius of the second bore, the curve being shaped to correspond substantially to the path of the apex of the first rotor over the extent of the progressive rotor-to-rotor seal.
  • the apex of the first rotor moves in sealing relationship along the transition surface of the second rotor, and the volume of the chamber progressively changes as a result of movement of the transition surface relatively toward or away from the cylindrical surface.
  • the direction of rotation causes the transition surface to move relatively toward the cylindrical surface while the apex moves to points of increasing radius along the curve of the transition surface.
  • the direction of motion is in the opposite direction.
  • the transition surface of the second rotor is adapted to transform the expansive force of the contained gas into shaft energy.
  • an intake or an exhaust flow path is defined by cooperative opposed surfaces of one of the rotors and the block during rotation of the rotors.
  • the path is typically formed prior to the formation of the respective rotor-to-bore-wall seal and in many cases is associated with a source of pressurized fluid which forces the fluid through the path.
  • an inflow path and an outflow path are formed simultaneously at different sides, to establish a through-flow of fluid through the space in which the chamber is to be formed.
  • simultaneous flow paths enable through-flow of air to scavenge combustion gases from the region, to cool the working surfaces of the engine and to provide combustion air to the chamber for the next cycle.
  • a stationary surface that bounds the chamber when the volume of the chamber is reduced includes fuel injection and/or ignition means.
  • the intake means comprises an inlet port to enable flow of fluid into the chamber while the chamber expands.
  • an exhaust means provides for outward flow of pressurized fluid from the chamber while the chamber decreases in volume.
  • a rotary machine which comprises a rotor and means defining a bore surface with which the rotor is arranged to interact to cylically define a fluid chamber during rotor rotation.
  • a variable member defining a portion of the bore surface is movable toward and away from the rotor in the manner to vary the rotational position of a transition point at which a sealed relationship between the rotor and the bore surface begins or ends, and means responsive to desired operating conditions to vary the position of the variable portion thereby to vary the rotational position of the point at which the sealed relationship begins or ends.
  • the rotary machine is in the form of a rotary internal combustion engine in which the rotor and bore surface are cooperatively constructed to form at least part of a combustion chamber, the variable member defining with the rotor the point where the volume of the combustion chamber is first closed, variation in the position of the member serving to vary the compression ratio of the engine; and the bore surface is comprised in part of a relatively stationary first bore surface segment of radius which progressively enlarges relative to the radius of the rotor at points at progressively greater arcuate distance about the rotor axis from the point of the segment which lies closest to the rotor, the variable member defining a second bore surface segment which is movable outwardly relative to the first segment and has a transition end portion disposed closely adjacent to the relatively stationary segment, the transition end portion being movable along the first bore surface segment as the variable member moves outwardly from the rotor axis to expose an increasing amount of the first bore surface segment, preferably the variable member is pivotable about a pivot axis lying directly out
  • the invention applies to a rotary machine that cyclically defines a chamber of progressively changing volume by means of a pair of co-acting rotors.
  • the rotors are mounted for dependent rotation on parallel axes of a ⁇ jacent cylindrical bores formed in a block, the axes being spaced apart a distance less than the sum of the radii of the bores.
  • the rotors have surfaces adapted to provide a progressive rotor-to-rotor seal while each rotor also forms a rotor-to-bore-wall seal and face-to-end-closing-surface seals, the rotor surfaces in cooperation with the other surfaces of the machine defining the chamber.
  • the rotors rotate in the same direction
  • a cylindrical surface of the first rotor of radius substantially equal to the radius of its bore and having substantial arcuate extent, is arranged in sealing relationship with its bore wall and with a surface of the second rotor, at least part of the surface of the second rotor exposed to this chamber has a progressively changing radius to cause the chamber volume to progressively change during rotation, and the rotor surfaces are constructed to avoid interfering contact.
  • the transition surface (upon which the apex of the first rotor formed a seal during the compression stage) is followed by a large cylindrical surface, and on the first rotor the large cylindrical surface is followed by a transition surface.
  • a second seal-forming apex is defined between the transition and cylindrical surfaces on the second rotor.
  • each of the rotors has a transition surface preceding its large cylindrical surface and a transition surface following its large cylindrical surface, with an apex formed at each end of each large cylindrical surface.
  • Different sets of surfaces and apexes, during different stages of rotation, thus can form chambers.
  • the second rotor has a minor cylindrical surface beyond the small end of the transition surface, of radius substantially equal to the difference between the length of the line of centers of the rotors and the radius of the cylindrical surface of the first rotor.
  • This minor cylindrical surface is arranged to be at the line of centers when the large cylindrical surface of the first rotor is at the line of centers, thereby to form a seal.
  • the rotors are of identical size and shape with all of the features mentioned above and rotate at the same speed to form a pair of spaced-apart chambers.
  • the sealing members ' at each apex are adapted to apply against the opposed surfaces outward sealing pressure that decreases in magnitude with increase in the velocity of rotation.
  • the rotor-contacting surface of the sealing member is free to move in response to intertial effects.
  • the sealing member is free to slightly swing between first (rest) and second (high speed) positions about a pivot region that is positioned inwardly from the periphery of the rotor, the pivot region being offset from a radius of the rotor that projects to the center of mass of the sealing member.
  • the motion of the sealing surface can be made to be mostly tangential or mostly radial depending upon the needs of the particular embodiment.
  • the sealing member it is a rigid element extending outwardly from a rotating pivot bearing, the sealing member being biased toward the first position by an indepndent spring means, or is a cantilever spring portion capable of flexing generally in the pivot region in response to centrifugal effects; the force of the spring is progressively overcome by centrifugal effects as the rotor increases in speed; and in the preferred rotary machine of the invention, the second (high speed) position of the sealing surface relative to the first position is positioned tangentially in the direction of the major cylindrical surface of its rotor and away from its transition surface.
  • a further important feature of the invention is that the described sealing member, at a given speed of rotation of tne rotor, can oe constructed and arranged to bear against the transition surface with pressure normal to the transition surface which varies generally inversely with change of volume of the chamber.
  • the sealing member described above may be used in conjunction with any rotary device to form a seal with an opposed surface, the seal being constructed and arranged, preferably as earlier described, to respond to rotational speed to relieve sealing pressure as speed increases.
  • the invention applies to a rotary machine which comprises a rotor, means defining a complementary, opposed surface, and a sealing member bodily carried by the rotor member and movable with respect to the rotor member toward the complementary surface to form a seal therewith, the point of sealing of the sealing me Der progressing about the surface as the rotor rotates.
  • restraint means are responsive to increase in the rotational rotor speed to apply increased restraint on the freedom of relative motion of the sealing member toward the surface thereby to enable decrease or elimination of direct pressure contact between the sealing member and the surface upon increased rotor speed.
  • the restraining means comprises a restraint member carried by the rotor and defining a friction brake surface engageable with the sealing member in a manner to restrain movement of the seal member, the restraint member being responsive to increase in centrifugal force attributable to increased speed of rotor rotation, to increase the pressure of engagement of the friction brake surface upon the sealing member, thereby to increase the restraint of the sealing member
  • the sealing member comprises a member having a rotary bearing surface bearing upon a corresponding surface defined by the rotor, the sealing member extending from and rotable with the rotary bearing surface to move into sealing engagement with the complementary surface
  • the restraint member comprising a member lying inwardly of the sealing member, the restraint member having a surface engaged for relative motion with a corresponding surface of the sealing member, the restraint member being constrained against rotation with the sealing member and disposed to respond to increase in centrifugal force to engage the sealing member with increased pressure, thereby to frictionally restrain
  • the rotor includes a seal means for providing a sealing relationship with a complementary stationary chamber surface during rotary motion of the rotor, the seal means being comprised of at least one sealing member carried on the rotor and defining a sealing surface disposed in face-to-face relationship with the complementary surface, the bias means between the member and the rotor adapted to bias the sealing member toward the complementary surface, the bias means having a biasing portion with at least a component lying perpendicular to the radius of the rotor and a point of attachment spaced from the biasing portion, which is adapted and configured to apply a biasing force to the sealing member toward said complementary surface, the dimensional extent of the biasing portion in a direction perpendicular to the radius of the rotor at a first speed of rotation being different from the dimensional extent at a second speed of rotation, the biasing portion adapted to move elastically between positions at first and second speeds of rotation in response to increase of centrifugal force thereon, the biasing force applied by the biasing
  • OMPI having a dimensional component perpendicular to a radius of the rotor, whereby, due to said perpendicular dimensional component, the bias means, when the rotor is at rest, biasing a sealing member toward a complementary stationary surface, and when the rotor is rotating at a different, higher speed, the outer end of the bias means is urged radially outward by centrifugal force thereby reducing its perpendicular dimensional component and reducing the biasing force of the bias means toward the sealing member, and the sealing member comprises a plurality of flat sealing members disposed in axially superposed relationship, there being bias means between each pair of said flat sealing members and between said rotor and its adjacent said flat sealing member, adapted to bias the respective members apart, whereby the total clearance is divided between a plurality of small, flow-resistant gaps.
  • end seals for the machine comprises substantially flat seal elements disposed on the rotor in face-to-face relationship with the end-closing surface of the bore, with means between the seal and the rotor to bias the seal element toward the end closing surface.
  • a surface of the seal defines at least one recess whereby fluid passing from a zone of high pressure to a zone of lower pressure across the seal surface encounters an enlarged volume with pressure of intermediate magnitude, the seal surface adapted to isolate the recess to maintain the pressure therein at the intermediate magnitude.
  • a plurality of isolated recesses are provided to be encountered successively by the passing fluid, the pressure in the
  • WIPO i_RNATX recesses being of progressively decreasing magnitude from the region of high pressure to the region of lower pressure along the fluid path.
  • a recess is provided in a fluid path across a surface remote from the sealing surface, the fluid under pressure in this recess being effective to bias an overlying seal toward the end surface; preferably recesses defined on different surfaces are connected axially through the seal, whereby the pressures in the recesses can be nearly balanced to maintain equal sealing effectiveness through the various axial gaps.
  • a machine comprises a moving element and means defining a fixed surface with which the moving element is arranged to interact to cyclically define a fluid chamber during movement of the element, a surface of the element and the fixed surface adapted to be disposed in close-mated relationship to retard movement of fluid therebetween between the fluid chamber and an area of different pressure.
  • a multiplicity of grooves defined in a fixed surface are configured-and arranged to permit fluid moving between surfaces in close-mated relationship from a first area of relatively high pressure to a second area of relatively lower pressure to pressurize the grooves in progression from the first area toward the second area.
  • the grooves defined in the fixed surface are configured and arranged to provide that movement of element surface in close-mated relationship with the fixed surface is adapted to progressively expose the grooves to the fluid chamber, whereby as leakage of fluid between the close-mated surfaces from the area of relatively higher pressure to a first groove defined in the fixed surface adjacent to the area of relatively higher pressure increase the pressure therein, movement of the element causes the first groove to be exposed to the area of higher pressure, thereby increasing the sealing performance of the close-mated surfaces.
  • Fig. 1 is a cross-sectional view of a segment of a preferred internal combustion engine according to the invention taken on line 1-1 of Fig. 3 showing the rotors full rather than in cross-section;
  • Fig. la is a similar view of an engine with variable compression ratio taken at the line la-la of Fig. 3a;
  • Fig. lb and lc are diagrammatic views of the engine of Fig. la at different compression ratios;
  • Fig. Id is a view similar to that in Figs. 1 and la of another variable compression engine construction;
  • Fig. 2 is an axial cross section taken on line
  • OMPI Fig. 2a is a similar view of the engine having variable compression, taken at line 2a-2a of- Fig. 3a;
  • Fig. 3 is a diagrammatic side view partially in section of a complete engine having six segments in accordance with Fig. 1;
  • Fig. 3a is a diagrammatic side view partially in section of a two-chamber engine block with variable compression
  • Fig. 4 is a cross-sectional view taken on line 4-4 of Fig. 3 showing gearing of the rotor shafts;
  • Figs. 5 through 5f depict the engine segment of Fig. 1 showing the rotors in the various phases of operation of an upper chamber, from intake through exhaust;
  • Fig. 6 is an isometric view of a rotor removed from the engine, not showing spline teeth or labyrinth grooves;
  • Fig. 7 is a side view of an apex seal employed in the rotor of Fig. 6;
  • Fig. 7a is an axial view in section of the bias spring of the apex seal, taken on line 7a-7a of Fig. 8, the apex seal and spring being shown in full;
  • Fig. 8 is a diagrammatic plan view partially in section of the apex seal of the rotor of Fig. 6 acting upon the surface of the mating rotor;
  • Fig. 8a is a similar view of an apex seal with restraining means, while Fig. 8b is a side plan view of the seal with restraining means;
  • Fig. 9 is a diagrammatic view of the apex seal of Fig. 8, suggesting its movement in use;
  • Fig. 9a is a free body diagram of the apex seal member of Fig. 8.
  • Fig. 10 is a plan view on enlarged scale of a single rotor of Fig. 1, omitting the spline teeth, while Figs. 11 and 12 are partial axial cross-sectional views taken on lines 11-11 and 12-12 respectively, of Fig. 10;
  • Fig. 10a is a plan view of a rotor cut away to show the bias means,
  • Fig. 10b is a force diagram, while Figs. 11a and 12a are partially axial cross-sectional views taken on lines lla-lla and 12a-12a respectively of Fig. 10a;
  • Fig. lib is view similar to Fig. 11a of an alternative embodiment
  • Figs. 12b and 12d are enlarged representation views of the opposed rotor and fixed bore wall seals with the leak retarding system of Fig. lb
  • Figs. 12c and 12e are bar graph representations of the pressures in Figs. 12b and 12d, respectively
  • Fig. 13 is a cross-sectional view similar to
  • FIG. 1 of another preferred embodient employing three rotors
  • Fig. 14 and 15 are views of an identical pump structure adapted, respectively, by virtue of opposite rotation, to compress or expand the chamber;
  • Figs. 16 through l ⁇ c are sequential diagrammatic views of the preferred embodiment of a liquid pump having stages creating suction and pressure;
  • Fig. 17 is a cross-sectional view of a further embodiment employing rotors of unequal size but of identical revolutionary speed;
  • Fig. 18 is a cross-sectional view of a three rotor machine employing small outer rotors and a larger central rotor which rotates at one half the speed of the outer rotors;
  • Fig. 19 is a top section view showing an alternate apex seal construction.
  • Fig. 20 is a diagrammatic view of an alternate embodiment of a biased force seal
  • Figs. 21 and 22 are side views taken at the lines 21-21 and 22-22, respectively thereof. Structure and Operation
  • engine block 10 is comprised of block segments 12 and 14, gear-and-bearing segments 16 and bearing segments 18.
  • Power shafts 20 and 20' extend from respective ends of block 10.
  • the exhaust and intake manifolds 22 defining exhaust passages 24 and intake passages 26 on each side of the block are formed by unitary castings which extend substantially throughout the combined height of segments 12 and 14 of block 10 and service the combustion chambers formed in these block segments.
  • Fuel injection port and/or ignition means 28 for each segment is shown in the center.
  • Bolts 30 extend through the block and hold the segments together.
  • Bolts 31 extend through blocks 16 and 18 for the same purpose.
  • Block segment 12, shown in Fig. 1 is provided with holes for bolts 30 and additional holes 34 for bolts which terminate within the segments 16, further serving to hold the block segments together.
  • Each block segment 12 defines first and second adjacent cylindrical bores 36 and 38 formed in the block segment about parallel axis A and B. As shown in Figs. 1, 2 , each block segment has a single end plate 42, with opposite surfaces 40, 40' of this end plate closing the bores formed in adjacent block segments.
  • the central block segment 14 is identical to block segment 12, except it has two sets of rotors with an intervening dividing plate 42' serving to close one side of the bores for each set of rotors.
  • the bores in the block segments at respective ends of the block are closed by additional closing plates 44. Referring to Figs. 1 and 2, the bores 36 and 38 on axes A and B are defined in each block segment 12, and on each side of block segment 14.
  • the bores have equal radius R and the axes of the bores are spaced a distance D apart, D being less than the sum of the radii of the adjacent bores, i.e. less than 2R.
  • R may be 2 inches and D may be 3 inches.
  • First and second rotors 50 and 52, respectively, are closed in bores 36 and 38, on fixed axes A and B respectively, and splined in identical angular position to rotor shafts 46 and 48, respectively, extending along those axes. (Shafts 46 and 48 are shown bored for oil feed lines.)
  • the rotor surfaces are specially constructed to form progressive rotor-to-rotor seals between the two rotors while each rotor also forms a rotor-to-bore-wall seal with the wall of its respective bore, these rotor surfaces adapted to serve as bounding surfaces in cooperation with relatively stationary surfaces of the bores to define chambers of changing volume.
  • this relationship is realized by major and minor cylindrical surfaces, C L and C s , respectively, each centered on the axis A of the rotor, and diametrically opposed, these surfaces being joined by cylindrical transition surfaces, T. and T trash, which are centered about points spaced from the axis of the rotor.
  • the major and minor cylindrical surfaces have an equal arcuate extent, and the joining transition surfaces on each of the rotor similarly have equal arcuate extent .
  • the center for each transition surface, of radius R_ is located at the apex, A_, formed at the intersection of the major cylindrical
  • the minor cylindrical surface, C g has a radius substantially equal to the difference between the length of the line of centers of the rotors, D, and the radius, R, of the major cylindrical surface of the adjacent rotor.
  • Figs. 5 through 5f engine segment 12 of Fig. 1 is shown in reduced scale through a sequence of stages.
  • Rotors 50, 52 rotate in a clockwise direction from the stage of flow of air through the engine prior to the combustion reaction in the upper chamber (Fig. 5) to the flow-through of air following combustion (Fig. 5f) .
  • the air removes exhaust gas f om the upper chamber after combustion, cools internal surfaces of the engine and provides combustion air for the next cycle.
  • rotors 50, 52 in conjunction with surfaces 37, 39 of cylindrical bores 36, 38, respectively, and intervening surface 35 form a flow-through passage (shown by arrows) for cooling air from intake 26 to exhaust 24, which is supplied, e.g., by a blower (not shown).
  • Fig. 5a shows rotors 50, 52 after clockwise rotation.
  • Rotor 52 closes intake 26, while rotor 50 closes exhaust port 24 to form closed chamber 60, the coaction of the rotors trapping a volume of the flowing fluid within the chamber, which is defined by the leading transition surface, T,, of rotor 52, the large cylindrical surface, C L , of rotor 50, the cylindrical surface 39 of chamber 38, and the intervening surface 35 joining cylindrical surfaces 37, 39 of bores 36, 38.
  • the small cylindrical surface, C s of rotor 52, contacts the large cylindrical surface of rotor 50, closing chamber 60.
  • rotors 50, 52 have rotated to decrease the volume of chamber 60, by the relative motion of leading transition surface, T L , on rotor 52 moving toward to large cylindrical surface, C ⁇ , of rotor 50, compressing the fluid in the chamber.
  • surface C being progressive parts of a constant diameter cylinder centered on axis A does not affect the volume of chamber 60 during this compression stage.
  • the seal between the two rotors is formed by the trailing apex seal, A_ F , of rotor 50 contacting the leading transitional surface T_ of rotor 52.
  • rotor 50 has come out of contact with the minor cylindrical surface, C s , and into contact with the transition surface T L of rotor 52. As the apex seal contacts the opposed transition surface the critical compression stage begins.
  • rotors 50, 52 have rotated to top center position and chamber 60, now formed by the major cylindrical surfaces, C,, of both rotors and by the intervening surface 35 that joins the cylinder bores, is at minimum size and the contained fluid is at maximum compression.
  • fuel is injected prior to this point and the air-and-fuel mixture compressed in the chamber is ignited.
  • the inertia of the spinning rotors carries the rotors through the compression phase to the point of maximum compression (Fig. 5c) .
  • the ratio of compression to expansion depends upon the arcuate locations of the points where a seal is first and last made.
  • the lip 27 of the intake manifold fairs into the cylindrical surface of the bore
  • the lip 25 of the exhaust manifold defines a cylindrical extension of the bore. Because the portions of bores 36 and 38 defined by the housing are equal, the bore extension provided by the exhaust manifold extends the expansion and the ratio of compression to expansion is therefore less than one.
  • the rotors form, with the bore surfaces 37, 35, 39, a flow-through path for flow of air from intake 26 to exhaust 24. The flow of air through this path removes combustion products, and also cools the engine.
  • each of the rotor pairs is 120° out of phase with adjacent rotors in order to form a dynamically balanced engine.
  • Segment 16 (Fig. 4) also includes an additional idler gear 74, to allow application of static torque to prevent backlash of the gears for better synchronization of the rotors. Also, use of idler gears distributes the power load for better efficiency.
  • variable members 1002 which are movable toward or away from rotors 50, 52 in a manner to vary- the rotational angle at which the sealed relationship between apex seals 82 of rotors 50, 52 and the bore surfaces 27 begin and define the maximum confined initial volume of the chamber.
  • This provides the engine with a variable compression ratio, i.e. the ratio between the volume of the combustion chamber when it is first formed (Fig. 5a) and the volume of the chamber at the time of ignition, typically approximately at the point of minimum chamber volume (Fig. 5c).
  • variable members 1002 are in the maximum chamber position, with arcuate surfaces 1004 disposed for initial sealing contact with seals 82 at the earliest point, e.g. as also shown in Fig. 1.
  • Downstream ends 1006 of variable members 1002 provide smooth transition onto fixed bore surfaces 1008, with surfaces 1010 contacting the curved surfaces 1012 of the fixed portions.
  • flexible fairing members 1016 also provide smoothly curved surfaces.
  • Variable member 1002 is constructed to pivot about axis V located to the right of a line between the rotor axis and the end of movable surface 1004 closest to the pivot axis V. Member 1002 is selectively positioned by means of piston 1018 on the basis of engine operating conditions.
  • the controlling condition is engine speed, with arcuate surfaces 1004 displaced to avoid early sealing contact at slower speeds, but other factors may be considered. If desired, the controlling factors can be evaluated by computer, shown in dashed line, which in turn controls the positions of surfaces 1004.
  • arcuate surfaces 1004 are disposed at positions for delayed sealing contact, (Fig. lb) .
  • an example of the compression ratio would be 3:1:10.35 (initial confined volume: minimum confined volume: final confined volume) and the peak pressure before ignition would be about 430 psia.
  • the engine would be very efficient during periods of low power need due to the enormous expansion ratio, and would be very quiet due to mild combustion shock and low pressure exhaust.
  • the exhaust pressure would be about two atmospheres versus 5 1/2 atmospheres in typical piston engines.
  • the arcuate surfaces 1004 are disposed for early sealing contact and maximum compression rates for operation at higher engine speeds.
  • a compression ratio would be 9:1:10.35, with maximum pressure about 1437 psia, for driving and accelerating power.
  • Fig. 2a a different sectional view of the rotary engine operating at low speeds is shown with variable member 1002 in retracted position, and in Fig. 3a, a chamber engine block with variable compression is shown.
  • Fig. Id another construction with the bore cylindrical surfaces 27, 39 and 25, 37 defined by variable members 1002 is shown. Hydraulic pressure is applied to surface 1014 of piston 1016 to urge it against the surface of asymmetrical cam 1018 in aperture 1020. The rotational position of cam 1018 controls the adjustment of surface defining bore 36, 38.
  • the contact surface 1004 is a soft material, e.g. • nickel, aluminum or plastic, to allow it to wear to fit. Movement of the contact surface is linear, with no provision for smooth transition between downstream surfaces.
  • high compresion engine operation e.g. above 3,000 r.p.m., the clearance between adjacent surfaces would be lowered to less than 0.001 inches (0.025 mm). It is anticipated an automobile engine equipped with this system would require, tuning only every 60,000 miles (96,500 km).
  • a single rotor 50 identical to the rotors described above, is shown in detail with spline teeth and face seal labyrinths omitted. It comprises rotor body 80 to which are attached apex seals 82 and face seals 84, 86.
  • apex seal 82 is located at the apex of the rotating surfaces of rotor 50, i.e. at the intersection of the major cylindrical surface, C ⁇ ⁇ _, and the transition surface, T.
  • Apex seal 82 is a oveable sealing member having sealing surface 90 (Fig. 8) adapted to contact the opposed surface 92 of the opposite rotor 52 and apply an outward sealing pressure against that surface.
  • Apex seal 82 has a moveable tail portion 94 that is free to slightly swing between a first position P, (Fig. 9) and a second position P 2 (shown in dashed line) about a pivot region positioned inwardly from the periphery of the rotor.
  • each apex seal 82 consists of upper and lower sealing members 81, 83 urged axially apart by corrugated spring 96 which urges face surfaces 98, 100 of members 81, 83 into sealing contact with the opposed end surfaces 40, 40' (not shown here) of bore 36. Leakage through the spring compartment is restricted by an overlap of the joint between members
  • the apex seal member 82 has an enlarged head portion 102 to which the tail portion 94 is joined.
  • Head 102 is fixed against radial movement but is allowed to rotate about axis X.
  • Aperture 88 of rotor 50 is sized with some slight clearance (C, Fig. 9, e.g. .007 inch) to allow the tail portion 94 of seal 82 to rotate slightly about the axis X between a first (rest) position P, , and a second (high speed) position P 2 - In the rest position, the tail portion 94 is biased toward position P, by spring 108 (Figs. 7a and 8) disposed in the rotor 50.
  • spring 108 is a mildly corrugated thin piece of metal.
  • Axis X of head 102 lies on a radius R of rotor 50 (Figs. 9, 10) which is offset from the center of mass of the sealing member, either considering the entire mass of the member or the mass of the non-balanced tail portion 94.
  • radius R cm __ is shown p - roj jected throug sh the center of mass cm, of the non-balanced portion.
  • spring 108 biases the tail portion 94 of seal 82 toward positon P, , Fig. 9, where sealing surface 90 exerts maximum contacting pressure on the opposing surface 92 (transition surface T) .
  • the centrifugal force has a radial component, F-_ , which has no effect on seal position, and a tangential component, F ⁇ , which tends to move the center of mass, C.,, of the seal to overcome the opposed spring force, F g , thus moving the sealing surface 90 toward position P 2 (a movement shown exaggerated in Fig. 9) .
  • This movement reduces the contacting force F cp exerted by the sealing surface 90 on the opposed surface 92 as speed increases.
  • the seal between the apex of one rotor and the transition surface of the opposed rotor be tightly maintained, e.g. to avoid leakage and lost power.
  • the spring 108 enables the apex sealing surface 90 to exert the required contact force F_ against the opposed transition surface 92.
  • seal contact pressure becomes less critical.
  • the novel seal relaxes this seal pressure and thus reduces efficiency loss that otherwise would occur due to friction. Further, the seal pressure may be made to vary with inverse relationship to the size of the chamber.
  • the effective lever arm L of the contact force F Cp is greatest in the rotor position of Fig. 5c where the chamber volume is smallest. Contrarwise, when the chamber is largest, i.e. when the seal member approaches alignment with the line of centers, between Figs. 5d and 5e, this lever arm is minimal.
  • the total sealing pressure is also affected by friction effects that are taken into account in the design, bearing in mind that though the friction force tending to drag the seal open is also lowest in the position between Figs. 5d and 5e, the effective lever arm for this force is at a maximum, and vice versa with respect to the position of Fig. 5c.
  • apex seal 82 is shown positioned in rotor 50 which in this case has an enlarged aperture 88' for head 102. Also disposed in aperture 88' is restraint or damping means 1102 which has an arcuate surface 1104 complementary to the surface 1106 of seal head 102. A biasing means (not shown) urges the arcuate surface 1104 of restraint means 1102 into friction-brake contact.
  • seal 84, and similarly seal 86 is comprised of two substantially flat, plate-form members 118, 120 at each surface, the outer surface of member 118 forming the contacting surface 122 between the rotor and the bore wall 40, 40'.
  • the inner surface 124 of member 118 and the outer surface 126 of member 120, and inner surface 128 of member 120 and surface 130 of the rotor body 80 form additional contacting surfaces.
  • the clearance between rotor surface 116 and bore surface 40 is divided into segments which are, of course, smaller than the total clearance and thus are more restrictive, due, e.g. to viscous friction, to gas flow between the opposing surfaces.
  • the surfaces of member 118 and member 120 also contain grooves 132 running substantially parallel to the cylindrical surfaces of the rotor. These grooves are divided from each other by ridges 134 of reduced clearance with the opposed surface, thus forming chambers or recesses for cascading pressure from the region of high pressure to the region of lower pressure (sometimes referred to labyrinth seals) .
  • the chambers between member 118 and the bore surface 40, 40', between members 118, 120, and between member 120 and the rotor surface 130 are also connected by means of axial holes 136, 138 which enable a balancing of pressure between the individual parts.
  • Fig. 12 is similar to Fig. 11 showing the members 118, 120 of the flat plate seals at a different position about the rotor axis. Pin 140 holds the seals 84, 86 to the rotor body 80.
  • bias means 1202 for retractably biasing face seal 84' toward a complementary bore surface is shown.
  • bias means 1202 is a relatively flat sheet of corrugated spring steel fixed at point Q to retaining pin 140' which in turn is fixed in the rotor body 80'. Face seal 84', through which retaining pin 140' passes, rests on the opposed ends 1204, 1206 of bias means 1202 which at rest urge the seal 84' into sealing contact with the complementary bore surface (not shown) . Sealing contact is achieved along surfaces 122' while most of the intervening portion of the seal is apertured (1208) to prevent pressure differential between the face seal surfaces.
  • bias means 1202 which has dimensional extent both along the rotor radius, R R , and also perpendicular thereto P R , is fixed to the rotor at point Q along the length of the bias means closer to the inner end from its center of mass.
  • centrifugal force CM
  • the portion of the spring lying inwardly at the point of attachment is also urged outward by the centrifugal force generated.
  • two bias means 1202', 1202*' may be used to bias two overlying face seals 118', 120' to divide the clearance for reduced leakage, as discussed above relative to Fig. 11.
  • a face seal 1302 without a flush radial surface is shown.
  • Arcuate face seal 1302 lies within an arcuate aperture 1304 disposed inward from the radial surface 1306 of rotor 1308.
  • seal 1302 Over its major length, seal 1302 fits into aperture 1304 with tight clearance to provide a tortuous path for gas leakage around the seal.
  • retaining pins 1310 are provided with attached bias means 1312 that apply biasing force to seal 1302 toward the complementary bore surface 1314. As discussed above, centrifugal force generated by increased rotor rotational speed cause bias means 1312 to apply reduced force to the seal.
  • a track sealing system for retarding leakage from fluid chamber 60 is shown. Defined in the
  • OMPI ⁇ NATlO surface 25 of bore 36 are a series of parallel grooves 1022 lying generally coaxial with the bore, and perpendicular to the direction of rotation of rotor 50.
  • the size, shape and arrangement of the grooves varies with application. In a typical compression engine (shown) the grooves are about 0.125 inches (3.2 mm) deep, and have approximately the same width, W. The distance between grooves Y, is about equal to W, or slightly less.
  • the relationship of the close-mated surfaces of the moving rotor and the fixed bore surface defining the grooves are shown in enlarged scale in Figs. 12b and 12d, to which we now refer.
  • chamber 60 is at a pressure, P relatively higher than port 24. Fluid under pressure in chamber 60 leaks through the gap 1024, typically between about .004 to .007 inches (0.10 to 0.18 mm) , between the moving surface of rotor 50 and the fixed bore surface 25 in the direction indicated by arrow . Leakage beyond the first groove is somewhat limited as the leaking fluid fills and pressurizes the relatively large volume, compared to the narrow gap, of the groove to a pressure, P, , approaching, but slightly below the chamber pressure P . Pressurization of the grooves occurs progressively as shown by the bar graph of pressure in Fig. 12c.
  • a second chamber 160a, 160a' (only chamber 160a' in the lower phase is shown) is formed simultaneously in each stage of rotation, i.e. in Fig. 13 the engine is forming two compression chambers 160' and 160a'.
  • a flow-through path from intake 126 to exhaust 124 is formed across the top of the rotors again as in Fig. 1.
  • An engine of this embodiment would typically provide greater power output for the weight of engine machinery required, as compared to the embodiment of Fig. 1.
  • Fig. 14 shows a fluid pressure pump 210.
  • fluid taken into the engine through intake 226 is pressurized in chamber 260 by action of rotors 250, 252.
  • Valving means 228 remains closed until the desired degree of compression of the fluid in chamber 260 is achieved, e.g. if the fluid is substantially noncompressible, e.g. water, valving means 228 will open almost immediately and the compressive action of the device will be used to squeeze the liquid forcefully through exit port 224. If the fluid is compressible, valving means 228 will remain closed until the fluid is substantially compressed, e.g. until rotor 250 and rotor 252 reach a point close to maximum compression.
  • Compression in chamber 260 is achieved by the combined action of the rotors 250 and 252 with the cooperative surfaces of engine 210 to reduce the size of chamber 260 to its minimum point.
  • a similar process would occur in the lower phase, i.e. 180° out of phase with the process just described, with the valving means 228* acting to allow compressed fluid in chamber 260' to exit.
  • a device 310 similar to the fluid pressure pump of Fig. 14 is shown. However, in this embodiment the rotors 350, 352 rotate in a counter clockwise direction thus causing chamber 360 to expand in size.
  • valving means 328 activates to allow fluid to be drawn through intake 326 into chamber 360. The rotation of rotor 350 creates a lowered pressure in chamber 360 which upon opening of the valving means induces fluid to enter chamber 360. Again a similar process would take place 180° out of phase in lower chamber 360' .
  • a pump 410 with simultaneous suction and pumping phases suitable for pumping fluid e.g. for use as a circulation pump
  • the pump comprises rotors 450, 452, slightly different in configuration from the rotors of Fig. 1 to accommodate a closer spacing of the rotor axes in this embodiment (closer spacing enabling increase of pumping flow versus size of overall machine) .
  • the rotors rotate in phase in the same direction and at the same speed, and intake and exhaust ports 426, 426' and 424, 424', respectively, are provided, each with an associated one-way-valve 425.
  • intake and exhaust ports 426, 426' and 424, 424' are provided, each with an associated one-way-valve 425.
  • chamber 460 sealed by the surfaces of the rotors and the block, is decreasing in volume to force fluid out through one-way exhaust 425 and port 424 while the back volume draws fluid in primarily through intake port 426'.
  • both upper chambers 460 and 460a are at minimum volume.
  • chamber 460a is expanding in volume to draw fluid into the pump through one-way intake valve 425 and port 426 while fluid is exhausted from the back volume primarily through exhaust port 424*.
  • chamber 460a' is nearly sealed by the rotor surfaces for exhaust of fluid through valve 424'.
  • Fig. 17 shows an internal combustion engine 510 of operation similar to Fig. 1.
  • rotors 550, 552 are of different size. Both rotors move in the same direction at the same revolutionary speed, i.e. same rpm, but have different surface speeds. Operation of this device is the same as the earlier embodiments.
  • the seals of this embodiment illustrate some of the variations that can be used to advantage.
  • the seals 582 of the smaller rotor are of cantilever form, the larger root portion 502 being fixed to rotor 552, and the slender tail portions 504 being spring cantilever extensions integral with root 502, but free to deflect within a range of clearance provided by the slot in the rotor through which they extend.
  • the ends of these extensions form seals as in the previously described embodiment, Figs. 7-9a.
  • the leading seal 584 of the larger rotor in Fig. 17 is an inertial seal, specially constructed to cause the seal surface to radially retract between rest and high speed positions.
  • This seal member can form effective seals both with the rotor and bore surfaces at respective stages of rotation. This is accomplished by selected location of the seal surface and the center of the mass.
  • the radius R ' is projected from the rotor center to the pivot axis X' for the seal member.
  • the center of mass cm' of the seal member lies to one side of this radius while the sealing surface lies to the other side.
  • the center of mass cm* moves toward alignment with radius R _*__ (and toward the large cylindrical surface) while the sealing surface rotates away from that radius in the rotational direction opposite direction opposite to that of rotor 550, to a position closer to the center of the rotor 550 and away from the surfaces against which it seals.
  • both the frictional and effective intertial forces act in the same direction.
  • the trailing seal 588 is similar to seal 584 positioned in a way to be effective with the bore 537 and the opposed rotor. It also rotates, with increase in speed, in direction opposite to that of the rotor, in this case away from the large cylindrical surface, toward the following transitional surface.
  • Fig. 18 shows still another embodiment of a device 610 according to the invention.
  • three rotors 650, 652, 652* rotate in the same direction but at different rpm, e.g. center rotor 650 turns at one half the revolutionary speed of rotors 652, 652'.
  • Rotors 652, 652* are 180° out of phase, but operate at the same position on the cycle, i.e. simultaneously form compression and expansion chambers 660, 660a* with the surface of center rotor 650.
  • the small cylindrical surface may not be configured for sealing contact with the opposed large cylindrical surface, or the apex seal may not trace the point of contact with the opposed transition surface.
  • the apex seal 582 may be -in the form of a
  • OMPI cantilevered member 504 with the head portion 502 fixed against rotation also the head portion maybe fixed to the rotor surface, e.g. by a screw.
  • the labyrinth effect employed for the seals on the rotor faces could also be employed on the cylindrical surfaces by means of axially alinged recesses 532 on the major cylindrical surfaces disposed for rotor-to-bore wall sealing relationship during critical periods of compression and/or expansion.
  • the intake and/or exhaust ports could be aligned axially.
  • variable members may be used to define a portion of the bore wall on the expansion side of the machine, e.g. for an expansion machine, or may be used on both sides, e.g.
  • a rectilinear head 102' may be used on apex seal 82' to fix the bias of the flexible tail 94' in the rest position, without requiring a contact spring.
  • the damping or restraint means could be made adjustable by allowing variation of the position of the friction brake contact surface on the seal surface relative to the rotor radius, i.e. the clamping force generated is greater where the surface is perpendicular to the radius as opposed to some other angle approaching parallel.
  • he clamping or restraint means could also be used in other types of rotary devices or engines, e.g. of the Wankel type, to temporarily fix or restrain a seal to reduce contact at higher speeds.
  • the bias means sensitive to centrifugal force could be used to retract or project seals or other surfaces in other types of rotary devices or engines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Machines rotatives (10) du type ayant une chambre de fluide (60) de volume variable, p.ex. comme dans un moteur ou dans une pompe, dans lesquelles deux rotors (50, 52) tournent dans le même sens. Une surface cylindrique (CL) du premier rotor, sensiblement arquée, de rayon sensiblement égal au rayon (R) de son alésage (36, 38), est conçue pour avoir une relation d'étanchéité sur toute une plage de rotation définissant une chambre avec sa paroi de l'alésage (27, 39; 25, 37) et avec une surface du second rotor; la surface (TL, TF) du second rotor a un rayon variant progressivement pour que le volume de la chambre change progressivement pendant la rotation. Pour former des chambres multiples, chacune soumise à une compression et à une dilatation successives, chacun des rotors possède une surface de transition (TL) précédant sa grande surface cylindrique (CL) et possède une surface de transition (TF) suivant sa grande surface cylindrique, avec un joint (82) au sommet formé à chaque extrémité de chaque grande surface cylindrique. De préférence une petite surface cylindrique (CS) sur chaque rotor entre les deux surfaces de transition assure une étanchéité contre la grande surface cylindrique (CL) de l'autre rotor pendant la rotation. Utile également dans d'autres machines, le rotor porte des organes d'étanchéité mobiles (82, 84) qui appliquent une pression d'étanchéité contre une surface opposée, laquelle pression diminue avec l'augmentation de la vitesse de rotation, avec restriction (1102) pour commander le mouvement d'étanchéité. D'autres configurations d'étanchéité (1022) sont décrites. De même, un organe variable (1002) définissant une partie de la surface d'alésage est mobile par rapport au rotor grâce à des moyens sensibles aux conditions de fonctionnement désiré pour faire varier le point où le rotor et la surface commencent ou terminent une relation d'étanchéité.
PCT/US1983/001244 1982-08-26 1983-08-15 Machine rotative WO1984000993A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU19460/83A AU1946083A (en) 1982-08-26 1983-08-15 Rotary machine
PCT/US1984/000873 WO1984004943A1 (fr) 1983-06-06 1984-06-05 Machine rotative
EP19840902419 EP0146612A4 (fr) 1983-06-06 1984-06-05 Machine rotative.

Applications Claiming Priority (2)

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US41166882A 1982-08-26 1982-08-26
US50132483A 1983-06-06 1983-06-06

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4677950A (en) * 1986-01-10 1987-07-07 Norm Buske Rotary cam fluid working apparatus
WO2003089765A1 (fr) * 2002-04-16 2003-10-30 James Richard G Machine rotative a pistons

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6926200B1 (en) 1989-09-06 2005-08-09 Fujitsu Limited Electronic cashless system

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US2856120A (en) * 1954-10-16 1958-10-14 Fawzi Mohamed Ibrahim Rotary piston machine, especially for use as a compressor
FR1314527A (fr) * 1961-11-30 1963-01-11 Moteur à explosions à rotors
US3174274A (en) * 1961-12-13 1965-03-23 Reinhold A Frye Rotary engine
DE1551093A1 (de) * 1966-08-11 1970-03-19 Daimler Benz Ag Kolben einer Rotationskolben-Brennkraftmaschine
US3637332A (en) * 1970-07-28 1972-01-25 United Aircraft Corp Variable compression means for a rotary engine
US3707340A (en) * 1969-10-23 1972-12-26 Saviem Device for reducing leakage in rotary engines at low running speeds
US3768936A (en) * 1971-10-27 1973-10-30 Ramsey Corp Combination apex and side seals for rotary piston engines
US3773442A (en) * 1972-04-17 1973-11-20 Gen Motors Corp Rotary machine rotor side seal groove construction
DE2412888A1 (de) * 1974-03-18 1975-10-02 Friedrich Dr Ing Storck Dreh- bzw. kreiskolbenmaschine mit gegeneingriff der kolbenlaeufer
US3965697A (en) * 1974-03-14 1976-06-29 Beierwaltes Richard R Compressor and air cooling system employing same
US3994266A (en) * 1975-09-09 1976-11-30 Curtiss-Wright Corporation Rotary diesel engine
US4028021A (en) * 1975-12-08 1977-06-07 Curtiss-Wright Corporation Rotary trochoidal compressor with compressible sealing
US4058321A (en) * 1976-10-12 1977-11-15 Curtiss-Wright Corporation Oil seal construction for rotary mechanisms
US4087099A (en) * 1976-03-01 1978-05-02 Toyo Kogyo Co., Ltd. Oil seal means for rotary piston engines
SU909231A1 (ru) * 1980-01-18 1982-02-28 Волгоградский Политехнический Институт Торцовое уплотнение роторной машины
DE3042783A1 (de) * 1980-11-13 1982-05-19 geb. Friedhoff Gisela 4352 Herten Blusch Integrierte-walzenkolben

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2856120A (en) * 1954-10-16 1958-10-14 Fawzi Mohamed Ibrahim Rotary piston machine, especially for use as a compressor
US2845909A (en) * 1955-02-18 1958-08-05 Pitkanen Gilbert Rotary piston engine
FR1314527A (fr) * 1961-11-30 1963-01-11 Moteur à explosions à rotors
US3174274A (en) * 1961-12-13 1965-03-23 Reinhold A Frye Rotary engine
DE1551093A1 (de) * 1966-08-11 1970-03-19 Daimler Benz Ag Kolben einer Rotationskolben-Brennkraftmaschine
US3707340A (en) * 1969-10-23 1972-12-26 Saviem Device for reducing leakage in rotary engines at low running speeds
US3637332A (en) * 1970-07-28 1972-01-25 United Aircraft Corp Variable compression means for a rotary engine
US3768936A (en) * 1971-10-27 1973-10-30 Ramsey Corp Combination apex and side seals for rotary piston engines
US3773442A (en) * 1972-04-17 1973-11-20 Gen Motors Corp Rotary machine rotor side seal groove construction
US3965697A (en) * 1974-03-14 1976-06-29 Beierwaltes Richard R Compressor and air cooling system employing same
DE2412888A1 (de) * 1974-03-18 1975-10-02 Friedrich Dr Ing Storck Dreh- bzw. kreiskolbenmaschine mit gegeneingriff der kolbenlaeufer
US3994266A (en) * 1975-09-09 1976-11-30 Curtiss-Wright Corporation Rotary diesel engine
US4028021A (en) * 1975-12-08 1977-06-07 Curtiss-Wright Corporation Rotary trochoidal compressor with compressible sealing
US4087099A (en) * 1976-03-01 1978-05-02 Toyo Kogyo Co., Ltd. Oil seal means for rotary piston engines
US4058321A (en) * 1976-10-12 1977-11-15 Curtiss-Wright Corporation Oil seal construction for rotary mechanisms
SU909231A1 (ru) * 1980-01-18 1982-02-28 Волгоградский Политехнический Институт Торцовое уплотнение роторной машины
DE3042783A1 (de) * 1980-11-13 1982-05-19 geb. Friedhoff Gisela 4352 Herten Blusch Integrierte-walzenkolben

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4677950A (en) * 1986-01-10 1987-07-07 Norm Buske Rotary cam fluid working apparatus
WO2003089765A1 (fr) * 2002-04-16 2003-10-30 James Richard G Machine rotative a pistons
US6886528B2 (en) 2002-04-16 2005-05-03 Richard G. James Rotary machine

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