US3769796A - Rotary heat engines - Google Patents

Rotary heat engines Download PDF

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US3769796A
US3769796A US00206779A US3769796DA US3769796A US 3769796 A US3769796 A US 3769796A US 00206779 A US00206779 A US 00206779A US 3769796D A US3769796D A US 3769796DA US 3769796 A US3769796 A US 3769796A
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engine
gear
rotary
boiler
housing
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M Bechtold
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EIDP Inc
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EI Du Pont de Nemours and Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/04—Plants characterised by the engines being structurally combined with boilers or condensers the boilers or condensers being rotated in use

Definitions

  • a rotary closed Rankine cycle engine including rotary closed housing containing a boiler and an expander, and a condenser connected to the housing, all rotatable as a unit about a common axis.
  • the boiler is of annular construction and the housing and boiler are rotationally driven at a predetermined speed to maintain in the boiler an annular body of liquid having a liquid/vapor interface spaced a predetermined distance radially outward from the engine axis.
  • the condenser is mounted coaxially adjacent the housing to rotate therewith as a unit about the engine axis.
  • the expander actuates a coaxial driving member in the rotary housing and an occluded fixed ratio gear train mounted coaxially within the rotatable housing is driven by the expander driving member and connected to and communicating with the rotary housing-boiler-condenser unit to rotationally drive the latter at said predetermined speed.
  • An external drive member is connected to the rotary housing and rotationally driven thereby, and means is provided opposing the reaction torque generated by the internal gear train so that the power output of the expander is transmitted directly to the rotary housing and the external drive member.
  • This invention relates to rotary heat engines, and more particularly to rotary heatcngines of the closed Rankine cycle type especially adapted for use with high molecular weight power fluids.
  • Rotary heat engines of the type set forth comprising a rotatable closed housing, containing an annular boiler with attached internal condenser unit and an expander are known in the art.
  • An example of such an engine is disclosed in US. Pat. No. 3,613,368 issued Oct. 19, 1971.
  • Prior to the present invention, and as shown in the aforesaid patent it has been the practice to rotationally drive the rotary boiler-condenser unit independently of the primary power output of the engine, for example, by means of a rotary power source that is entirely separate and apart from the Rankine engine.
  • Such an arrangement is comparatively complexand requires the provision of an independent rotary power source for continuously driving the boiler-condenser unit that is in-addition to and indirectly split from the total power developed by the Rankine engine.
  • the provision of some means, such as a brake is required to absorb or use the excess power delivered .to .therotary boiler-condenser unit over that required to rotationally drive'said unit.
  • control systems for such an arrangement are complex.
  • the rotary housing lboilencondenser unit of the Rankine engine is internallycoupled mechanically to the internal expander driving member so that, except at start-up of the engine, the "housing-boilercondenser unit is rotationally driven continuously by the primary power output generated by the engine.
  • the principal advantage of the present invention lies in its simplicity and the fact that the proportion ofthetotal power generated required to rotationally drive the housing-boiler-condenser unit is automatically split-off from the total power developed by the engineand the *balance, of the power is applied directly to the externalfload on the engine.
  • the present invention contemplates' the internal'mechanical coupling of the rotary housing-boiler-condenser unit to the internal expander driving members through an internal fixed-ratio gear I train .so that the boiler-condenser unit is rotationally driven at a constant ratioto the speed of the expander.
  • An advantage of this is that when the expander is a full admission nozzle turbine, the turbine can operate at the engine controlled by regulation of the rate that fuel is supplied to the combustion chamber to heat the .boiler liquid.
  • the expander will operate at peak efficiency at all power levels.
  • engine accesseries are driven at constant speed independent of the engine power level.
  • an object of the invention is to provide a rotary heat engine of the type dc scribed comprising a closed rotary housing and boiler having an internal expander and an internal mechanical coupling between the expander driving member and housing to rotationally drive the latter, together with means cooperable with the mechanical coupling opposing the generated reaction torque so that the power output of the internal expander is transmitted directly to the rotary housing.
  • Another object of the invention is to provide a rotary heat engine embodying the foregoing features wherein the mechanical coupling between the expander driving member and rotary housing-boiler-condenser unit is a fixed-ratio gear train constructed and arranged to rotationally drive the engine at a predetermined constant speed.
  • Still another object 'of the invention is to provide a rotary heat engine in accordance with the foregoing wherein the fixed-ratio gear train coupling the internal expander driving member and rotary housing-boilercondenser unit comprises a coaxial first gear driven by said driving member, a second gear carried by said boiler-condenser unit for rotationally driving the latter, and at least one intermediate gear.
  • a further object of the invention is to provide a rotary heat engine as set forth having novel means cooperable with at least one gear of the occluded gear train to generate a counter torque force opposing or anchoring the reaction torque generated by said occluded fixed-ratio gear train.
  • a still further object of the invention is to provide a rotary heat engine as set forth having means selectively operable to eliminate the counter torque force opposing the reaction torque of the gear train during startup of the engine and to selectively control such counter torque force during operation after start-up to provide slip or rotation relative to the reaction torque and thereby vary the speed of rotation of the rotary housing-boiler-condenser unit below the designed predetermined constant speed norrnally provided by the fixed-ratio gear train as desired.
  • FIG. 1 is a vertical sectional view diametrically through a rotary heat engine embodying the present invention
  • FIG. 2 is a transverse sectional view online 22, FIG. 1; v
  • FIG. 3 is an end elevational view in reduced scale, from the right hand end of the engine as viewed in FIG.
  • FIG. 4 is a detached fragmentary sectional view diametrically through the engine
  • FIG. 5 is a fragmentary sectional view diametrically through the engine showing a second arrangement of fixed-ratio gear train
  • FIG. 6 is a schematic view from line 6-6, FIG. 5;
  • FIG. 7 is a fragmentary sectional view similar to FIG. 5 showing a third arrangement of fixed-ratio gear train
  • FIG. 8 is a schematic view from line 8-8, FIG. 7;
  • FIG. 9 is a vertical sectional view diametrically through a rotary engine employing magnetic means for counteracting the reaction torque generated by the engme;
  • FIG. is a sectional view, in reduced scale, on line 10-10, FIG. 9;
  • FIG. 11 is a fragmentary sectional view diametrically through the engine of FIG. 9 showing an alternate coupling arrangement employing electromagnets;
  • FIG. 12 is a sectional view taken on line 12-l2, FIG. 11;
  • FIG. 13 is a schematic diagram of an electric circuit for the electromagnets of FIGS. 11 and 12,
  • FIG. 14 is a fragmentary vertical sectional view diametrically through the rotary engine of FIG. 9 illustrating a modification thereof for counteracting the reaction torque generated by the engine;
  • FIG. is a transverse section on line 1515, FIG. 14;
  • FIG. 16 is a fragmentary vertical sectional view diametrically through the engine of FIG. 1 illustrating the adaptation of a flywheel to the turbine drive shaft.
  • a rotary engine in the form of a closed Rankine cycle power system embodying the present invention' comprises a rotary housing and boiler B, a suitable internal expander such as, for example, a turbine T, a rotary condenser C coupled to the rotary, housing -and boiler for rotation therewith as a unit, and an internal occluded fixed-ratio gear train driven by the expander and connected to the rotary housing-boilercondenser unit to rotationally drive the latter at a predetermined speed, as hereinafter set forth and described.
  • a suitable internal expander such as, for example, a turbine T
  • a rotary condenser C coupled to the rotary, housing -and boiler for rotation therewith as a unit
  • an internal occluded fixed-ratio gear train driven by the expander and connected to the rotary housing-boilercondenser unit to rotationally drive the latter at a predetermined speed
  • the rotary boiler B comprises a cylindrical chamber 1 defined by an outer continuous circumferentially extending wall 2, side walls 3 and 4, and an inner cylindrical wall 5.
  • the outer circumferential wall 2 of the boiler chamber is configurated or contoured, for example as shown, to provide an expanded or extended thermal conductive surface area in accordance with the invention disclosed in the copending application of Philip J. Rennolds, Ser. No. 128,076 filed Mar.' 25, 1971, now US. Pat. No.
  • the boiler chamber wall 3 extends radially inward beyond the wall 5 and is connected at its inner end, as by bolts 3a, to an annular hub structure 6 disposed coaxially with respect to and internally of the boiler B.
  • the hub 6 houses the turbine T as described hereinafter.
  • the hub 6 has a central bore 7 extending axially therethrough and mounted coaxially in the outer end thereof is a shaft 8 that is secured in the hub 6 for rotation therewith.
  • the shaft 8 is rotatably journalled in a bearing! that is mounted in a fixed standard or support 10.
  • the inner cylindrical wall 5 of the boiler extends axially beyond the boiler chamber wall 4 as shown, and is fixedly secured, as by bolts 11, to the peripheral portion of the adjacent surface of a radially extending coaxial circular plate or disk 12 that projects outwardly from the inner end of a coaxially extending tubular shaft 13.
  • the tubular shaft 13 and plate 12 are rotatably mounted by means of bearings 14' and 15 upon a coaxially extending stationary shaft 16 that has its outer end mounted in a spherical bearing 17 housed in a hub structure 18 supported coaxially of the engine by means of radial spokes 19 from a fixed support 20.
  • shaft 16 is secured against rotation by means of a radial pin 17a.
  • cylindrical rotary housingboiler B and internal hub structure 6 together with the tubular shaft 13 and plate l2 constitute a unitary closed housing structure that is rotatably mounted by means of the bearings 9, 14 and 15 for coaxial rotation as a unit about the engine axis.
  • the rotary housing-boiler is adapted to be driven about its axis at a predetermined speed of rotation calculated to create the centrifugal force necessary to dispose and maintain the selected boiler liquid therein uniformly distributed circumferentially about and in contact with the inner surface of the outer peripheral wall 2 of the boiler with a liquid/vapor interface, designated x in FIG. 1, that is highly stable and essentially cylindrical and concentric with the axis of rotation with the boiler.
  • a liquid/vapor interface x is disposed at a predetermined radius from the rotation axis of the boiler to provide high boiling heat fluxes in excess of those obtainable at ambient gravity.
  • the annular body of liquid in the boiler may be heated to the required boiling temperature to vaporize the same, for example, by the combustion of a suitable fuel-air mixture in a stationary combustion box 21 that circumscribes the rotatable boiling'chamber 1.
  • Fuel for combustion is discharged into the combustion box 21 from a nozzle 22 at the required rate and pressure, and air for mixture with the fuel is discharged into the combustion box through a plurality of ports 23 in the peripheral wall 24.
  • a hood structure 25 defines a plenum chamber 26 into which the air is supplied through'a duct 27 at the pressure and volume required for efficient combustion of the fuel to heat the liquid in the boiler casing to the desired temperature.
  • the internal expander in the form of a turbine T, is of the single stage type comprising a rotor 30 having a series of turbine blades 31 arranged peripherally thereabout.
  • the turbine rotor 30 is received within an annular recess 32 provided in the hub structure 6 and is mounted for coaxial rotation independently of the boiler B on a shaft 33 that is rotationally supported within bore 7 of the hub 6 by means of bearings 34.
  • An annular series of nozzles 35 is'provided in the hub 6 coaxially adjacent the turbine rotor 30 and in confronting relation to the blades 31 thereof.
  • An annular high pressure vapor manifold 36 is provided in the hub structure 6 and leads to the nozzles 35.
  • High pressure vapor is supplied from the boiler chamber 1 to the manifold 36 by a plurality of vapor tubes 37 arranged in equally spaced relation circumferentially of the axis to insure rotational balance in the boiler.
  • the high pressure vapor is discharged from the manifold 36 through the nozzles 35 and impinges upon the blades 31 to drive the turbine rotor 30 and its shaft 33 at the desired speed of rotation.
  • a seal 34a is provided on the shaft 33 inwardly-adjacent the turbine rotor 30 to minimize migration of the pressure vapor from the turbine along shaft 33.
  • An annular diffuser 38 is provided in the hub 6 to receive the'exhaust vapor from the expander, such as turbine T, and the inlet opening thereto is disposed in confronting relation .to the turbine blades 31 at the opposite side thereof from the nozzles 35. Exhaust vapor entering the diffuser 38- is discharged into an annular exhaust chamber 39 in closed rotary housing from which it passes into the condenser C.
  • a plurality of axially extending radial partitions or baffles 39a is provided in the exhaust chamber 39 and arranged in equally spaced relation circumferentially about the engine axis. These baffles 39a function to maintain the angular velocity of the exhaust vapor at that of the rotating boilercondenser unit and to direct the vapor toward and into the heat exchange tubes 41 of the condenser C.
  • the condenser C comprises a coaxial array of annular radial fins 40v and axial heat exchange tubes 41 mounted at the opposite side of the plate 12 from the boiler for rotation with boiler B, plate 12 and shaft 13 as a unit.
  • the fins 40 consist of separate or independent annular disk elements supported and secured in predetermined equally spaced parallel relation with respect to one another by means of the plurality of heat exchange tubes or pipes 41 that extend longitudinally through the fins 40 parallel with respect to the rotational axis thereof.
  • the fins 40 and tubes 41 are fabricated of metal having high thermal conductivity such as, for example, copper or aluminum, and said fins preferably are bonded to said heat exchange tubes 41 by brazing, soldering or the like, to provide maximum thermal conductivity therebetween.
  • the tubes or pipes 41 are arranged in rotationally balanced spaced relation circumferentially of the fins 40 and the inner ends of the tubes 41 are mounted and secured in corresponding openings 42 provided through the plate 12 so that the interiors of the tubes 41 are in communication with the interior of the vapor chamber 39
  • the outer ends of the tubes 41 are mounted and secured in recesses 43 provided in an annular end ring 44 that is disposed coaxially adjacent the outermostof the fins 40 and supported from the tubular shaft 13 by circumferentially spaced radial spokes 45.
  • the condenser C a'unit about their common 'axis.
  • the inner peripheral edges of the fins 40 define interand boiler 13 are rotatable as I nally thereof a coaxial inlet chamber 46 for the cooling fluid to be discharged outwardly by and between the plurality of rotating fins 40 as hereinafter set forth.
  • the inner diameter of the ring 44 is substantially the same as the inner diameter of the adjacent group of fins 40 i so as not to restrict the flow of fluid into the chamber 46, and an outwardly flared or bell-shaped fluid intake member 47 is fixedly supported by the spokes 19 from the stationary support 20 in coaxial relation outwardly adjacent the end ring 44 as shown in FIG. 1.
  • the axial spacing or distancebetween the adjacent fins 40 is determined with relation to the rotational speed at which the boiler-condenser 'unit is driven and to the inner and outer radii of said fins so as to utilize the viscous properties of the cooling fluid and the shear forces exerted thereon by the rotating fins 40 to convey and accelerate the fluid radially outward between said fins in accordance with the invention-set forth and described in the copending application for U. S. Pat. of
  • both the plate 12 and the ring 44 The outer radius of both the plate 12 and the ring 44 is the same and is such that the plate 12 and ring 44 extend radially outward beyond the fins 40a distance to provide radial flange portions F and F" operable to augment fluid flow outward y between the fins-40 as described in the copending application of Stanley B. Levy, Ser. No. l80,733 filed Sept. 15,1971. Also, fluid flow augmentation blades of the type and construction shown and described in said Levy application S. N. 180,733 can be provided when desired in any particular engine installation.
  • the turbine exhaust vapor discharged to the chamber 39 passes into the heat exchange tubes 41 where the .vapor is condensed by heat exchange with a cooling fluid, such as ambient air, discharged outwardly between the array of fins 40 as previously described.
  • the condensate thus formed in the tubes 41 flows into an annular collector 48 from which it is discharged radially by centrifugal force generated by rotation of the condenser C, through a plurality of conduits 49 and returned to the boiler chamber 1. 7
  • the particular feature of the present invention resides in the provision of a novel mechanical coupling between the internal expander and rotary housing boiler-condenser unit so that during operation of the engine, after start-up, the housing-boiler-condenser unit is rotationally driven continuouslyby the primary power output generated by the engine. According to the present invention this is accomplished by means of an internal occluded fixed-ratio gear train arranged coaxially of the engine axis and interiorly of the rotary housing-boiler-condenser unit.
  • fixed-ratio gear train used in this specification andthe appended claims is not limited to a gear train embodying intermeshing toothed gear elements and is intended to include other gear trains of fixedratio wherein the driving connection between the elements of the train, for example, is by frictional engagement between said elements, or otherwise, so long as gray'50 is a plurality of planetary gears 51 that are also meshed with a circumscribing annular ring gear 52.
  • the ring gear 52 is fixedly mountedon and carried by an annular flange 12a that is formed integral with, and projects axially from the adjacent face of the plate 12.
  • three planetary gears 51 are provided and arranged in equally spaced relation 'circumferentially about the engine axis.
  • Each of the planetary gears 51 is rotatably mounted on a stub shaft 54 by means of a bearing 55 and eachstub shaft 54 is fixedly mounted in a stationary spider portion 56 provided at the inner end of the stationary shaft 16.
  • the axes of the planetary gears 51 are fixedlypositioned so that they do not rotate or move circumferentially relative to or about the engine axis; Thus the full. power output of the engine expander is transmittedfr'om the driving sun.
  • Means such as a clutch (not shown), can be provided for breaking the drive between motor M and pulley 57 when the engine attains normal operation, or the motor can continue to be driven by the rotating boiler-condenser unit and shaft 8 and function as a generator operable,- for example, for charging a battery that powers accessories such as the starter motor, lights and the like.
  • a power takeoff 59 or other suitable driving connection is provided at the outer end of the output shaft 8 which may be used to drive any selected equipment or machinery such as, for example, a wheeled vehicle, boat, or otherwise, as desired.
  • the pressure vapor'generated in the boiler is discharged inwardly through the tubes 37 to manifold 36 and thence through the nozzles 35 into impinging contact against the turbine blades 31 thereby driving the turbine rotor 30 and shaft 33 at the desired predetermined speed of rotation.
  • the shaft 33 through the occluded gear train previously described drives the rotary housing-boilercondenser unit and the shaft 8 at a predetermined speed of rotation relative to the speed of shaft 33 determined by the fixed ratio of the gear train.
  • the direction of rotation of the housing-boiler-condenser unit and its shaft 8 is opposite the direction of rotation of the drive shaft 33.
  • the exhaust vapor'from the turbine enters the diffuser numeral 38 and is discharged therefrom through housing chamber 39 into the heat exchange tubes 41 where it is condensed by the cooling fluid discharged outwardly between the fins 40 as previously described.
  • the condensate flows outwardly from the tubes 41 into the collector 48 from which it is returned to the boiler chamber 1 through tubes 49 at a controlled rate equal to the rate of vaporization of the boiler liquid.
  • a plenum chamber may be provided for the heat exchange fluid discharged outwardly through the array of fins 40.
  • a plenum chamber may comprise a stationary cylindrical wall circumscribing the array of fins and enclosed by spaced apart end wall portions 61 and 62 that closely interfit with the outer edge portions of the rotating plate 12 and ring 44, respectively.
  • the plenum chamber preferably is provided with a pair of diametrically disposed tangentially extending fluid outlets 63 and 64, respectively, as shown in FIG. 3 of the drawings.
  • a U-shaped tube 65 having a threaded cap closure 66 may be provided circumferentially of the boiler B and arranged as shown for use either as a fill tube for charging the boiler with working liquid or for periodically evacuating the boilercondenser system to remove small percentages of air or other non-condensable vapors that may become entrained in the working fluid of the boiler-condenser system.
  • FIGS. 5 and 6 of the drawings there is shown a fixed-ratio gear train comprising a rotationally driven sun gear 50a on the shaft 33a driven by the turbine rotor 30a.
  • a stationary sun gear 67 is mounted coaxially at the inner end of the stationary shaft 16a and driving connection to the rotary housing-boiler-condenser unit is provided by a plurality of pairs of gears 68 and 69 that are meshed, respectively, with the driven sun gear 500 and the stationary sun gear 67.
  • Each pair of gears 68 and 69 is fixedlymounted coaxially upon a stub shaft 70 and each of the latter has its opposite'ends rotationally journalled, by means of bearings 71 and 72, in the adjacent face of plate portion 120 of the rotatable shaft 13a and the rotatable hub structure 6a of the boiler B, respectively.
  • the driven sun gear 50a drives the gears 68 on stub shaft 70 thereby rotationally driving the latter and the gears 69 thereon rotationally about the fixed gear 67 so that the housing-boiler-condenser unit is rotationally driven about the engine axis at the desired speed in the direction opposite the direction of rotation of the turbine rotor 30a and its shaft 33a.
  • FIGS. 7 and 8 Another gear arrangement is shown in FIGS. 7 and 8 which may be employed for driving the housing-boiler-condenser unit in the same direction of rotation as the turbine 30b and its shaft 33b.
  • the driven sun gear 50b drives a plurality of compound gears 71 each rotationally mounted by means of a bearing 72'on a stub shaft 73 that is fixedly mounted in the stationary spider 56b at the inner end of the non rotatable shaft 16b.
  • the sun gear .50b is meshed with and rotationally drives the larger diameter gear 74 of each compound gear 71, and the smaller diameter gear 75 thereof drives a gear 76 rotationally mounted by a bearing 77 ona stub shaft 78 thatis also fixedly mounted in the stationary spider 56b radially outward from the corresponding stub shaft 73.
  • the gear 76 in turn is meshed with and rotationally drives a ring gear 76a that is mounted on an inwardly extending flange portion of th'eplate 12b at the inner end of the rotatable shaft 13b thereby rotationally driving the latter and the boiler-condenser unit at the desired speed in the same direction of rotation as the turbine shaft 33b.
  • the gear train is housed within a closed chamber having a plug located peripherally therein for periodically draining any vapor condensate therefrom.
  • reaction torque of the gear train is mechanically opposed or resisted by a fixedly positioned member at the inner end of the non-rotatable shaft 16,160 or 16b, as the case may be.
  • the invention is not limited to such arrangements and other means may be provided for holding or resisting the reaction torque of the gear train.
  • reaction torque of the gear train may be opposed or resisted by magnetic means and such an arrangement may be employed to advantage in medium power rotary engines and particularly in installations where it may be desirable to enclose the engine in an hermetically sealed casing or housing.
  • One embodiment of a rotary engine wherein the reaction torque is opposed by means of magnets is shown in FIGS. 9 and of the drawings.
  • the annular cylindrical housing and boiler B has a coaxial central hub structure 79 similar to that previously described and this hub structure includes axially off-set wall portions 80 defining an enclosed gear chamber 81 at the opposite side of the hub 79 from the condenser C'.
  • the wall portions 80 terminate inwardly in a projecting coaxial tubular shaft portion 82 that is rotatably mounted by means of a bearing 83 in a fixed standard or support 84.
  • the condenser C constructed substantially as previously described, includes an array of spaced parallel annular fins 85 supported coaxially of the engine by a shaft 86 that has its outer end rotatably mounted by a bearing 87 in a fixed standard or support structure 88.
  • the inner end of the shaft 86 is fixedly connected to the adjacent member89 of the housing-boiler-condenser hub structure.
  • the boilercondenser is rotatably mounted by the bearings 83 and 87 for coaxial rotation as a unit about the engine axis.
  • a turbine rotor 90having a series of turbine blades 91 is received within a recess provided in the hub 79 and is mounted for coaxial rotation independently of the housing-boiler-condenser unit on a shaft 92 that is rotationally supported by bearings 93 in the bore 79a of the hub 79.
  • a seal 93a is provided on the shaft 92 adjacent the turbine rotor 90 to minimize migration of pressure vapor along the shaft 92 to the gear chamber 81 where it would condense, and a drain plug 81a is provided in the peripheral wall of chamber 81 for periodic removal of vapor condensate therefrom.
  • the internal occluded gear train comprises a sun gear 94 fixedly mounted on and driven by the turbine shaft 92.
  • the sun gear 94 drives a plurality of planetary gears 95 that in turn drive a circumscribing ring gear 96 mounted on and carried by the boiler hub structure 79.
  • three planetary gears 95 are provided and arranged in equally spaced relation circumferentially about the engine axis.
  • Eachplanetarygear95 is rotatably mounted on a stub shaft 97 by means of a bearing 98 and each stub shaft 97 is fixedly mounted in a spider portion 99 provided at the inner end of a coaxial shaft 100 that is rotationally journalled by means of bearings 101,102 within the rotatably mounted tubular shaft 82 of the boiler-condenser unit.
  • the reaction torque of the gear train is opposed and the shaft 100 and spider 99 are restrained against rotation about the engine axis bymeansof cooperating pairs of magnets.
  • Mounted on the outer end of theshaft 100 is the hub 103 of a wheel-like member 104 having a coaxial cylindrical flange or rim;105 of predetermined diameter.
  • the hub 103 is keyed or 0th erwise secured against rotation relative to the shaft 100.
  • Fixedly mounted in predetermined equally spaced relation circumferentially about the outer surface of the flange'105 is a plurality of magnets 106 (see FIG.
  • the members 104 and 108 or the portions thereof in whichthe magnets 106 and 107 are mounted must be of non-magnetic material.
  • a driving connection between the shaft 111 and the tubular shaft 82 of the rotary housing-boiler-condenser.unit is provided by a chain 115 from a sprocket 116 secured on the shaft 1 11 and a sprocket 117 keyed on the said shaft 82.
  • a power take-off 1 18 or other suitable driving connection is provided at the opposite end of the shaft 111.
  • the wheel member 104 and the magnets 106 are enclosed within a lightweight vapor-proof housing or casing 119 that is rotatable with the housing-boilercondenser unit and provided for the purpose of preventing leakage of pressure vapor from the turbine to the ambient atmosphere along shaft 100 thereby eliminating the necessity for providing; elaborate and costly pressure vapor seals about the shaft 100.
  • the housing 119 comprises: an inner wall portion 120 secured as at 121 to a flange 122 on the pulley 117 on shaft 82, a peripheral wall portion 123 extending axially between the series of magnets 106 and 107 and an outer wall portion 124.
  • An annular sump is provided at the junction of the inner and peripheral wall portions 120 and 123 of the housing 119 for collecting the condensate of any pressure vapor that. may migrate past the seal 93a and find its way along the shaft into said housing 119 and a threaded plug is provided in the sump for periodically draining off condensate that may be collected therein.
  • the housing or casing 1 19 is fabricated of non-magnetic material of high electrical resistance such as, for example, fibre reinforced plastic material soas to minimize eddy current losses and also not affect the magnetic field between cooperating pairs of magnets 106 and 107.
  • the sixteen cooperatively disposed pairs of magnets 106 and 107 each composed of barium ferrite having dimensions of lX3 ll centimeters and circularly arranged on a 13 inch diameter provide a counter torque force sufficient to oppose or anchor a reaction torque of 50 ft.lbs. at a fixed-speed gear train ratio of 11.5 to l, which is the rated torque output of a 20 hp engine made in accordance with the present invention.
  • FIGS. 9 and 10 these results may be accomplished, for exam ple, by providing electromagnets 107a in the fixed support structure 108a in lieu of the magnets 107 for cooperation with core members 106a of suitable ferrous material, as shown in FIGS. 1 1 and 12 of the drawings.
  • the electromagnets 107a are connected in parallel relation between the conductors 125 and 126 of an electric circuit that are connected through a double pole single throw switch 127 to a suitable source of electrical energy 128.
  • a rheostat or other suitable infinite control switch 129 is connected in the conductor 125 between the switch 127 and magnets 107a.
  • the electromagnets 107a are deenergized so that there is zero counter torque force opposing the reaction torque of the engine and, with the switch 127 closed, the control 129 can be selectively operated to vary the magnetic field intensity in the magnets 107a to provide the desired relative slip or fixation of the planetary gears 95 about the engine axis under the influence of the reaction torque generated by the engine.
  • FIGS. 1, 5 and 7 of the drawings Similar operation and results can be obtained in the embodiments of the invention shown in FIGS. 1, 5 and 7 of the drawings by providing a suitable clutch mechanism (not shown), for example, between the shaft 16 and spider 56 (FIG. 1), the shaft 16a and gear 67 (FIG. 5) and shaft 16b and spider 56b (FIG. 7).
  • a suitable clutch mechanism (not shown), for example, between the shaft 16 and spider 56 (FIG. 1), the shaft 16a and gear 67 (FIG. 5) and shaft 16b and spider 56b (FIG. 7).
  • Still other arrangements may be provided for generating a counter torque force in opposition to the reaction torque generated by the engine.
  • a pendulum of predetermined density, dimensions and location may be employed for generating an effective counter torque force, This may be accomplished, for example, in a rotary engine of the construction shown in FIG. 9, simply by substituting a suitable pendulum for the wheel member 104 on the shaft 100 and the magnets 106 and 107, as shown in FIGS. 14 and 15 of the drawings.
  • the reaction torque of the engine gear train is opposed and the gear shaft 100a that is journalled in the tubular shaft portion 82 of the rotary boiler-condenser unit of the engine may be effectively restrained against rotation about the engine axis by means of a pendulum 130 fixedly mounted on the outer end portion of said shaft 100a by means of bolts 131.
  • the pendulum is of predetermined density
  • a lead pendulum 130 in the configuration of a 60 triangle as shown, having a radius of 8 inches, an axial length of 8.5 inches and weighing 117 lbs. will provide a counter torque force sufficient to oppose or anchor a reaction torque of 50 ft. lbs. at a fixedspeed gear train ratio of 11.5 to 1, which is the rated torque output of a 20 hp engine of the present invention.
  • the pendulum 130 is enclosed within a vapor-proof housing 1 19a that is rotatable with the housing-boiler-condenser unit.
  • the .housing 119a comprises an inner wall 120a secured at 121a to a flange 122a on the pulley 1 17a on the shaft 82, a peripheral wall portion 123a and an outer wall portion 124a.
  • a vapor condensate sump with drain is provided at the juncture of the inner and peripheral wall portions 120a and 123a of the housing 119a.
  • the rotationally driven components provide an inherent rotational kinetic energy storage system that is highly useful to the performance of the engine, and the energy storage capacity or capability of the engine can be materially increased by the addition of a suitable flywheel on the high-speed turbine shaft of the engine.
  • FIG. 16 of the drawings is a fragmentary sectional view of an engineof the construction and arrangement shown in FIG. 1.
  • the turbine driven shaft 33 having the sun gear 50 thereon, is extended axially in the opposite direction as indicated at 33a and journalled in the bore 7 of hub structure 6 by bearings 132 and 133.
  • a flywheel 134 of predetermined dimensions and weight is keyed upon the outer end of the shaft extension 33a and secured thereon by a nut 135 so that the flywheel 134 is rotationally driven by the turbine 30 at the designed speed of rotation.
  • the flywheel 134 is enclosed within a housing 136 secured coaxially endwise of the rotary housing-boilercondenser unit and rotatable therewith.
  • a seal 133a is provided on the shaft 33a to minimize migration of pressure vapor from the turbine to the flywheel housing 136 where it would condense, and a threaded plug 136a is provided in the peripheral wall of the housing for periodically draining collected condensate therefrom.
  • a drive shaft portion 8a is formed on the housing 136 coaxially endwise thereof and is journalled by bearing 9a in a fixed standard or support 10a.
  • a drive pulley 57a for the start-up motor is keyed on the outer end of said shaft and power take-off connection 59a is provided at the extremity of the shaft.
  • flywheel on the high speed turbine shaft further increases the energy storage capability of the engine. For example, a 1
  • turbine speed flywheel weighing 0.692 lb./hp (that is, a 69.2 lb. flywheel for a hp engine) will increase the rotational kinetic energy storage capability of the engine by a factor of 3.
  • the rotating engine is capable of bringing a 3,500 lb. vehicle travelling at 45 mph to a stop without braking and storing all of the vehicular energy if the engine is permitted to overspeed by 15 percent. This ability to efficiently store kinetic energy by dynamic braking increases the system efficiency.
  • an engine constructed as shown and described having an output of hp at the turbine shaft 33 comprises a boiler having a mean internal diameter of 19.375 inches and an axial internallength of 3.625 inches.
  • the diameter of the turbine rotor at mid-height of the blades 31 is 4.301 inches, and the fins of the condenser C have an outer diameter of 14.00 inches and an inner diameter of 10.50 inches.
  • the axial length of the series of fins 40 is 10.50 inches and the spacing between adjacent fins 40 is 0.032 inches.
  • the housing-boiler-condenser assembly is rotationally driven at a speed in'the fixed ratio of 1 to 11.50 with respect to the turbine rotor speed through the occluded gear train and the latter is constructed and arranged in the embodiment of FIG. 1 to rotationally drive the housing-boiler-condenser assembly in the direction opposite the direction of rotationof the turbine rotor 30 and shaft 33.
  • a high molecular weight fluid such as trichlorotrifluorobenzene describedand claimed in my U. S. Pat. No. 3,702,534, is-
  • Boiler temperature (F.) Boiler pressure (psia) 150.00 Turbine speed (rpm) 30000.00 (relative to nozzles) Boiler-Condenser speed (rpm) f 2400.00 Condensertemperature (F.) a 303.00 Condenser pressure (psia) 3.30 Power Fluid flow rate, lb/sec. 0.638 Rankine cycle efficiency 0.196
  • the present invention provides a novel rotary heat engine of the closed Rankine cycle type wherein the rotary housing-boiler-condenser unit is internally coupled mechanically to the internal expander driving member so that the housing-boiler-condenser unit is rotationally driven continuously by the primary power output generated by the engine with the proportion of the power required to drive the boiler-condenser unit being automatically split-off from the total power developed and the balance of the power applied directly to the external load on the engine.
  • the engine of the present invention is especially useful for driving constant speed devicesand equipment such as, for example, electric generators and similar equipment and, in combination with power transmission mechanisms such as, for example of the hydromechanical, toroidal disk, variable pitch pulley and like types that receive power at constant speed and variable torque and provide power output of variable torque and speed, is ideally suited for driving vehicles such as automobiles and the like.
  • a rotary closed Rankine cycle engine comprising: a closed cylindrical housing rotatable about its axis and containing an annular boiler, said housing and boiler adapted to be rotated at a predetermined speed tomaintain an annular liquid body about the inner peripheral surface of said boiler with a liquid/vapor interface spaced a predetermined distance radially outward from said axis, I means to heat the liquid body in the boiler to generate pressure vapor therein, an expander coaxially within said closed housing for extracting work from said pressure vapor and including a coaxially rotatable driving member actu ated thereby, a condenser for the exhaust vapor from the expander mounted coaxially adjacent and communicating with the closed housing forming a sealed chamber and rotatable therewith as a unit, means for returning vapor condensate from the condenser to the boiler, an occluded fixed ratio gear train mounted coaxially 'within the rotary closed housing and interconnected between the expander driving member and said closed housing operable to
  • gear anchoring means comprises stationary nonrotatable means fixedlypositioning the'gear circumferentially with r'espectto the engine axis.
  • gear anchoring means comprises a magnetic coupling between the gear and a stationary non-rotatable member operable to anchor said gear c-ircumferentially with respect to the engine axis.
  • gear anchoring means comprises a pendulum member connected to the gear and having predetermined density and dimensions operable to anchor said gear circumferentially with respect to the engine axis.
  • a rotary engine as claimed in claim 1 comprising means variably controlling the generated counter torque force in relation to the generated engine reaction torque.
  • a rotary engine as claimed in claim 2 comprising means for variably controlling the gear anchoring means to provide relative rotation of the gear circumferentially about the engine axis.
  • gear train includes a first gear coaxially of the engine axis driven by the expander driving member
  • a rotary engine as claimed in claim 8 wherein the means anchoring the third gear comprises a stationary member on which said third gear is rotatably mounted.
  • a rotary engine asclaimed in claim 8 wherein the means anchoring the third gear comprises rotatable means mounting said third gear and magnetic coupling means between said mounting means and a stationary non-rotatable member operable to anchor the gear against rotation about the engine axis.
  • a rotary engine as claimed in claim 8 wherein the means anchoring the third gear comprises coaxial rotatable means mounting said third gear and a pendulum member of predetermined density, dimensions and location mounted on said rotable member.
  • a rotary engine as claimed in claim 1 comprising a flywheel fixedly mountedon the coaxially rotatable driving member of the expander and having predetermined dimensions and weight operable to materially increase the energy storage capacity of the engine.
  • An engine as claimed in claim 13 wherein the expander comprises a turbine having a series of nozzles rotatable with the boiler-condenser unit, and a driven rotor and shaft mounted for rotation coaxially of the engine axis.
  • a rotary engine as claimed in claim 4 comprising means for selectively varying the magnetic field'intensity of the magnetic coupling between the gear and sta tionary member to variably control the counter torque anchoring force in relation to the reaction torque of the engine and provide predetermined relative rotation of the gear about the engine axis.
  • a rotary engine as claimed in claim 16 wherein the means anchoring the intermediate gear mounting means comprises a stationary non-rotatable means fixedly positioning said ,gear mounting means circumferentially with respect to the engine axis.
  • anchoring means for the intermediate gear mounting means comprises a pendulum member connected to said mounting means and having predetermined density, dimensions and location operable to anchor the mounting means circumferentially with respect to the engine axis.
  • a rotary engine as claimed in claim 16 comprising a flywheel fixedly mounted coaxially on the turbine rotor shaft and having predetermineddimensions and weight operable to materially increase the energy storage capacity of the engine.
  • a rotary engine as claimed in claim 16 comprising means for variably controlling the anchoring means for said intermediate gear mounting means to provide relative rotation of the latter about the engine axis.
  • a rotary engine'as claimed in claim 18 comprising means for selectively varying the magnetic field intensity of the magnetic coupling between the gear mounting and stationary member to variably control the anchoring force in relation to the reaction torque of the engine and provide predetermined relative rotation of the mounting means and gears about the engine axis.
  • the magnetic coupling includes electromagnetic means and means for selectively controlling the current to said electromagnetic means for varying the magnetic field intensity of said coupling and thereby the anchoring force in relation to the engine reaction torque to pro vide predetermined relative rotation of the mounting means and gears about the engine axis.
  • a rotary engine as claimed in claim 10 comprising means for selectively varying the magnetic field intensity of the magnetic coupling between the gear and stationary member to variably control the counter torque anchoring force in relation to the reaction torque of the engine and provide predetermined relative rotation of the gear about the engine axis.
  • An engine as claimed in claim 10 wherein the expander comprises a turbine having a series of nozzles rotatable with the boiler-condenser unit, and a driven rotor and shaft mounted for rotation coaxially of the engine axis on which the said first gear is mounted.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
US00206779A 1971-12-10 1971-02-10 Rotary heat engines Expired - Lifetime US3769796A (en)

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US20677971A 1971-12-10 1971-12-10

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CA (1) CA971372A (zh)
DE (1) DE2260207A1 (zh)
FR (1) FR2164398A5 (zh)
GB (1) GB1389900A (zh)
IL (1) IL41036A (zh)
IT (1) IT971653B (zh)
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SE (1) SE384558B (zh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3850147A (en) * 1973-11-19 1974-11-26 Du Pont Rotary boilers and combustors
US4070862A (en) * 1976-09-24 1978-01-31 E. I. Du Pont De Nemours And Company Cascaded two-fluid rotary closed Rankine cycle engine
FR2552160A1 (fr) * 1983-09-15 1985-03-22 Bech Jean Moteur thermique a vapeur pour engin submersible autonome, sans communication avec la surface
US20020158530A1 (en) * 2000-02-23 2002-10-31 Gennesseaux Andre Rene Georges Self-contained (heat and electricity) cogeneration system comprising a flywheel
US20040144092A1 (en) * 2003-01-06 2004-07-29 Jarman John Warner Rotary heat engine
US20170248347A1 (en) * 2016-02-29 2017-08-31 Nativus, Inc. Rotary heat exchanger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0376388U (zh) * 1989-11-28 1991-07-31
GB2277964B (en) * 1993-05-10 1996-10-30 Edgar Stanley Askam External combustion engine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2525804A (en) * 1945-05-02 1950-10-17 Robert B Kellogg Aircraft rotary boiler turbine air condenser power plant
US2576284A (en) * 1948-02-19 1951-11-27 Crocchi Piero Vapor electricity generator set
US2583872A (en) * 1947-08-02 1952-01-29 United Aircraft Corp Gas turbine power plant, including planetary gearing between a compressor, turbine, and power consumer
US2810304A (en) * 1952-09-18 1957-10-22 Joy Mfg Co Apparatus for controlling the transmission of torque
US3613368A (en) * 1970-05-08 1971-10-19 Du Pont Rotary heat engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2525804A (en) * 1945-05-02 1950-10-17 Robert B Kellogg Aircraft rotary boiler turbine air condenser power plant
US2583872A (en) * 1947-08-02 1952-01-29 United Aircraft Corp Gas turbine power plant, including planetary gearing between a compressor, turbine, and power consumer
US2576284A (en) * 1948-02-19 1951-11-27 Crocchi Piero Vapor electricity generator set
US2810304A (en) * 1952-09-18 1957-10-22 Joy Mfg Co Apparatus for controlling the transmission of torque
US3613368A (en) * 1970-05-08 1971-10-19 Du Pont Rotary heat engine

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3850147A (en) * 1973-11-19 1974-11-26 Du Pont Rotary boilers and combustors
US4070862A (en) * 1976-09-24 1978-01-31 E. I. Du Pont De Nemours And Company Cascaded two-fluid rotary closed Rankine cycle engine
FR2552160A1 (fr) * 1983-09-15 1985-03-22 Bech Jean Moteur thermique a vapeur pour engin submersible autonome, sans communication avec la surface
EP0143728A1 (fr) * 1983-09-15 1985-06-05 Jean André Bech Moteur thermique à vapeur pour engin submersible autonome, sans communication avec la surface
US20020158530A1 (en) * 2000-02-23 2002-10-31 Gennesseaux Andre Rene Georges Self-contained (heat and electricity) cogeneration system comprising a flywheel
US6784562B2 (en) * 2000-02-23 2004-08-31 Energiestro Heat engine electricity generating system having low-pressure enclosure for flywheel, clutch and electric generator
US20040144092A1 (en) * 2003-01-06 2004-07-29 Jarman John Warner Rotary heat engine
US6892539B2 (en) * 2003-01-06 2005-05-17 John Warner Jarman Rotary heat engine
US20170248347A1 (en) * 2016-02-29 2017-08-31 Nativus, Inc. Rotary heat exchanger
US11397029B2 (en) * 2016-02-29 2022-07-26 Nativus, Inc. Rotary heat exchanger

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IL41036A (en) 1975-12-31
GB1389900A (en) 1975-04-09
SE384558B (sv) 1976-05-10
JPS4865303A (zh) 1973-09-08
CA971372A (en) 1975-07-22
IT971653B (it) 1974-05-10
JPS5514246B2 (zh) 1980-04-15
FR2164398A5 (zh) 1973-07-27
IL41036A0 (en) 1973-02-28
NL7216695A (zh) 1973-06-13
DE2260207A1 (de) 1973-06-20

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