US3628899A - Expansible fluid rotary engine - Google Patents

Expansible fluid rotary engine Download PDF

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US3628899A
US3628899A US839012A US3628899DA US3628899A US 3628899 A US3628899 A US 3628899A US 839012 A US839012 A US 839012A US 3628899D A US3628899D A US 3628899DA US 3628899 A US3628899 A US 3628899A
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valves
fluid
cavity
outer body
valve
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Leslie C George
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    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F04C2/22—Rotary-piston machines or pumps of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth-equivalents than the outer member
    • 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
    • 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
    • F02B2730/00—Internal-combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/01—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber
    • F02B2730/018—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber with piston rotating around an axis passing through the gravity centre, this piston or the housing rotating at the same time around an axis parallel to the first axis
    • 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 engine comprises a two-lobed housing having an epitrochoidal inner surface in which is mounted a triangular rotor on an eccentric carried by a central driven shaft, the rotor and epitrochoidal surfaces forming variable-volume working chambers. lnlet and exhaust valves are disposed in the housing on opposite sides of the cusps of the epitrochoidal surfaces.
  • a timing mechanism oscillates the valves between open and closed positions to respectively admit expansible fluid into the chambers to rotate the rotor and to exhaust the expanded fluid from the chambers.
  • the valves in their closed positions have surfaces conforming to the lobe surfaces to permit the apex portions of the rotor to sweep past the valves without breaking the seal between adjacent chambers.
  • the valves are timed by a plurality of camshafts coupled to the driven shaft. The rotor can be driven in the reverse direction.
  • the present invention relates to a rotary engine and particularly relates to a fluid expansible rotary engine of the type mounting a rotor within an epitrochoidally shaped multilobed housing.
  • Rotary engines of the type having a multilobed epitrochoidal outer housing and an inner rotor having a plurality of apices equal to one more in number than the number of lobes with the rotor and housing forming variable-volume working chambers have been previously proposed and constructed for use as internal combustion engines and are commonly known as Wankel engines.
  • Wankel engines having a generally triangular rotor having three apices and rotatable in a two-lobed epitrochoidal housing, there is usually a suction stroke, a compression stroke, an expansion stroke and a discharge stroke, with the shaft making three revolutions for every complete revolution of the rotor.
  • a rotary engine of the type having a rotor rotatable on an eccentric and within an epitrochoidal-shaped housing has many distinct advantages over the common internal combustion engine by virtue of its unique geometry and configuration.
  • the present invention therefore provides a rotary engine of this geometry and configuration for use with an expansible fluid, such as steam, freon and the like.
  • an expansible fluid such as steam, freon and the like.
  • inlet and exhaust valves are required and are provided on opposite sides of the cusps separating adjacent lobes of the epitrochoidal multilobed chamber. Operation of these valves requires a controlled opening and closing of these valves such that the expansible fluid can expand to drive the rotor and exhaust.
  • the inlet valve must be opened at the end of an exhaust stroke to admit the expansible fluid into a working chamber and then closed to permit the fluid to expand and drive the rotor.
  • the exhaust valve must be timed to open at the end of the expansion stroke and then closed prior to complete evacuation of the exhaust vapors to insure recompression equal to the pressure of the incoming pressure fluid.
  • the apex portions of the rotor must make continuous sealing contact with the surfaces of the epitrochoidal chamber to avoid leakage between adjacent chambers.
  • the present invention provides a rotary engine having the previously described geometry and configuration and including cylindrically shaped oscillating inlet and exhaust valves having slots extending diametrically therethrough.
  • the slot In the open position of each inlet valve, the slot provides communication between an associated variablevolume working chamber and a source of expansible fluid under pressure.
  • the slot In the valve open position of each exhaust valve, the slot provides communication between the working chamber containing the expanded fluid and reservoir. Portions of the valves, when open, extend through the chamber surface and project into the working chamber.
  • an arcuate axially extending cutout is formed in the cylindrical surface of the valve to correspond and conform to the shape of lobed surface of the epitrochoidal shaped housing.
  • the cutout is circumferentially spaced from the slot about the cylindrical valve member.
  • a timing mechanism is provided to oscillate the cylindrical valves between open and closed positions whereby the expansible fluid can be admitted and exhausted in synchronism with the rotor cycle.
  • camshafts coupled to the engine output or driven shaft carry cam surfaces which cooperate with push rods, which, in turn engage spring-biased levers carried by the cylindrical valves whereby the axial displacement of the push rods cause the levers to oscillate the valves between open and closed positions.
  • the period of fluid admission is adjustable to facilitate engine starting.
  • the cam surface on the camshaft is cut away at an angle.
  • the cam surface is selectively positioned to a greater or lesser circumferential extent below the push rod associated with the inlet valve whereby the inlet valve may be held open for a selected period of time.
  • each of the camshafts carries a pair of cam surfaces.
  • the camshafts are axially displaced such that one of the cam surfaces is engageable with the push rods operating the associated inlet or exhaust valves in a manner to permit operation in one direction.
  • the timing of the valves can be reversed to permit rotation of the rotor in the opposite rotary direction. That is to say, the valves employed as inlet and exhaust valves for rotating the rotor in one direction can be employed as exhaust and inlet valves respectively for rotating the rotor in the opposite direction.
  • FIG. 1 is a cross-sectional view of an expansible fluid rotary engine constructed in accordance with the present invention
  • FIG. 2 is a cross-sectional view thereof taken generally about on line 2-2 in FIG. 1;
  • FIG. 3a-3d are reduced cross-sectional views similar to FIG. 1 illustrating the rotor in various operating positions:
  • FIG. 4 is an end elevational view of a timing mechanism em ployed with the expansible fluid rotary engine hereof;
  • FIG. 5 is a fragmentary elevational view of a timing camshaft employed with the engine hereof;
  • FIG. 5a is a schematic illustration of an expansible fluid circuit for operating the engine in a reverse direction
  • FIG. 6 is a schematic end elevation view of a further form of timing mechanism employed with the engine hereof;
  • FIG. 7 is a fragmentary elevational view of the timing mechanism illustrated in FIG. 6.
  • FIG. 8 is a cross-sectional view of an expansible fluid rotary engine constructed in accordance with the present invention and having a mixed pressure operation.
  • a trochoidal-type rotary engine having an outer body comprising a two-lobed peripheral housing 12 with a basically epitrochoidal inner surface 14 defining lobes 14a and 14b and a pair of end walls 16 and i8 as seen in FIG. 2.
  • a shaft 20 extends longitudinally through the engine housing and is suitably joumaled in end walls 16 and I8.
  • Shaft carries an eccentric portion 22 which is received in a rotor 24, the eccentric 22 serving as a crank as the rotor 24 rotates.
  • Rotor 24 is generally triangular in outline as viewed in an axial direction having three apex portions 30a, 30b and 300 each carrying an apex seal 32a, 32b and 320.
  • the seals 32 of rotor 24 define, with portions of the inner epitrochoidal surfaces 14 and the arcuate surfaces 34A, 34B, and 34C of the rotor 24 three variable-volume working chambers A, B and C. Cutout portions 36 are recessed from each of the surfaces 34 for the transfer of expansible fluid across the cusps of the epitrochoidal-shaped chamber.
  • the housing 12 may be fonned of a casting or the like.
  • a plurality of longitudinally extending bores 38 are formed through housing 12.
  • a pair of bores 38 are provided on opposite sides of each epitrochoidal surface 14 and on opposite sides of each cusp.
  • the bores 38 are formed such that portions of their peripheries open through the surfaces 14a and 14b of the epitrochoidal chamber and form slots therein.
  • Longitudinally extending reduced diameter bores or passages 40 are also formed through housing 12, outwardly of and in communication with bores 38.
  • a pair of cylindrically expansible fluid inlet valves 421 and 441 are provided in diametrically opposed bores 38 and a pair of similar cylindrical exhaust valves 46E and 48E are provided in the other pair of diametrically opposed bores 38.
  • each of the valves 421, 441, 46E and 48E is provided with a through diametrically extending slot 50.
  • Valves 421, 441, 46E and 48E are suitably mounted for rotation in end walls 16 and 18 and are provided with suitable seals, indicated at 52 in FIG. 2. It will be appreciated that the passages 40 and the slots 50 are arranged such that when the valves 421, 441, 4615 and 4813 are rotated to positions wherein the slots 50 open into chambers A, B and C, the opposite ends of the slots open into the axially extending cylindrical passages.
  • the passages 40 associated with the inlet valves 421 and 441 communicate through an aperture, not shown, in end wall 16 with a source of expansible fluid under pressure.
  • the passages 40 associated with the exhaust valves 4613 and 48E communicate through an aperture 54, as seen in FIG. 2, formed in end wall I6, the aperture 54 preferably communicating with a fluid reservoir, not shown. Accordingly, when the valves 421 and 4612 are disposed in the positions illustrated in FIG. I, expansible fluid under pressure is admitted from passage 40 through the slot 50 in valve 421 into working chamber A, while the expansible fluid in working chamber B is exhausted therefrom through the slot 50 in valve 46E into its associated passage 40. It will be appreciated that communication through these valves to their associated passages 40 is precluded when they are rotated to valve positions exemplified by the positions of closed valves 441 and 4813 in FIG. 1.
  • rotor 24 rotates within the epitrochoidal chamber with the seals 32 sweeping along the epitrochoidal surfaces 14a and 14b in continuous sealingengagement therewith.
  • Each seal 32 is disposed in a recess 61 formed in the associated apex portions 30 of the rotor 29 and comprises, as seen in FIG. 2, an elongated strip including a main body 60 formed by a very lightweight metal and having a tip 62 formed of a plastic material such as nylon or teflon. The tip material provides a wearing surface bearing against the inner walls and 14b of the epitrochoidal chamber.
  • a plurality of helical springs 64 are located between each seal strip and the base of its associated recess 61 whereby seal strips 32 are biased outwardly into constant sealing engagement with the epitrochoidal surfaces 14a and 14.
  • valves 421, 441, 4613 and 4815 are specifically configured such that, when these valves lie in a valve closed position, they form with the adjacent epitrochoidal surfaces 140 and ll4b a smooth, continuous and unbroken surface. This permits the apex seals to remain in sealing engagement with the walls of the epitrochoidal chamber even as the seals sweep past the valves.
  • each of the cylindrical valve members 421, 441, 46B and 4813 is provided with an arcuate cutout portion 66 extending axially along its periphery and corresponding in curvature to and forming a continuation of the curvature of the associated epitrochoidal surfaces 14a and 14b.
  • surfaces 66 complement the epitrochoidal surfaces 140 and 14b when the valves are disposed in a closed position, i.e., the valves 441 and 4813 in FIG. 1, whereby the apex seals 62 remain in constant sealing engagement along the surface 140 and 1411 as they sweep past the slots accommodating the valves and formed through the chamber wall.
  • valves 421 and 46E are open and valves 441 and 48E are closed.
  • Valve 421 accordingly admits expansible fluid under pressure from associated passage 40 into chamber A, the latter being defined between the rotor surface 34A and the wall portion of surface 14a and 14b between apex seals 32a and 32c.
  • Valve 46B is open permitting chamber B to exhaust through the valve into its associated passage 40, chamber B being defined between the rotor surface 34b and the wall portion of surfaces 14a and 14b between the apex seals 32a and 32b.
  • Valves 441 and 48E have just closed and the chamber C defined by rotor surface 340 and the portion of surfaces 14a and 14b between apex seals 32b and 320 contains expansible fluid admitted from its associated passage 40 when valve 441 was open.
  • the fluid in chamber C expands to drive rotor 24 in a counterclockwise direction thereby also driving output shaft 20 in a counterclockwise direction.
  • the valve 421 has rotated to a closed position. Note that, in the movement of rotor 24 from the position illustrated in FIG. 3a to the position illustrated in FIG.
  • valve 465 remains in the open position exhausting chamber B.
  • the valve 48E has rotated to an open position exhausting chamber C.
  • rotor 24 is driven by the expansion of the fluid in chamber A with the rotor obtaining the position illustrated in FIG. 30.
  • the valve 46E has rotated to a closed position and the valve 44I has rotated to an open position to admit fluid into chamber B. Chamber C continues to exhaust the fluid through the open valve 48E.
  • cylindrical valves 421, 441, 46E and 48B oscillate about their longitudinal axes between positions admitting fluid into and exhausting fluid from the working chambers and positions wherein the arcuate surfaces 66 form continuations of epitrochoidal surfaces 14a and 14b.
  • a timing mechanism is provided and illustrated in FIGS. 4 and 5.
  • the cylindrical valves extend through the end wall 18 of the engine housing and carry lever arms 70. Springs 72 engage between lugs 74 fixed to the engine housing and the lever arms 70 thereby biasing the valves into normally closed positions. Levers 70 bear against adjusting screws 76 in the valve closed positions.
  • Push rods 78 are slidably carried by the housing and engage the ends of associated levers 70, the opposite ends of push rods 78 carrying rollers 77 for hearing against associated camshafts 80.
  • Each camshaft 80 mounts a pair of projecting cams 82a and 82b at axially spaced positions therealong.
  • the camshafts 80a associated with inlet valves 42] and 44[ carry cams 82a and 82b as illustrated in FIG. 5, while the camshafts 80b associated with the exhaust valves 46E and 48B carry cams 82a and 82b in an axially reversed position, not shown. That is to say, each cam 82a on camshafts 80b is located in the position occupied by cam 82b in FIG.
  • cams 82a and 82b are normally associated with the inlet and exhaust valves respectively.
  • the camshafts 80 are slidably carried by the engine housing, by means not shown, and carry sprockets 84 splined to the camshafts 80.
  • An external portion of the driven shaft mounts a similar sprocket 86 in FIG. 4 and a drive chain 88 connects between the drive sprocket 86 and the driven sprocket 84.
  • a chain drive 87 encompasses the four sprockets 84 whereby the camshafts are driven in a time relation to the driven shaft 20.
  • the cams 82a are substantially triangular in shape having a base surface portion 89 and a hypotenuse surface 90 for reasons noted hereinafter.
  • the rollers 77 on the end of push rods 78 associated with the inlet valves engage cams 82a and ride up base surfaces 89 and over the cams to displace the push rods. This, in turn displaces levers 70 thereby pivoting the associated inlet valve.
  • the rollers on push rods 78 drop off the cam surfaces 90 back onto the camshafts 80a whereby springs 72 pivot levers 70 and the associated valves in the opposite direction into the normally closed valve positions.
  • camshafts 80b and cams 82b associated with the exhaust valves operate in a like manner with the cams 82b similarly causing displacement of the exhaust rods and levers corresponding oscillation of the exhaust valves is effected. It will, of course, be appreciated that the camshafts are initially positioned such that the cams are disposed in various circumferential positions in relation to the associated push rods whereby the proper timing cycle is effected.
  • cams 820 are triangular in shape, as previously described.
  • the period in which the cams 82a displace the push rods and hence maintain the inlet valves in an open position can be varied.
  • each of the camshafts is axially displaceable by means of a pivoted actuating lever 92 which has a yoke portion 94 engageable with a collar 96 carried on camshaft 80.
  • the opposite end of the lever 92 is reciprocated by means of a fluid-actuated cylinder 98. Accordingly, to extend the period of admission, the fluid-actuated piston is extended to pivot lever 92 in a clockwise direction as seen in FIG. 5 thereby to displace camshaft 80 to the right. By thus displacing camshaft 80, a circumferentially greater surface of cam 82a is disposed below roller 77 whereby the associated inlet valve is maintained in an open position for an extended period of time. This is particularly desirable during starting torque with the period of admission being curtailed or shortened by axially displacing the camshaft 80 to the left as seen in FIG. 5 as the rotor begins to turn.
  • the inlet valves would be maintained in their normally closed positions whereby the engine would stop.
  • the cams 82b associated with the exhaust valves are rectangular in shape about camshafts 80 whereby axial displacement of the latter to vary the period of admission has no effect on the period during which the exhaust valves remain open.
  • the cylinders 98 can be operated, as by suitable valving, not shown, to jointly advance and retract the camshafts 80.
  • each camshaft 80 is shifted axially in a like direction such that the cam surfaces 820 underlying the push rods 78 associated with the inlet valves and the cam surfaces 82b, underlying the push rods 78 normally associated with the exhaust valves, are moved to inoperative positions with the cams 82a on shafts 80b and the cams 82b on shafts 80a being moved to positions underlying the push rods 78.
  • the timing action for the valves would be reversed, that is, the valves 42[ and MI become the exhaust valves and the valves 46E and 48B become the expansible fluid admission valves.
  • Suitable valving for example, the valving arrangement shown in FIG. 5a, is provided to provide the expansible fluid under pressure to the passages 40 associated with valves 46B and 48E and to exhaust the fluid from the passages 40 associated with the valves 42l and 441.
  • a closed cycle operation is shown with the expansible fluid source being indicated at S.
  • the supply and exhaust conduits indicated at 91 and 93 respectively communicate through a four-way two-position valve 95.
  • the fluid is supplied through valve to the valves 42I and 441 via passages 40, and conduit 97.
  • the exhaust fluid is returned to the source S via passage 99 from the valves 46E and 48E.
  • the fluid is supplied to the valves 46E and 48E via conduit 99 and the exhaust fluid is returned to the source S via conduit 97.
  • the expansible fluid can be selectively provided to valves 42], 44I or 46E, 48E as desired with the expanded fluid being returned through the other set of valves.
  • a pair of triangularly shaped earns 82:: and 82a are spaced along a single camshaft I00.
  • a pair of cam surfaces 82!; and 82b are spaced one from the other between the cam surfaces 824 and 821;.
  • the position of the camshaft I illustrated in FIG. 7 corresponds to the position of the rotor 24 illustrated in FIG. 3a. That is to say, the inlet valve 42I is open as it has been pivoted by the displacement of push rod 78 riding on the cam 82a. As seen in FIG. 7, the push rod 78 associated with the exhaust 48E rides on camshaft 100 whereby the valve lies in its normally closed position. Upon further rotation of the camshaft 100, the camshaft 82:: rotates beyond lever 78a whereby the spring 72 biases lever 70 against screw 76 thereby to pivot inlet valve cylinder 421 back to its normally closed position illustrated in FIG. 3b.
  • cam surface 82 will have rotated to a position below the push rod 78 associated with valve 48E to thereby open the valve as illustrated in FIG. 3b.
  • a camshaft 100 of this type is provided on each side of the engine housing.
  • the camshafts 100 of the embodiments of FIGS. 6 and 7 can be axially displaced to both alter the period of admission of expansible fluid into the working chambers as previously described and also to reverse the function of the admission and exhaust valves, i.e., to operate the admission valves 42! and 4141 as exhaust valves and to operate the exhaust valves 46E and 488 as admission valves thereby to reverse the engine. This is accomplished by axially displacing both camshafts 100 to the left as seen in FIG. 7 such that the left hand push rod 78 engages the cam 82b and the other right-hand push rod 78 engages the cam 82a.
  • Expansible fluid is then provided the passages 40 associated with valves 46E and 48E by shifting the valve 95 as previously described.
  • the camshafts can be axially shifted to both alter the period of admission and to reverse the engine.
  • valve 95 can be provided between the valve 95 and the camshaft action such that one .cannot be actuated without the other.
  • the expandible fluid rotary engine hereof can also be employed as a mixed pressure engine. That is to say, expansible fluid at two different pressures from two different sources, can be utilized simultaneously in the same engine.
  • FIG,. 8 there are provided two additional valves, an inlet valve llol and an inlet valve 112I lying closely adjacent and beyond the inlet valve 421 and MI, respectively.
  • These valves are identical in construction to the valves previously described and include diametrically extending slots 50 and arcuate sur face portions 66 conforming to the walls of the epitrochoidal chamber.
  • valves IIOI and 112] lie in communication with an expansible fluid source, not shown, at a pressure lower than the pressure of the fluid supplied to the passages 40 associated with inlet valves 4l2l and 441.
  • the valves IIOI and 112] are timed such that they remain in a closed position when the high-pressure expansible fluid in the chambers defined in part by the arcuate surfaces 60 of the valves IIOI and 112i is expanding after having been admitted through the valves 421 and 44] respectively. That is to say, the valves 1101 and Il2l are maintained in a closed position while the high-pressure fluid is first admitted into the associated working chamber as previously described. The high-pressure fluid inlet valve is then closed by the previously described timing mechanism.
  • valve llOI and 1121 When the pressure in the working chamber is reduced to a pressure substantially equal to or less than that of the lower pressure expansible fluid in passage 40, the valve llOI and 1121, as the case may be, opens to admit the lower pressure expansible fluid and then immediately closes. In this fashion, the expansible fluid in the chamber will continue to expand and rotate rotor 24 in a like direction as in the previ ous embodiments.
  • the timing mechanism for the valves Il0I and ll2I can be identical to the single-camshaft timing devices illustrated in FIG. 5.
  • the cams associated with mixed pressure operating camshafts are reduced in circumferential extent in comparison with the cam surfaces 821: whereby the period of admission for the lower pressure inlet valves IIOI and 1121 would be substantially reduced.
  • a further feature of the present invention provides for ready inspection and replacement of the apex seals at the apex por tions of the rotor when necessary without dismantling the engine.
  • the wear on these seals is much less than the wear associated with apex seals in internal combustion engines.
  • the seals should be replaced.
  • a plurality of end covers 120 are provided about end wall 16 and suitably secured thereto the bolts 122 one end cover would be sufficient.
  • These end covers preferably comprise material iron or steel plugs with seal of neoprene or such plugs having inner faces which lie flush with the inner surfaces of end plate 16.
  • a tapped hole I24 is provided in the end of the apex seals whereby a bolt or screw can be threaded into the tapped hole and the seal including the springs withdrawn from apex recesses 61.
  • the seals can be inspected and replaced without dismantling the end pieces or plates.
  • a compound rotor comprising a pair or rotors on a common shaft can be provided, as schematically illustrated in FIG. 3d.
  • the rotors are angularly offset one from the other, preferably at 45 whereby at least one of the inlet valves of one of the rotors would lie in a position to admit fluid into the working chamber and thereby drive the compounded rotor assembly.
  • the rotary engine hereof can be employed in a multilobed epitrochoidal housing mounting a rotor having one more side than the number of lobes.
  • the present invention can be employed with a three-lobe epitrochoidal housing mounting a substantially square rotor.
  • exhaust valves are mounted on opposite sides of the cusps of the epitrochoidal chamber. Similar timing arrangements could be there employed, for example, utilizing a single camshaft for each valve or one camshaft for a pair of inlet and exhaust valves.
  • a closed cycle can be employed utilizing freon 12 as the expansible fluid.
  • Expansible fluids such as hexafleurobenzine or freon 12 as well as other fluids which are expansible from a high to a low pressure such as steam can also be employed.
  • the present invention could be employed as a pump or blower, if desired.
  • a rotary mechanism utilizing a fluid comprising: an outer body having a cavity, an inner body received within said outer body cavity, means including a shaft for mounting said inner body within said outer body cavity for relative rotation therein with the axis of said inner body being laterally spaced from and parallel to the axis of said outer body cavity and said shaft, said inner and outer bodies having respectively facing outer and inner peripheral surfaces defining a plurality of variablevolume working chambers, the inner peripheral surfaces of said outer body cavity having a multilobed epitrochoidal shape with said lobes being equally spaced about the axis of said outer body cavity, the outer peripheral surfaces of said inner body including a plurality of apex portions spaced circumferentially about the inner body axis and engageable with the inner peripheral surfaces of said outer body cavity to form seals between adjacent working chambers, said apex portions being one more in number than the number of said lobes, first and second valves carried by said outer body and spaced one from the other about the inner surface of said outer body cavity, said
  • a mechanism according to claim 2 including means coupling said timing means to said shaft whereby said valves are movable between open and closed positions in accordance with rotary position of said inner body in said outer body cavity, said members being carried by said outer body for rotation about axes generally parallel to the axis of rotation of said inner body and said shaft, each of said members including a passage opening into said cavity when said valves lie in open position, each of the continuing surfaces of said members being spaced circumferentially about said member from passage opening.
  • each of said apex portions has a recess, a seal strip disposed in said recess and a spring carried within said recesses for continuously biasing said seal strip outwardly into engagement with the inner surface of said outer body and the continuing surfaces of said members as said inner body rotates within said cavity.
  • outer body includes an end wall having an opening in transverse alignment with the path transcribed by said seal strips as said inner body rotates within said cavity and a member releasably secured in said opening to provide access through said outer body to said seal strip.
  • a mechanism according to claim 1 including means coupling said timing means to said shaft whereby said valves are movable between open and closed positions in accordance with the rotary position of said inner body in said outer body cavity.
  • a mechanism according to claim 1 wherein said mechanism comprises a fluid expansible rotary engine, means for supplying expansible fluid under pressure to said first valve for admission into said working chambers when said first valve lies in said open position to thereby rotate said inner body in one direction, and means for receiving the fluid issuing from said working chambers through said second valve when said second valve lies in said open position.
  • a mechanism according to claim 8 including means for selectively varying the period of fluid admission into said working chambers.
  • a mechanism according to claim 8 including means for supplying expansible fluid under pressure to said second valve for admitting of fluid into said working chambers when said second valve lies in the open position to thereby rotate said rotor in the opposite direction, means for receiving fluid issuing from said working chambers through said first valve when said first valve lies in said open position and means for adjusting said timing means to provide for movement of said first and second members to said open position to respectively exhaust and admit the fluid from said chamber.
  • timing means includes means for oscillating said valves between said open and closed positions.
  • timing means include a camshaft carrying a cam, means coupling said camshaft to said first-mentioned shaft to rotate said camshaft, a cam follower engageable with said cam, and means coupling said cam follower and at least one of said valves to oscillate said one valve in response to rotation of said camshaft.
  • a rotary mechanism utilizing a fluid comprising: an outer body having a cavity, an inner body received within said outer body cavity, means including a shaft for mounting said inner body within said outer body cavity for relative rotation therein with the axis of said inner body being laterally spaced from and parallel to the axis of said outer body cavity and said shaft, said inner and outer bodies having respectively facing outer and inner peripheral surfaces defining a plurality of variable-volume working chambers, the inner peripheral surfaces of said outer body cavity being multilobed with said lobes being equally spaced about the axis of said outer body cavity, the outer peripheral surfaces of said inner body including a plurality of apex portions spaced circumferentially about the inner body axis and engageable with the inner peripheral surfaces of said outer body cavity to form seals between adjacent working chambers, said apex portions being one more in number than the number of said lobes, first and second valves carried by said outer body and spaced one from the other about the inner surface of one of said lobes, third and fourth valves
  • each of said members in said closed position has a surface forming a continuation of the shape of the respective lobal surfaces of the inner surface of said outer body to permit the apex portions of said inner body to sweep past in sealing engagement therewith as said inner body rotates about the outer body cavity.
  • each of said members in said closed position has a surface forming a portion of the surface defining the associated variable-volume working chamber, the apex portions of said inner body forming a seal with said member along the surface thereof as said apex portions sweep past said member when said inner body rotates about the outer body cavity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US839012A 1969-07-03 1969-07-03 Expansible fluid rotary engine Expired - Lifetime US3628899A (en)

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3744940A (en) * 1971-12-16 1973-07-10 Curtiss Wright Corp Rotary expansion engine of the wankel type
US3847514A (en) * 1973-11-19 1974-11-12 Curtiss Wright Corp Self-starter system for single rotor rotary expansion engine
US3869863A (en) * 1973-03-22 1975-03-11 Mark A Juge Rotary steam vapor and external combustion engine
US4215533A (en) * 1976-09-03 1980-08-05 The United States Of America As Represented By The Secretary Of The Navy Rotary expander engine
DE3002170A1 (de) * 1980-01-22 1981-07-23 Borsig Gmbh Regelbarer kreiskolbenverdichter
US4410299A (en) * 1980-01-16 1983-10-18 Ogura Glutch Co., Ltd. Compressor having functions of discharge interruption and discharge control of pressurized gas
WO1988001696A1 (en) * 1986-09-05 1988-03-10 Duffy James T Trochoidal gas processing devices
US5165238A (en) * 1991-05-21 1992-11-24 Paul Marius A Continuous external heat engine
US5362219A (en) * 1989-10-30 1994-11-08 Paul Marius A Internal combustion engine with compound air compression
US20060065233A1 (en) * 2004-09-24 2006-03-30 Wontech Co. Ltd. Rotary engine
US20160252010A1 (en) * 2011-07-28 2016-09-01 Pratt & Whitney Canada Corp. Rotary internal combustion engine with removable subchamber insert

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022134313A1 (de) * 2022-12-21 2024-06-27 Technische Universität Dresden, Körperschaft des öffentlichen Rechts Expansions-Verdichtungs-Vorrichtung und Verfahren zum Betreiben der Expansions-Verdichtungs-Vorrichtung in einem Kreisprozess

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US351957A (en) * 1886-11-02 Rotary engine
US667323A (en) * 1899-12-26 1901-02-05 Louis C Krummel Rotary engine.
US1305155A (en) * 1919-05-27 Xhtbmtal-cohbijstion etoote
US1874247A (en) * 1927-03-02 1932-08-30 R F Bicknell Rotary gas engine
US2742882A (en) * 1951-02-27 1956-04-24 Leo F Porter Rotary-turbine-explosion type engine
US2905095A (en) * 1957-09-16 1959-09-22 Hartmann Mfg Company Fluid pump or motor with fluid pressure balancing means
GB989588A (en) * 1962-08-30 1965-04-22 Rene Linder Rotary fluid delivering machine
CA717315A (en) * 1965-09-07 Hoppner Ernst Rotary combustion engine
US3347213A (en) * 1964-11-20 1967-10-17 Nsu Motorenwerke Ag Rotary combustion engine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US351957A (en) * 1886-11-02 Rotary engine
US1305155A (en) * 1919-05-27 Xhtbmtal-cohbijstion etoote
CA717315A (en) * 1965-09-07 Hoppner Ernst Rotary combustion engine
US667323A (en) * 1899-12-26 1901-02-05 Louis C Krummel Rotary engine.
US1874247A (en) * 1927-03-02 1932-08-30 R F Bicknell Rotary gas engine
US2742882A (en) * 1951-02-27 1956-04-24 Leo F Porter Rotary-turbine-explosion type engine
US2905095A (en) * 1957-09-16 1959-09-22 Hartmann Mfg Company Fluid pump or motor with fluid pressure balancing means
GB989588A (en) * 1962-08-30 1965-04-22 Rene Linder Rotary fluid delivering machine
US3347213A (en) * 1964-11-20 1967-10-17 Nsu Motorenwerke Ag Rotary combustion engine

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3744940A (en) * 1971-12-16 1973-07-10 Curtiss Wright Corp Rotary expansion engine of the wankel type
US3869863A (en) * 1973-03-22 1975-03-11 Mark A Juge Rotary steam vapor and external combustion engine
US3847514A (en) * 1973-11-19 1974-11-12 Curtiss Wright Corp Self-starter system for single rotor rotary expansion engine
US4215533A (en) * 1976-09-03 1980-08-05 The United States Of America As Represented By The Secretary Of The Navy Rotary expander engine
US4410299A (en) * 1980-01-16 1983-10-18 Ogura Glutch Co., Ltd. Compressor having functions of discharge interruption and discharge control of pressurized gas
DE3002170A1 (de) * 1980-01-22 1981-07-23 Borsig Gmbh Regelbarer kreiskolbenverdichter
WO1988001696A1 (en) * 1986-09-05 1988-03-10 Duffy James T Trochoidal gas processing devices
US5362219A (en) * 1989-10-30 1994-11-08 Paul Marius A Internal combustion engine with compound air compression
US5165238A (en) * 1991-05-21 1992-11-24 Paul Marius A Continuous external heat engine
US20060065233A1 (en) * 2004-09-24 2006-03-30 Wontech Co. Ltd. Rotary engine
US7434563B2 (en) * 2004-09-24 2008-10-14 Wontech Co., Ltd. Rotary engine
US20160252010A1 (en) * 2011-07-28 2016-09-01 Pratt & Whitney Canada Corp. Rotary internal combustion engine with removable subchamber insert
US10544732B2 (en) * 2011-07-28 2020-01-28 Pratt & Whitney Canada Corp. Rotary internal combustion engine with removable subchamber insert

Also Published As

Publication number Publication date
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