US3690302A - Rotary boilers - Google Patents

Rotary boilers Download PDF

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Publication number
US3690302A
US3690302A US128076A US3690302DA US3690302A US 3690302 A US3690302 A US 3690302A US 128076 A US128076 A US 128076A US 3690302D A US3690302D A US 3690302DA US 3690302 A US3690302 A US 3690302A
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Prior art keywords
boiler
liquid
peripheral wall
wall
vapor interface
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US128076A
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English (en)
Inventor
Philip J Rennolds
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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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B5/00—Steam boilers of drum type, i.e. without internal furnace or fire tubes, the boiler body being contacted externally by flue gas
    • F22B5/005—Steam boilers of drum type, i.e. without internal furnace or fire tubes, the boiler body being contacted externally by flue gas with rotating drums
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B27/00—Instantaneous or flash steam boilers
    • F22B27/12—Instantaneous or flash steam boilers built-up from rotary heat-exchange elements, e.g. from tube assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24V—COLLECTION, PRODUCTION OR USE OF HEAT NOT OTHERWISE PROVIDED FOR
    • F24V40/00—Production or use of heat resulting from internal friction of moving fluids or from friction between fluids and moving bodies

Definitions

  • a rotary boiler comprising a boiler chamber defined by axially spaced side walls and radially spaced outer peripheral wall.
  • the boiler is rotated about its axis at a speed to maintain an annular body of organic liquid distributed circumferentially about the inner surface of the peripheral boiler wall with a cylindrical liquid/vapor interface disposed at a predetermined radius from the rotation axis.
  • Combustion means is provided outwardly adjacent the boiler peripheral wall to heat and vaporize the liquid at high boiling heat fluxes greater than obtainable at ambient gravity.
  • the boiler peripheral wall is configurated, as by flutes or corrugations, in the circumferential direction to provide transversely thereof in the axial direction a total length of wall heat conduction surface to the liquid that is substantially greater than the linear axial spacing of the boiler side walls at the liquid/vapor interface.
  • the greater heat conduction surface of the peripheral wall reduces the heat flux at the wall and the temperature difference between the wall and the liquid/vapor interface to an extent that a compact boiler can be operated at high overall thermal flux with minimal decomposition of the boiler fluid.
  • PATENTEDSEP 12 m2 SHEEI 3 OF 3 mvswroa: PHILIP J. RENNOLDS AT'TYS.
  • the present invention relates to rotary boilers, and more particularly to rotary boilers of novel construction particularly adapted for use in closed-Rankinecycle engines.
  • Rotary boilers are known in the art of vapor generation and have been demonstrated to provide a number of advantages over conventional boilers.
  • the high centrifugal acceleration in such a boiler produces a sharp stable interface between the liquid and vapor during boiling.
  • Such a boiler produces a high quality vapor with steady flow of both vapor and liquid and the boiler operates independent of the ambient gravity field and orientation.
  • the high rotational speeds customarily employed in rotary boilers permit heat fluxes well above the peak boiling level for ambient gravity.
  • a closed-Rankine-cycle engine using external combustion as a source of heat is capable of providing an excellent low-pollution replacement for conventional internal combustion engines customarily used in automotive vehicles.
  • a practical closedRankine-cycle engine for such use must be small and compact and, therefore, necessarily requires a vaporizer or boiler that is also compact and is operable with high molecular weight organic power fluids that can be vaporized with little or no decomposition of the organic fluid.
  • a rotary boiler of relatively short, compact axial length defined by axially spaced side walls and a circumferentially extending outer peripheral wall that is suitably configurated, such as fluted or corrugated, in the direction circumferentially of the boiler to provide in the axial direction transversely of said peripheral wall a combustion heat conduction surface of substantially greater extent or length than the linear axial spac ing of the boiler end walls at the liquid/vapor interface.
  • the increased extent or length of the boiler peripheral wall surface provides a greatly reduced heat flux at the wall that is substantially less than the high heat flux at the liquid/vapor interface, thereby greatly reducing the temperature difference between the peripheral wall and the liquid/vapor interface while still maintaining the high boiling heat flux at said liquid/vapor interface that is required for a compact boiler while at the same time providing a very low rate of decomposition of the organic boiler fluid.
  • an object of the present invention is to provide a rotary boiler of novel design and construction useful for vaporizing liquids, including water and refrigerant liquids, and particularly suited for use in closed-Rankinewycle engines.
  • Another object of the invention is to provide a rotary boiler of novel design and construction that is of relatively small, compact size and can be operated using high molecular weight organic power fluid to provide high boiling heat fluxes at the liquid/vapor interface with little or no decomposition of the organic power fluid.
  • a further object of the invention is to provide a rotary boiler as set forth which is operable at high heat flux at the liquid/vapor interface and at a substantially lower heat flux at the peripheral boiler wall so that the difference between the temperature at the boiler wall and the temperature at the liquid/vapor interface is sufficiently small to enable the rotary boiler to be operated in a closed-Rankine-cycle engine at maximum overall thermal efficiency of the engine.
  • FIG. 1 is a sectional view taken diametrically through a rotary boiler and stationary combustion chamber embodying the present invention showing the same schematically in a closed-Rankine-cycle power generation system including a turbine and a condenser;
  • FIG. 2 is a sectional view taken on line 2-2, FIG. 1;
  • FIG. 3 is a fragmentary view on line 3-3, FIG. 2;
  • FIG. 4 is an enlarged fragmentary transverse sectional view similar to FIG. 3 schematically illustrating the radial component of convection flow of liquid in the boiler;
  • FIG. 5 is an enlarged sectional view on line 5-5, FIG. 1 schematically illustrating the tangential or spiral components of convection flow of liquid in the boiler;
  • FIG. 6 is a view generally similar to FIG. 1 showing a modified construction of a rotary boiler embodying the present invention
  • FIG. 7 is a sectional view taken on line 7-7, FIG. 6, and
  • FIGS. 8,9, 10 and 11, respectively, are enlarged fragmentary transverse sectional views showing modifications in design and construction of the outer peripheral wall of the rotary boiler.
  • one embodiment of rotary boiler constructed according to the present invention comprises a generally cylindrical casing 1 having axially spaced side walls 2 and 3, respectively, and a continuous circumferentially extending outer peripheral wall 4 of predetermined cross-sectional configuration and dimensions as hereinafter more particularly described.
  • Fixedly secured to and extending coaxially through the casing side walls 2 and 3 is a shaft member 5 by means of which the boiler casing l is rotatably mounted in bearings 6 and 7.
  • the boiler may be rotationally driven at the desired speed by means .of an electric motor M driving a gear 8 which in turn drives a gear 9 mounted on the shaft 5.
  • the space enclosed within the circumferential wall 4 and side walls 2 and 3 of the boiler defines a vapor chamber V within the rotating boiler casing l.
  • the chamber V is in communication through a plurality of vapor tubes 10 with an axial passage 11 in the shaft 5 so that the vapor generated in the boiler and collecting in the chamber V is discharged from the rotating boiler through the vapor tubes 10, said shaft passage 11 and a conduit 12, for example, to a suitable expander such as a turbine 13.
  • the vapor tubes 10 function to transfer rotational energy in the vaporsback to the linear exit system as the vapors leave the boiler through the shaft 5, and the tubes 10 are disposed in equally spaced relation circumferentially around the boiler to insure rotational balance when driven by the motor M.
  • Liquid is admitted to the boiler at a controlled rate equal to the rate of vaporization of the liquid.
  • the liquid admitted to the boiler is in the form of liquid condensate, fed through an axial passage 14 in the shaft 5 and a plurality of feed tubes 15 extending radially from passage 14 to a point below the surface level of the boiler liquid.
  • the feed tubes 15 are thermally insulated or fabricated of suitable insulating material since the liquid pressure in said tubes 15 increases with their radius and is therefore relatively lower adjacent the rotation axis so that excessive heating of the lower pressure liquid may cause vapor binding within the tubes and interference with pumping of the liquid.
  • the liquid condensate is supplied to the shaft passage 14 by a pipe 16 from a condenser 17 having its inlet connected by a conduit 18 to the exhaust of the turbine 13.
  • the feed tubes 15 are equally spaced circumferentially around the boiler for rotational balance.
  • the radial vapor tubes 10 and feed tubes 15 are desirable in a boiler of the present type to control radial flow of the liquid and vapor fluids for proper and efficient operation of the boiler for the reasons set forth in the aforesaid copending application of William A. Doerner, Ser. No. 12,296, filed Feb. 18, 1970, now US. Pat. No. 3,590,786.
  • means other than the tubes 10 and 15, such as baffles, to insure rotation of the boiler liquid with the boiler can be employed.
  • the rotary boiler is driven by the motor M at a predetermined speed of rotation calculated to create the centrifugal force necessary to dispose and maintain the selected boiler liquid uniformly distributed circumferentially about and in contact with the inner surface of the outer peripheral wall 4 of the boiler, with a liquid/vapor interface, designated x in FIG. 1, that is highly stable and is essentially cylindrical and concentric with the axis of rotation of the boiler.
  • the 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 and also to provide the desired boiler (vapor) pressure correlated to the radial length of the liquid leg in the feed tubes 15.
  • the diameter of the outer peripheral wall 4 of the boiler and the axial spacing of the end walls 2 and 3 must be as small as possible and at the same time provide at the speed of rotation a liquid/vapor interface x of sufficient axial length and radius to produce the high boiling heat fluxes and desired boiler (vapor) pressure previously described.
  • the required increase or extended axial length of combuation heat conduction surface of the peripheral boiler wall can be provided by forming or constructing the peripheral wall 4 in a manner to include circumferentially therein, for example, a plurality of parallel continuous flutes or corrugations 20, as shown in FIG.
  • the wall 4 is fabricated of any suitable heat conductive metal such as, for example, steel, copper, aluminum and the like, and the number of the flutes or corrugations 20 and the configuration and dimensions thereof are selected and predetermined to provide a total axial direction length of heat conductive peripheral wall surface with respect to the linear axial length of the liquid/vapor interface sufficient to enable the boiler to be operated at maximum overall thermal efficiency of the closed-Rankine-cycle engine with minimal decomposition of the organic power fluid.
  • the total axial direction'length of the peripheral wall heat comductive surface to liquid provided by the present invention should be at least one and one-half times the linear axial spacing of the boiler side wall portions 2 and 3 at the liquid/vapor interface (i.e., the linear axial length of the interface x in FIG. 1) and preferably, for best results, should be in the range of from about 3 to about 5 times the linear axial spacing of the boiler end walls 2 and 3 at the interface at or the axial length of said interface.
  • the annular body of liquid in the boiler may be heated tothe 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 casing 1.
  • Fuel for combustion is discharged intosaid 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 residual combustion gases are discharged through an exhaust duct 28 and a stationary transverse baffle 29 having projecting portions 30 for complementary interfitting cooperation with the flutes or corrugations 20 of the boiler peripheral wall 4 is mounted intermediate the fuel nozzle 22 and outlet duct 28 to control recirculation of the combustion gases.
  • a rotary boiler constructed in accordance with the invention comprises a metal peripheral boiler wall 4 of 0.031 inch thickness having circumferential flutes or corrugations 20 therein.
  • the inner and outer diameters of the inner corrugated sur face are 6 inches and 6 /16 inches, respectively, and the pitch or distance in a direction parallel to the axis of symmetry between similar points on adjacent corrugations is 0.335 inch.
  • the radii at the peaks of the several corrugations are 0.031 inch inside and 0.062 inch outside, respectively, and the linear axial spacing of the boiler side wall portions 2 and 3 at the liquid/vapor interface is 1.34 inches.
  • the peripheral wall 4 having the flutes or corrugations 20 provides in the axial direction of the boiler a total surface length of the peripheral wall 4 that is 3.1 6 times the linear axial spacing of the boiler side wall portions.
  • the described rotary boiler provides a substantially low heat flux at the peripheral wall 4 and produces very much smaller temperature differences between the wall 4 and the liquid/vapor interface with high boiling heat fluxes at said interface as compared to a similar rotary boiler having a flat or axially plane peripheral wall surface.
  • a similar rotary boiler having a flat or axially plane peripheral wall surface.
  • the average temperature difference between wall 4 and liquid/vapor interface was 58 F.
  • a similar flat peripheral wall boiler with the same linear axial spacing of the boiler side wall portions would have l/3.l6 of the boiler area and would therefore require a heat flux of 149,000 Btu/hr ft to provide the same total heat input to the fluid.
  • the corrugated boiler wall is much thinner than a flat wall boiler of equal axial length providing the same heat flux at the liquid/vapor interface.
  • the thinner metal wall of the corrugated boiler operating at a fraction of the peripheral wall heat flux of a flat wall boiler, requires a greatly reduced thermal gradient through the metal wall to conduct the necessary heat flux through the wall.
  • the difference in thermal gradient between a corrugated and flat wall boiler is still greater for the case where the flat wall boiler is provided with fins on its external periphery to promote heat transfer from the combustion heating gases.
  • the reduction in thermal gradient in the boiler wall for a corrugated boiler reduces the average wall temperature and thus makes possible the use of cheap alloys. That is, expensive alloys normally used in high temperature Rankine cycle engine boilers are not required. Furthermore, the lower temperature of the external surface of the corrugated boiler wall significantly increases heat transfer from the hot combustion gases due to the greater temperature difference between the hot gases and the boiler wall thereby improving burner efficiency. A further ad vantage of the thinner metal wall of the configurated boiler is its faster response to increased heat input.
  • FIGS. 6 and 7 of the drawings A modified construction of a rotary boiler embodying the present invention is shown in FIGS. 6 and 7 of the drawings.
  • the rotary boiler shown is a wheel-like structure comprising an annular casing 1a having axially spaced side walls 2a and 3a, respectively, and a continuous circumferentially extending outer peripheral wall 4a provided with circumferentially extending parallel continuous flutes or corrugations 20a therein constructed and arranged as previously described.
  • the annular casing 1a is supported concentrically from a shaft 5a by a plurality of vapor tubes a.
  • the shaft 5a is rotatably mounted in bearings 6a and 7a and the boiler may be rotationally driven at the desired speed by means of an electric motor M driving a gear 8a which in turn drives a gear 90 mounted on the shaft 5a.
  • the space within the peripheral wall 4a and side walls 2a and 3a of the casing la defines a vapor chamber V that is in communication through the vapor tubes 1011 with an axial passage 11a in the shaft 50 so that vapor generated in the boiler and collecting in the chamber V is discharged inwardly through the vapor tubes 10a and shaft passage lla to a suitable expander as previously described.
  • Liquid is admitted to the boiler, for example, in the form of liquid condensate from an axial passage 14a in the shaft 50 by means of a plurality of feed tubes 15a that extend radially outward within the vapor tubes 10a to a point below the surface level of the boiler liquid.
  • the vapor tubes 10a and feed tubes 15a are equally spaced circumferentially with respect to the shaft 5a and boiler casing 1a to impart rotational balance to the boiler.
  • the rotary boiler is driven by the motor M at a predetermined speed of rotation to dispose and maintain the selected boiler liquid uniformly distributed circumferentially about the inner surface of the peripheral wall 4a of the boiler with a cylindrical liquid/vapor interface designated x in FIG. 6.
  • the flutes or corrugations 20a in the boiler peripheral wall 4a provide a substantially low heat flux at the peripheral wall 4a and very much smaller temperature differences between said wall 4a and the liquid/vapor interface x with high boiling heat flux at said interface as compared to a similar rotary boiler having a flat or axial plane peripheral wall surface.
  • the design and construction of the boiler peripheral wall is not limited to the particular configuration and arrangement provided by the flutes or corrugations 20 and 20a in the walls 4 and 4a shown in FIGS. 1 and 6, respectively, of the drawings.
  • Various other configurations and constructions may be employed, for example, as shown in FIGS. 8, 9, 10 and 11, the arrangements of FIGS. 8 and 10 being preferred over FIGS. 9 and 11, so long as the peripheral wall configuration employed provides the increased or extended total axial length of heat conduction to liquid surface of the wall 4a to produce the desired low heat flux at the peripheral wall and the small temperature difference between the wall and liquid/vapor interface required for operation of the boiler at the desired high boiling heat flux at the liquid/vapor interface with minimal decomposition of the boiler fluid.
  • the present invention provides a rotary boiler that may be constructed in relatively small, compact size having high strength characteristics.
  • a boiler is especially suited for use with high molecular weight organic power fluids and provides high heat fluxes at the liquid/vapor interface withminimal decomposition of the power fluid and substantially lower heat fluxes at the peripheral boiler wall.
  • the resulting tempera ture difference between the boiler wall and the liquid/vapor interface is sufficiently small to enable operation of the rotary boiler in a closed-Rankine-cycle engine at maximum overall thermal efficiency of the engine with fast response to increased heat input.
  • a rotary boiler comprising, a generally cylindrical structure having axially spaced apart side wall portions interconnected by a continuous circumferentially extending peripheral wall defining a boiler chamber,
  • combustion means adjacent the peripheral wall of the boiler operable to heat and vaporize the liquid therein
  • the linear axial spacing of the boiler side walls at said liquid/vapor interface and at said peripheral wall being approximately the same and said peripheral wall being contoured transversely and circumferentially of the boiler to provide a combustion heat conduction peripheral wall having inner and outer surfaces respectively confronting the liquid and combustion means having a total length in the axial direction substantially greater than the linear axial spacing of the boiler side wall portions, thereby providing at the peripheral wall a heat flux substantially less than the heat flux at the liquid/vapor interface and a substantially small temperature difference between the wall and the liquid/vapor interface while still maintaining high boiling heat flux at said liquid/vapor interface.
  • the total length of the contoured combustion heat conduction peripheral wall surface in axial direction is at least one and one-half times the linear axial spacing of the boiler side wall portions at the liquid/vapor interface.
  • the total length of the contoured combustion heat conduction peripheral wall surface in the axial direction is within the range of from about three to about five times the linear axial spacing of the boiler side wall portions at the liquid/vapor interface.
  • the boiler peripheral wall is contoured to provide transversely thereof a plurality of continuous circumferentially extending annular surfaces in contact with the boiler liquid operable to entrain particles of said liquid in paths of movement having both radial and circumferential directional components at different accelerations and speeds relative to the boiler rotation whereby the liquid particles are retained in scrubbing interaction with said annular surfaces a period of time to insure maximum heat conduction from the boiler wall to the boiler liquid.
  • contoured peripheral wall comprises at least one pair of continuous circumferentially extending confronting annular surface portions disposed at outwardly converging acute angles to the rotational axis of the boiler.
  • annular surfaces comprise at least one pair of said surfaces disposed in confronting outwardly converging relation at acute angles to the rotational axis of the boiler.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Paper (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US128076A 1971-03-25 1971-03-25 Rotary boilers Expired - Lifetime US3690302A (en)

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CA (1) CA954395A (it)
CH (1) CH544259A (it)
DE (1) DE2214566A1 (it)
FR (1) FR2131611A5 (it)
GB (1) GB1345485A (it)
IT (1) IT952385B (it)
NL (1) NL7203994A (it)
SE (1) SE367695B (it)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3791349A (en) * 1973-01-29 1974-02-12 Sonaqua Inc Steam generator
US4232733A (en) * 1979-05-16 1980-11-11 Etablissement Euroburner Thermal exchanger
USRE32169E (en) * 1976-07-23 1986-06-03 Etablissement Euroburner Thermal exchanger
US4785631A (en) * 1986-08-29 1988-11-22 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Waste-heat turbine unit
US5188090A (en) * 1991-04-08 1993-02-23 Hydro Dynamics, Inc. Apparatus for heating fluids
US5385298A (en) * 1991-04-08 1995-01-31 Hydro Dynamics, Inc. Apparatus for heating fluids
US5931153A (en) * 1998-07-09 1999-08-03 Giebeler; James F. Apparatus and method for generating heat
US5957122A (en) * 1998-08-31 1999-09-28 Hydro Dynamics, Inc. C-faced heating pump
US20040062647A1 (en) * 2002-09-26 2004-04-01 Garrett Norman H. Roto-dynamic fluidic systems
US20060029491A1 (en) * 2002-09-26 2006-02-09 Garrett Norman H Iii Roto-dynamic fluidic systems
RU2285199C2 (ru) * 2004-12-21 2006-10-10 Олег Петрович Кряжевских Паровой котел с вращающимся парогенератором
US7856170B2 (en) 2005-03-15 2010-12-21 Rational Ag Device for producing steam and cooking appliance
CN106052114A (zh) * 2016-05-31 2016-10-26 芜湖鸣人热能设备有限公司 旋转加热式锅炉
US10222056B2 (en) 2011-05-19 2019-03-05 Cavitation Holdings, Llc Apparatus for heating fluids
EP3754181A4 (en) * 2018-02-14 2021-09-29 Ida Covertruck SL ENERGY CONVERSION DEVICE

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1307690B1 (de) 2000-08-09 2006-10-04 Rational AG Verfahren und vorrichtung zum erzeugen von dampf, insbesondere für ein gargerät
DE102009022773A1 (de) 2009-05-19 2010-11-25 Wolfgang Maier Rotationsverdampfer

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2098841A (en) * 1937-04-10 1937-11-09 Heil Co Steam generator
US3051144A (en) * 1958-10-06 1962-08-28 Dynamic Engineering Corp Rotary hot water and steam generator
US3590786A (en) * 1970-02-18 1971-07-06 Du Pont Rotary boiler

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2098841A (en) * 1937-04-10 1937-11-09 Heil Co Steam generator
US3051144A (en) * 1958-10-06 1962-08-28 Dynamic Engineering Corp Rotary hot water and steam generator
US3590786A (en) * 1970-02-18 1971-07-06 Du Pont Rotary boiler

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3791349A (en) * 1973-01-29 1974-02-12 Sonaqua Inc Steam generator
USRE32169E (en) * 1976-07-23 1986-06-03 Etablissement Euroburner Thermal exchanger
US4232733A (en) * 1979-05-16 1980-11-11 Etablissement Euroburner Thermal exchanger
US4785631A (en) * 1986-08-29 1988-11-22 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Waste-heat turbine unit
US5188090A (en) * 1991-04-08 1993-02-23 Hydro Dynamics, Inc. Apparatus for heating fluids
US5385298A (en) * 1991-04-08 1995-01-31 Hydro Dynamics, Inc. Apparatus for heating fluids
US6164274A (en) * 1998-07-09 2000-12-26 Giebeler; James F. Apparatus and method for heating fluid
US5931153A (en) * 1998-07-09 1999-08-03 Giebeler; James F. Apparatus and method for generating heat
US5957122A (en) * 1998-08-31 1999-09-28 Hydro Dynamics, Inc. C-faced heating pump
US20040062647A1 (en) * 2002-09-26 2004-04-01 Garrett Norman H. Roto-dynamic fluidic systems
US6974305B2 (en) 2002-09-26 2005-12-13 Garrett Iii Norman H Roto-dynamic fluidic systems
US20060029491A1 (en) * 2002-09-26 2006-02-09 Garrett Norman H Iii Roto-dynamic fluidic systems
RU2285199C2 (ru) * 2004-12-21 2006-10-10 Олег Петрович Кряжевских Паровой котел с вращающимся парогенератором
US7856170B2 (en) 2005-03-15 2010-12-21 Rational Ag Device for producing steam and cooking appliance
US10222056B2 (en) 2011-05-19 2019-03-05 Cavitation Holdings, Llc Apparatus for heating fluids
US11320142B2 (en) 2011-05-19 2022-05-03 Cavitation Holdings, Llc Apparatus for heating fluids
CN106052114A (zh) * 2016-05-31 2016-10-26 芜湖鸣人热能设备有限公司 旋转加热式锅炉
EP3754181A4 (en) * 2018-02-14 2021-09-29 Ida Covertruck SL ENERGY CONVERSION DEVICE

Also Published As

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DE2214566A1 (de) 1972-10-05
CH544259A (de) 1973-11-15
IT952385B (it) 1973-07-20
NL7203994A (it) 1972-09-27
FR2131611A5 (it) 1972-11-10
SE367695B (it) 1974-06-04
CA954395A (en) 1974-09-10
GB1345485A (en) 1974-01-30

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