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WO1993007374A1 - Moteur rotatif a cycle stirling - Google Patents

Moteur rotatif a cycle stirling Download PDF

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Publication number
WO1993007374A1
WO1993007374A1 PCT/US1991/007337 US9107337W WO9307374A1 WO 1993007374 A1 WO1993007374 A1 WO 1993007374A1 US 9107337 W US9107337 W US 9107337W WO 9307374 A1 WO9307374 A1 WO 9307374A1
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WO
WIPO (PCT)
Prior art keywords
engine
heat
recited
rotor
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US1991/007337
Other languages
English (en)
Inventor
Bennie D. Macomber
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.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to PCT/US1991/007337 priority Critical patent/WO1993007374A1/fr
Publication of WO1993007374A1 publication Critical patent/WO1993007374A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2242/00—Ericsson-type engines having open regenerative cycles controlled by valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2254/00—Heat inputs
    • F02G2254/30—Heat inputs using solar radiation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to Stirling cycle engines in general and more specifically to improvements using rotary chambers with ports and external heat exchangers to alternately heat and cool the working fluid effectively producing rotational mechanical work.
  • U.S. patent 4,044,559 issued to Kelly discloses a closed series cycle or double-acting reciprocating Stirling engine cycle. Tandem rotary units employ a series gas flow loop using a large number of heat transfer tubes with separation between the hot and cold sources. Hydrogen gas is used as fuel obtained from an electrolysis unit driven by a wind generator. Redshaw employs a rotary Stirling cycle system in U.S patent 3,984,981 utilizing rotors also internal heat exchangers, and displacers as heat regenerators. Chambers are formed with two wedge-shaped spherical sectors connected by a disk-like coupling producing four variable displacement chambers. Sectors contain passageways through hollow shafts covered with fins to provide heat transfer. Porous heat absorbing material becomes the heat regenerator transferring heat from one chamber to the other.
  • Patent 3,958,422 also issued to Kelly uses multiple rotary units having an eccentric rotor with vanes independent from adjacent units. Multiple heat transfer loops with heating and cooling sources provide the regeneration heat transfer. Hydrogen is employed as the working gas with any suitable fuel used as the heat source.
  • Kelly in an earlier patent (3,537,256) uses two simple eccentric rotors with vanes and interconnecting flow paths.
  • a modular split housing allows valves to be connected to both rotors.
  • the heat is optically transmitted to a hot displacer.
  • Photo heat powered by liquid fuel or electrical lamps provides the heat source for the invention.
  • An important object of the invention improves the ultimate efficiency of the apparatus by the complete separation of the high and low temperature working spaces. This is accomplished using ports in each chamber separating the working fluid intake from the discharge. A pair of chambers are utilized with elliptical shaped rotors linked together on a common shaft inside each chamber with the ports having an orientation synchronizing the rotors. This arrangement permits a constant volume heat rejection and addition during a half revolution of the shaft where no work is performed except for that necessary to overcome friction. During the second half revolution work is accomplished by the expansion and contraction of the working fluid.
  • Another object of the invention that is new and novel is the unidirectional flow of working fluid through the heat exchangers.
  • This flow path is unlike prior art where the fluid flows from one end to the other along a gas filled cylinder where the gas is transferred alternately to the hot and cold spaces at the ends of the cylinder with the resultant cyclic temperature changes which cause pressure modulation used to drive an output power piston or the like.
  • the fluid flow path of the present invention now distinctly separates the hot and cold chambers with their accompanying rotors such that a unidirectional flow of the working fluid, or gas, is always present ultimately improving the efficiency of the basic Stirling cycle. Further, this arrangement minimizes the loss of heat by conduction in the mass which completely bypasses the process of producing work.
  • Still another object of the invention is directed to the basic utilization of only one heat exchanger between the high and low temperature working spaces in the inventions simplest form. Further, the res idua l heat remaining after extracting work from the fluid is employed to preheat the working fluid, thus utilizing all of the. heat to its best advantage, rather than purging this heat to atmosphere, after the original task has been accomplished. inasmuch as the heat must be produced in the first place to generate work, the better employment of this energy yields higher efficiency which, ultimately, permits a practical application of the fundamental invention of Stirling.
  • Yet another object of the invention is the use of only rotary motion to produce power, vibration in this type of apparatus is greatly reduced over reciprocating types of engines using pistons within cylinders moving in a linear direction.
  • Engine vibration may be a source of problems to driven equipment therefore, the reduction in potential vibration is an important part of the inventions utility and wide spread application potential.
  • FIGURE 1 is a partial isometric view of the preferred embodiment however, in order to visually depict the heat exchangers in their relative position, they are not necessarily proportionate in size. The view also contains cut-away portions to illustrate the critical operating elements.
  • FIGURE 2 is a schematic diagram of the components within the cycle and the orientation of the rotors relative to the ports and interconnecting heat exchangers.
  • FIGURE 3 is a diagram of the chamber inner geometry depicting the rectangular coordinates forming the elliptical shape.
  • FIGURE 4 is a diagram of the geometry of the rotor shape.
  • FIGURE 5 is a cross-sectional view of one of the rotors within a chamber having the endwalls removed for clarity.
  • FIGURE 6 is a cross-sectional view taken along lines 6-6 of FIGURE 5 illustrating the crankshaft.
  • FIGURE 7 is a diagram of the rotor position at the start of the cycle where there is minimum volume below the rotor on the cold end at the beginning of the constant volume heat transfer phase.
  • FIGURE 8 is a diagram of the rotor position at the end of the heat transfer phase and the beginning of heat expansion and cold contraction of the working fluid phase.
  • FIGURE 9 is a diagram of the rotor position at the end of the heat expansion and cold contraction phase with porting about to occur.
  • FIGURE 10 is a diagram of the rotor position when porting is almost complete and constant volume heat transfer is about to begin on the opposite side of the rotors.
  • FIGURE 11 is a diagram of the components within the cycle including a solar collector for the heat source and all optional heat exchangers to produce an extremely efficient system.
  • FIGURES 1 through 10 The preferred embodiment, as shown in FIGURES 1 through 10 is comprised of at least a pair of hollow chambers 20 placed in end to end relationship as illustrated in FIGURE 1. These chambers 20 are basically the same configuration except for slight variations in connecting locations etc., each chamber further having internal sidewalls 22 and endwalls 24.
  • the basic shape of the chambers 20 is elliptical and it has been determined that the most optimum shape of the ellipse employes rectangular coordinates illustrated in FIGURE 3 calculated by the following mathematical equation:
  • FIGURE 6 and "a" is one half the
  • crankshaft rotational angle in degrees
  • FIGURE 1 best illustrates the preferred embodiment in this area.
  • the chambers 20 further contain a pair of ports, for clarity sake designated the first port 26 and second port 28, with the positioning of the ports relative to each other and the mating chamber of prime importance.
  • FIGURES 2 and 7-10 illustrate this physical location and it will later become apparent as to their functional purpose.
  • Each chamber 20 contains an elliptical shaped rotor 30, only slightly narrower than the chamber, and of such a radial configuration as to have rotatable contact against the inner sidewalls 22.
  • the rotors 30 are free to revolve within the chambers and contain a rotatable tip seal 32 positioned at the narrowest portion of the elliptical shape.
  • This tip seal 32 is well known in the art and seals the rotor 30 against the sidewalls 33 of the chamber and in connection with ports 26 and 28 provides porting of the working fluid 60 as it rotates. Further, the rotor 30 contains a curved groove 34 in each side as shown in FIGURE 5 in which a spring loaded curved side seal 36 is positioned. The side seal 36 interfaces contiguously with the tip seal 32 completely sealing the rotor 30 within the chamber 20.
  • FIGURE 4 This shape and physical layout is depicted in FIGURE 4 and also shown pictorially mating with the chamber 20 in the schematic diagrams.
  • Each rotor 30 contains drive movable orientation means in the form of a centrally located internal toothed ring gear 38 as illustrated in FIGURES 5 and 6.
  • the gear 38 is pressed on or otherwise attached to the rotor and is large enough to almost fill the width of the rotor and is relatively close to the side seals 36.
  • a crankshaft 40 connects the rotors 30 together in tandem as shown in FIGURE 1, at an opposed offset orientation, stationary orientation means in the form of an external tooth pinion gear 42 concentric to the crankshaft 40 is permanently attached to the chamber endwall 24 is illustrated in FIGURE 6.
  • the external teeth of the pinion gear 42 mesh with the internal teeth of the ring gear 38 synchronizing the rotors 30 keeping them in opposed relationship and positioned intimately with the chamber sidewalls 22 as the rotor revolves within the chamber 20.
  • the ring gear 38 has twice as many teeth as the pinion gear 42 causing the rotor 30 to rotate at one half the rate of the crankshaft to maintain a system balance and provide sequence to each rotor revolution relative to the ports 26 and 28.
  • a cooling heat exchanger 44 is connected through conduits 46 between the first ports 26 of each chamber
  • the cooling heat exchanger 44 is an air to gas device arranged in a thermal counter flow orientation allowing mass flow of media in opposed directions.
  • a heating heat exchanger 48 is likewise connected through passageways 50 between the second ports 28 of each chamber 20. This heat exchanger adds heat to the cycle as the basic heat source for engine operation.
  • the heat may be produced by almost any fuel that elevates the temperature usually through a conducting fluid such as air or liquid.
  • the heat source may be any type such as employing a combustion burner 52 as illustrated in FIGURE 2 in the form of fossil fuel i.e., gasoline, diesel butane/propane, natural gas and the like or any other flammable fuel used to produce heat during a combustion process.
  • FIGURE 2 illustrates a burner 52 in conjunction with a combustion chamber 54 where liquid fuel is mixed with ambient air and burned producing heat which is then in communication with the passageway 50 between ports 28.
  • heating means may be also used other than the combustion type described above such as a solar generator 56 depicted schematically in FIGURE 11.
  • the solar generator 56 may be any type known in the art and may use a secondary heat transfer fluid such as a liquid shown in the drawings or any other means together the sun's rays in sufficient concentration to produce heat. It will be noted that the invention is not limited to the heat sources identified in the preferred embodiment as any source of heat may be employed with equal ease and conformity.
  • Any of the above described heating means may also use a conducting fluid -58 such as air or liquid with the heat source elevating the temperature of the conducting fluid 58 and transferring the heat to the engine through mass flow within the heat exchanger 48.
  • a working fluid 60 is sealably contained at a constant volume within the chambers 20 and heat exchangers 44 and 48 provide the operational potential to rotate the rotors 30.
  • the rotors 30 are forced to rotate by expansion and contraction of the fluid 60.
  • the heat extracted by the cooling heat exchanger 44 causes the working fluid 60 to contract or decrease in volume creating a volumetric divergence sweeping the fluid around within and between the chambers 20 causing the cyclic action of the rotors thereby producing work.
  • This working fluid may be any substance suitable for the application including air, or a gas such as elium, hydrogen, chlorinated fluorocartions and the like as these and their gases are good conductors of heat allowing rapid heating and cooling of the working fluid 60.
  • Function of the basic cycle is illustrated schematically in FIGURES 7-10 and for clarity sake may be described as follows:
  • the chamber 20 is nearly circular inside the hollow portion and the rotor 30 is placed inside such that its rotor tips maintain constant contact against the sidewalls 22 providing a seal.
  • the crankshaft 40 revolves such that the center of the crank creates a circle as the shaft rotates.
  • the external toothed gear 42 situated concentric to the shaft is fixed mechanically so as not to rotate and is meshed with the internal toothed gear, having twice the number of teeth and attached to the rotor permitting the rotor to rotate in the chamber 20 at one-half the rate of the shaft 40.
  • the depiction of the gears has been omitted from the schematic in FIGURES 7-10 for reasons of clarity although they are an important part of the invention as they provide the proper positioning of the rotor during rotation.
  • the rotor 30 of the hot end is shown at the bottom of the chamber 20 permitting a minimum volume below the rotor and a maximum volume above the rotor. It may be seen by referring to position 2 in FIGURE 8, as the shaft rotates clockwise, the volume below the rotor is increasing and the volume above the rotor is decreasing, in reaching position 2, the shaft has rotated almost 180 degrees and the rotor has rotated almost 90 degrees. in position 3 shown in FIGURE 9, the volume below the rotor has increased to about the maximum and the volume above has decreased equally.
  • FIGURES 7-10 also illustrate two chambers 20 and rotors 20 connected in tandem on the same crankshaft 40.
  • the cranks of the crankshaft 40 are attached 180 degrees apart and the rotors are configured to be 90 degrees displaced.
  • the chambers have ports 26 and 28 at the circumferential edge as shown to allow connection of the cold chamber at the left to the hot chamber at the right.
  • the attachment also connects the heat exchangers 44 and 48 for the purpose of adding and rejecting heat.
  • the heating heat exchanger 48 at the bottom adds heat and the cooling heat exchanger 44 at the top rejects heat.
  • the second phase of the cycle is the power phase in which the heated working fluid 60 is allowed to expand and cool providing work against the left side of both rotors 30.
  • the end of this phase is shown in FIGURE 9.
  • the hot side expanded while the cold side contracted such that the cooled gas is in the minimum volume space to the right of the cold rotor and the heated fluid is in the maximum volume above the hot rotor and to the left of the cold rotor.
  • the fluid at this point will be at its original temperature and pressure and the process is ready to occur again after the porting processing shown in FIGURE 10.
  • the invention provides constant volume heat addition and rejection during a half revolution of the crankshaft in which no work flows except for that necessary to overcome the forces of friction. During the second half revolution work is provided by the expansion and contraction of the working fluid.
  • the porting process leads to some significant advantages.
  • the working fluid flow is unidirectional except for a small amount of heated fluid going back to the cold end during the expansion phase. This is in contrast to the reciprocating type Stirling engine in which the fluid flows through both heat exchangers in series. Regenerators are required between the heat exchangers in the reciprocating system to maintain the fluid at nearly a constant temperature between the heat exchangers. This provides additional unwanted volume which reduces the pressure available to provide work output. Since the invention sweeps the fluid around the chamber it does not suffer appreciable heat loss because of the separation of mechanical parts that operate at widely different temperatures.
  • FIGURE 11 illustrates the addition of optional heat exchangers to further improve the efficiency of the invention.
  • a regenerative heat exchanger 62 is added between the cooling and heating heat exchanger 44 and 48 allowing residual heat transferred from the cold end of the system to pre-warm the working fluid 60 prior to entering the heating heat exchanger 48.
  • a pre-heat heat exchanger 64 may pre-heat the air entering the burner 52 utilizing all of the heat available furthering the energy utilization process.
  • a remote solar collector 56 may be employed and the heat piped to heat exchanger 48 using a closed heat transfer system.
  • FIGURE 1 The invention is illustrated in FIGURE 1 and in the schematics as having only a pair of chambers 20 and rotors 30 however, it should not be construed that only two must be used as two pair or even three pair may be employed with equal ease and to some advantage in many applications. It should be noted that if two pair are used, the angular displacement would be 180° and 120° for three pair.

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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)

Abstract

Un moteur rotatif à cycle Stirling comporte deux stators creux (20) dotés chacun d'un rotor elliptique (30), qui y tourne de manière à former une liaison étanche avec les parois internes des stators. Un vilebrequin (40) solidarise les rotors et en transmet l'énergie de rotation lorsqu'ils tournent dans les stators. Des échangeurs de chaleur permettant le refroidissement (44) et le réchauffement (48) sont chacun reliés aux parois des rotors par les lumières (26) et (28). Un volume constant de fluide moteur (60) circule dans les stators et les échangeurs de chaleur, faisant tourner les rotors à mesure que leur volume se modifie du fait de l'expansion et de la contraction cycliques dudit fluide. Celui-ci balaie les stators au travers des lumières en se réchauffant et en se refroidissant alternativement dans les échangeurs de chaleur.
PCT/US1991/007337 1991-10-02 1991-10-02 Moteur rotatif a cycle stirling Ceased WO1993007374A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US1991/007337 WO1993007374A1 (fr) 1991-10-02 1991-10-02 Moteur rotatif a cycle stirling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1991/007337 WO1993007374A1 (fr) 1991-10-02 1991-10-02 Moteur rotatif a cycle stirling

Publications (1)

Publication Number Publication Date
WO1993007374A1 true WO1993007374A1 (fr) 1993-04-15

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997001700A1 (fr) * 1995-06-27 1997-01-16 Jeandupeux Pierre Antoine Moteur a combustion externe
US8893497B2 (en) 2012-08-03 2014-11-25 Kithd Technologies, Llc Kinematically independent, thermo-hydro-dynamic turbo-compound generator
CN110360004A (zh) * 2019-08-12 2019-10-22 曾祥云 一种活塞旋转的热机
CN115013147A (zh) * 2022-05-09 2022-09-06 江苏大学 一种促进燃烧室后部燃烧的双转子发动机及其控制策略

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009573A (en) * 1974-12-02 1977-03-01 Transpower Corporation Rotary hot gas regenerative engine
US4206604A (en) * 1978-04-18 1980-06-10 Steven Reich Rotary Stirling cycle machine
US4357800A (en) * 1979-12-17 1982-11-09 Hecker Walter G Rotary heat engine
US4753073A (en) * 1987-10-20 1988-06-28 Chandler Joseph A Stirling cycle rotary engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009573A (en) * 1974-12-02 1977-03-01 Transpower Corporation Rotary hot gas regenerative engine
US4206604A (en) * 1978-04-18 1980-06-10 Steven Reich Rotary Stirling cycle machine
US4357800A (en) * 1979-12-17 1982-11-09 Hecker Walter G Rotary heat engine
US4753073A (en) * 1987-10-20 1988-06-28 Chandler Joseph A Stirling cycle rotary engine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997001700A1 (fr) * 1995-06-27 1997-01-16 Jeandupeux Pierre Antoine Moteur a combustion externe
US8893497B2 (en) 2012-08-03 2014-11-25 Kithd Technologies, Llc Kinematically independent, thermo-hydro-dynamic turbo-compound generator
US10041381B2 (en) 2012-08-03 2018-08-07 Anatoly Sverdlin Kinematically independent, thermo-hydro-dynamic turbocompound generator
CN110360004A (zh) * 2019-08-12 2019-10-22 曾祥云 一种活塞旋转的热机
CN115013147A (zh) * 2022-05-09 2022-09-06 江苏大学 一种促进燃烧室后部燃烧的双转子发动机及其控制策略
CN115013147B (zh) * 2022-05-09 2024-03-19 江苏大学 一种促进燃烧室后部燃烧的双转子发动机及其控制策略

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