US3838668A - Combustion engine heat removal and temperature control - Google Patents

Combustion engine heat removal and temperature control Download PDF

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Publication number
US3838668A
US3838668A US00317947A US31794772A US3838668A US 3838668 A US3838668 A US 3838668A US 00317947 A US00317947 A US 00317947A US 31794772 A US31794772 A US 31794772A US 3838668 A US3838668 A US 3838668A
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United States
Prior art keywords
cylinder
combination
casing
heat exchanger
engine
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Expired - Lifetime
Application number
US00317947A
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English (en)
Inventor
L Hays
J Torola
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Biphase Energy Co
IMO Industries Inc
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Individual
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Priority to US00317947A priority Critical patent/US3838668A/en
Priority to JP14418273A priority patent/JPS538012B2/ja
Application granted granted Critical
Publication of US3838668A publication Critical patent/US3838668A/en
Assigned to TRANSAMERICA DELAVAL INC. reassignment TRANSAMERICA DELAVAL INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: RESEARCH-COTTRELL, INC.
Assigned to DOUGLAS ENERGY COMPANY reassignment DOUGLAS ENERGY COMPANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: STETTER MACHINERY CORPORATION
Anticipated expiration legal-status Critical
Assigned to BIPHASE ENERGY COMPANY reassignment BIPHASE ENERGY COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DOUGLAS ENERGY COMPANY
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • F01P9/02—Cooling by evaporation, e.g. by spraying water on to cylinders
    • 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
    • F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
    • F02B61/02—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/22—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point
    • F01P2003/2278—Heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2050/00—Applications
    • F01P2050/16—Motor-cycles
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • a casing extends about an internal combustion engine cylinder to define an evaporator region containing a liquid subject to evaporation during engine heat transfer thereto; a heat exchanger structure receives vapor from the evaporator region for condensation and re turn to the latter; and an expansion chamber offset from the casing is in closed communication with the evaporator region via the heat exchanger structure, the chamber containing a non-condensable gas for the purpose of temperature control.
  • This invention relates generally to the coolingof internal combustion engines. More specifically, it concerns the use of both liquid and gas for cooling engines, in a manner to provide a number of advantages.
  • the invention is embodied in the combination, with an internal combustion engine combustion cylinder or cylinders, of a casing extending in proximity to the cylinder and defining with the latter an evaporator region adjacent a wall of the casing, the evaporator region containing a liquid subject to evaporation in response to heat transfer via the wall during engine operation; a passageway for vapor transport to a heat exchanger structure and condensate return to the evaporator region; a heat exchange surface wherein the heat of vaporization is rejected to air or another cooling fluid, causing the vapor to condense; and, an expansion chamber offset from the casing and in closed communication with the evaporator region via the heat exchanger structure, the chamber containing a non-condensable gas and normally not receiving vapor.
  • Additional objects include the provision for return of the condensate to the heated surface at the engine either by capillary forces or by gravity; the provision of fine mesh screen or other means defining capillary passages carried by the engine cylinder and/or by the referenced passageway to provide capillary structure inducing the return flow of condensate; the adaptation of the invention to the cooling of a motorcycle engine in such manner that the overall size of the engine structure beneath the operator may be substantially reduced; the location of the heat exchanger surface proximate the fuel tank or other portions of the motorcycle structure, in unusually advantageous manner; and the substantial reduction in sizing of the overall engine cylinder structure and associated cooling surfaces.
  • FIG. 1 is a vertical section showing one preferred form of the invention
  • FIG. 2 is a perspective showing of a vehicle, as for example a motorcycle, to which the invention is applied;
  • FIG. 3 is a view like FIG. 2 showing another adaptation to a motorcycle
  • FIG. 4 is a view like FIG. 2 showing a modified adaptation to a motorcycle
  • FIG. 5 is a graph of wall temperature at different locations, during engine operation, and cooling.
  • FIG. 6 is another graph.
  • an internal combustion engine 10 includes a metallic cylinder 11 and a piston 16 reciprocable therein, forming a combustion zone 12.
  • a spark plug in the cylinder head 11a is indicated at 13, and suitable connecting rod and crankshaft components at 14 and 15.
  • the cylinder and head may be two or more separate parts.
  • the illustrated engine is of two-stroke cycle design, characterized in that the cylinder has a side wall with staggered ports 16a and 17. The former admits a combustible fuel-air mixture, to the combustion chamber on the piston up-stroke, and port 17 releases exhaust gas to the exterior on the piston down stroke.
  • the transfer ports are not shown.
  • a casing or jacket as for example that shown at 18, extends in proximity to the cylinderv and an evaporator region 19 is provided between the casing and cylinder.
  • the casing surrounds the cylinder and extends thereover; for maximum heat transfer to the cylindrical evaporator region 19a formed between the casing side wall 18b and cylinder side wall 11b, and to the upper evaporator region 19b formed between the casing top 18a and cylinder head 11a.
  • the hot exhaust fitting or duct 20 forming port 17 bridges the cylindrical evaporator region.
  • the lowermost extent of the cylindrical evaporator region 1911 extending below duct 20 (which may enclose part or all of 'the crank case for cooling thereof) contains liquid 21 subject to evaporation as a result of heat transfer as described, during operation of the engine.
  • an expansion chamber is provided at 22 and a heat exchanger at 23a which may beeither in relatively remotely spaced relation from the casing or closely coupled to the casing and in closed communication with the evaporator region, as for example via a duct or ducting 23.
  • the expansion chamber contains a non-condensable gas 24 (gas which does not condense over all operating conditions of the engine).
  • the vapor produced by evaporation in zone 19 flows through 'passage 23 to the heat exchanger 23a.
  • the heat exchanger may comprise a single tube with fins 26, on the cooling fluid side, or it may consist of many tubes with multiple fins connected to the passage 23,'or it may comprise other suitable fluid to fluid heat exchanger geometry.
  • the heat of condensation is removed from the vapor by the cooling fluid (such as circulating air) causing the vapor to condense on the inner walls.
  • the liquid condensate on such walls flows back to the evaporator section 19, under the influence of gravity or capillary forces produced by capillary structure to be described.
  • the fraction of the heat exchanger passage available to heat transfer is determined by the volume of the uncooled" chamber 22,
  • Capillary means may, with unusual advantage, be provided within the ducting to conduct and otherwise aid such condensate return flow.
  • One suitable type of capillary structure is fine mesh metallic screen 28 spot welded to the metal surfaces or otherwise self supported. Another consists of screen installed over wires which provide a greater interstitial liquid flow area. Still another consists of small passages in the wall covered with screen. Capillary forces act in aid of gravity in returning condensate to the evaporator region, the condensate flowing close to the walls of the duct so as to be shielded from the drag forces associated with vapor flow in the duct toward chamber 22.
  • capillary structure may likewise be applied or built in directly to the cylinder and/or head as at 28a to cause liquid flow against gravity from the bottom of the casing 18 to the sides and top of the cylinde and in the case of other engine types to any part of the engine.
  • the broken outline 40 indicates the usual engine fin structure extent, illustrating the dramatic reduction in cylinder and head dimensions achieved by the invention.
  • FIG. 2 indicates an application of the invention to a multicylinder motorcycle 41, the engine cylinder casing being shown at 18c. and corresponding to casing 18 i in FIG. 1, but enclosing three cylinders instead of one. Elimination of engine fins creates vertical space at 42, enabling the fuel tank 43 to have greater depth. increasing ,fuel capacity and lowering the motorcycle center of gravity.
  • the air heat exchanger structure 26a (corresponding to fins 26 in FIG. 1) is located for example forward of the casing 18c, as is the expansion chamber 22a.
  • FIG. 3 shows another application of the invention to a single cylinder motorcycle 50.
  • the casing 18d surrounding the cylinder and head is connected via duct 23b with heat exchanger structure 22c of which expansion chamber 22b is a part.
  • Ducting 23b (corresponding to duct 23 in FIG. 1) may be flexible. This location of the heat exchanger structure, behind the upper extent of the front wheel fender 58, ensures isolation from mud and dirt thrown by the front wheel, preventing fouling.
  • FIG. 4 shows application of the invention to a rotary piston engine, as for example of Wankel design.
  • a casing extends about a cylinder 81 but is spaced therefrom to form an evaporator region 82 corresponding to region 19 described above.
  • the lowermost extent 82a of that region contains liquid 84 subject to evaporation during engine operation.
  • An expansion chamber, not shown is in communication with the upper extent 82b of the evaporator region as via a duct 83.
  • Capillary structure, as for example mesh, is indicated at 8688 lining the duct 83 and extending over the walls of the casing and cylinder, as shown.
  • a generally triangular rotor 91 rotates in the cylinder and in relation to a combustible mixture inlet port 89 and an exhaust port 90.
  • Typical liquids 21 and 84 include water or Dow- Therm A, and typical non-condensable gases as at 24 include air, nitrogen and Argon.
  • a casing extending in proximity to the cylinder and defining therewith a common evaporator region adjacent both said wall and head and containing a cv an expansion chamber relatively offset from both the casing and heat exchanger structure and in closed communication with said evaporator region solely via said heat exchanger structure, the chamber closed to the exterior and containing a sufficient volume of non-condensable gas that the temperature of the cylinder wall remains substantially constant during engine operation.
  • capillary structure comprises a mesh screen carried by the duct, and located therein.
  • said ducting includes a horizontal section, and a vertical section extending to said expansion chamber and carrying integral cooling fins, the expansion chamber located above the level of all said fins, the volume of the expansion chamber substantially exceeding that of the heat exchanger interior passage means.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
US00317947A 1972-12-26 1972-12-26 Combustion engine heat removal and temperature control Expired - Lifetime US3838668A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US00317947A US3838668A (en) 1972-12-26 1972-12-26 Combustion engine heat removal and temperature control
JP14418273A JPS538012B2 (cs) 1972-12-26 1973-12-26

Applications Claiming Priority (1)

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US00317947A US3838668A (en) 1972-12-26 1972-12-26 Combustion engine heat removal and temperature control

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JP (1) JPS538012B2 (cs)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009417A (en) * 1975-01-27 1977-02-22 General Electric Company Electrical apparatus with heat pipe cooling
US4013047A (en) * 1975-12-12 1977-03-22 General Motors Corporation Engine with combustion wall temperature control means
US4169387A (en) * 1976-12-07 1979-10-02 Hans List Transducer for mechanical measured variables, especially a pressure transducer
US4250953A (en) * 1977-08-12 1981-02-17 Massachusetts Institute Of Technology Piston sealing
US4253431A (en) * 1977-07-29 1981-03-03 Klockner-Humboldt-Deutz Aktiengesellschaft Reciprocating piston internal combustion engine with at least one cylinder bushing
DE3114575A1 (de) * 1981-04-10 1982-10-28 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München "verfahren zur kuehlung von verbrennungsmaschinen"
US4381737A (en) * 1980-11-13 1983-05-03 Turner William H Rotary valved internal combustion engine
US4491101A (en) * 1983-09-06 1985-01-01 Strumbos William P Multiple heat-range spark plug
US4979472A (en) * 1988-02-01 1990-12-25 Poehlmann Anwendungstechnik Gmbh & Co. Kg Internal combustion engine having a hermetically sealed heat exchanger tube system
US5385446A (en) * 1992-05-05 1995-01-31 Hays; Lance G. Hybrid two-phase turbine
US5664420A (en) * 1992-05-05 1997-09-09 Biphase Energy Company Multistage two-phase turbine
US5669337A (en) * 1996-05-06 1997-09-23 Ford Global Technologies, Inc. Temperature sensing system for an internal combustion engine
US5685691A (en) * 1996-07-01 1997-11-11 Biphase Energy Company Movable inlet gas barrier for a free surface liquid scoop
US5750040A (en) * 1996-05-30 1998-05-12 Biphase Energy Company Three-phase rotary separator
DE19745758A1 (de) * 1997-10-16 1999-05-06 Guenter Dr Frank Maschinenkühlung durch Phasenübergang (Verdampfungskühlung), insbesondere für Verbrennungsmotoren
US6090299A (en) * 1996-05-30 2000-07-18 Biphase Energy Company Three-phase rotary separator
RU2448262C2 (ru) * 2005-09-29 2012-04-20 Прайм Мувер Интернэшнл, ЭлЭлСи Водородный ротационный двигатель внутреннего сгорания (варианты)
US20120325427A1 (en) * 2006-08-04 2012-12-27 Clarke Allan J Horizontal, underneath motorcycle heat exchanger
US11008927B2 (en) 2019-04-10 2021-05-18 James Moore Alternative method of heat removal from an internal combustion engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5216407U (cs) * 1975-07-23 1977-02-05
JPS5374642A (en) * 1976-12-16 1978-07-03 Hino Motors Ltd Cooling device of engine
JPS5625611U (cs) * 1979-08-03 1981-03-09

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1226180A (en) * 1915-05-18 1917-05-15 Edward Bouton Jr Method of and means for maintaining internal-combustion chambers at an efficient temperature.
US1432518A (en) * 1920-02-03 1922-10-17 James C Armstrong Cooling system for internal-combustion engines
GB404517A (en) * 1932-04-26 1934-01-18 Fusion Moteurs Improvements in evaporative cooling systems for the cylinders of internal combustionengines
US2449110A (en) * 1946-11-04 1948-09-14 Le Roi Company Cooling system for internal-combustion engines
US3390667A (en) * 1965-09-07 1968-07-02 Cie Francaise Thomson Two-stage cooling system for heat machine components
US3448729A (en) * 1967-02-08 1969-06-10 Dow Chemical Co Vapor and droplet separator for ebullient-cooled engines
US3457436A (en) * 1966-11-07 1969-07-22 Teledyne Inc Heat pipes with unique radiator configuration in combination with thermoionic converters
US3525386A (en) * 1969-01-22 1970-08-25 Atomic Energy Commission Thermal control chamber
US3680189A (en) * 1970-12-09 1972-08-01 Noren Products Inc Method of forming a heat pipe
US3731660A (en) * 1971-12-29 1973-05-08 Gen Motors Corp Vapor-cooled internal combustion engine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1226180A (en) * 1915-05-18 1917-05-15 Edward Bouton Jr Method of and means for maintaining internal-combustion chambers at an efficient temperature.
US1432518A (en) * 1920-02-03 1922-10-17 James C Armstrong Cooling system for internal-combustion engines
GB404517A (en) * 1932-04-26 1934-01-18 Fusion Moteurs Improvements in evaporative cooling systems for the cylinders of internal combustionengines
US2449110A (en) * 1946-11-04 1948-09-14 Le Roi Company Cooling system for internal-combustion engines
US3390667A (en) * 1965-09-07 1968-07-02 Cie Francaise Thomson Two-stage cooling system for heat machine components
US3457436A (en) * 1966-11-07 1969-07-22 Teledyne Inc Heat pipes with unique radiator configuration in combination with thermoionic converters
US3448729A (en) * 1967-02-08 1969-06-10 Dow Chemical Co Vapor and droplet separator for ebullient-cooled engines
US3525386A (en) * 1969-01-22 1970-08-25 Atomic Energy Commission Thermal control chamber
US3680189A (en) * 1970-12-09 1972-08-01 Noren Products Inc Method of forming a heat pipe
US3731660A (en) * 1971-12-29 1973-05-08 Gen Motors Corp Vapor-cooled internal combustion engine

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009417A (en) * 1975-01-27 1977-02-22 General Electric Company Electrical apparatus with heat pipe cooling
US4013047A (en) * 1975-12-12 1977-03-22 General Motors Corporation Engine with combustion wall temperature control means
US4169387A (en) * 1976-12-07 1979-10-02 Hans List Transducer for mechanical measured variables, especially a pressure transducer
US4253431A (en) * 1977-07-29 1981-03-03 Klockner-Humboldt-Deutz Aktiengesellschaft Reciprocating piston internal combustion engine with at least one cylinder bushing
US4250953A (en) * 1977-08-12 1981-02-17 Massachusetts Institute Of Technology Piston sealing
US4381737A (en) * 1980-11-13 1983-05-03 Turner William H Rotary valved internal combustion engine
DE3114575A1 (de) * 1981-04-10 1982-10-28 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München "verfahren zur kuehlung von verbrennungsmaschinen"
US4491101A (en) * 1983-09-06 1985-01-01 Strumbos William P Multiple heat-range spark plug
US4979472A (en) * 1988-02-01 1990-12-25 Poehlmann Anwendungstechnik Gmbh & Co. Kg Internal combustion engine having a hermetically sealed heat exchanger tube system
US5946915A (en) * 1992-05-05 1999-09-07 Biphase Energy Company Multistage two-phase turbine
US5385446A (en) * 1992-05-05 1995-01-31 Hays; Lance G. Hybrid two-phase turbine
US5525034A (en) * 1992-05-05 1996-06-11 Biphase Energy Company Hybrid two-phase turbine
US5664420A (en) * 1992-05-05 1997-09-09 Biphase Energy Company Multistage two-phase turbine
US6314738B1 (en) 1992-05-05 2001-11-13 Biphase Energy Company Multistage two-phase turbine
US5720799A (en) * 1992-05-05 1998-02-24 Biphase Energy Company Multistage two-phase turbine
US6122915A (en) * 1992-05-05 2000-09-26 Biphase Energy Company Multistage two-phase turbine
US5669337A (en) * 1996-05-06 1997-09-23 Ford Global Technologies, Inc. Temperature sensing system for an internal combustion engine
US6090299A (en) * 1996-05-30 2000-07-18 Biphase Energy Company Three-phase rotary separator
US5750040A (en) * 1996-05-30 1998-05-12 Biphase Energy Company Three-phase rotary separator
US5685691A (en) * 1996-07-01 1997-11-11 Biphase Energy Company Movable inlet gas barrier for a free surface liquid scoop
DE19745758A1 (de) * 1997-10-16 1999-05-06 Guenter Dr Frank Maschinenkühlung durch Phasenübergang (Verdampfungskühlung), insbesondere für Verbrennungsmotoren
RU2448262C2 (ru) * 2005-09-29 2012-04-20 Прайм Мувер Интернэшнл, ЭлЭлСи Водородный ротационный двигатель внутреннего сгорания (варианты)
US20120325427A1 (en) * 2006-08-04 2012-12-27 Clarke Allan J Horizontal, underneath motorcycle heat exchanger
US9459051B2 (en) * 2006-08-04 2016-10-04 Allan J. Clarke Heat exchanger for horizontal installation under a motorcycle engine
US11008927B2 (en) 2019-04-10 2021-05-18 James Moore Alternative method of heat removal from an internal combustion engine

Also Published As

Publication number Publication date
JPS538012B2 (cs) 1978-03-24
JPS4996141A (cs) 1974-09-11

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