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WO1998050693A1 - Moteur a echange thermique externe et procede de fonctionnement - Google Patents

Moteur a echange thermique externe et procede de fonctionnement Download PDF

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Publication number
WO1998050693A1
WO1998050693A1 PCT/RU1997/000144 RU9700144W WO9850693A1 WO 1998050693 A1 WO1998050693 A1 WO 1998050693A1 RU 9700144 W RU9700144 W RU 9700144W WO 9850693 A1 WO9850693 A1 WO 9850693A1
Authority
WO
WIPO (PCT)
Prior art keywords
working body
heat
cylinders
groups
volume
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/RU1997/000144
Other languages
English (en)
Inventor
Alexandr Nikolaevich Lischuk
Evgeny Jurievich Muryshev
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/RU1997/000144 priority Critical patent/WO1998050693A1/fr
Priority to AU37890/97A priority patent/AU3789097A/en
Publication of WO1998050693A1 publication Critical patent/WO1998050693A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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

Definitions

  • Branch of Technics The invention relates to the power engineering industry, in particular to the power plants with an engine of external supply of heat energy and it can be used to produce heat, cold, electric power and in other branches of technics, where the plants of this type can be applied.
  • the plant only provides limited economy, conditioned by low efficiency because of big energy loss in a steam and condensing blocks.
  • a Sterling multycylinder engine of double action containing as heat conducting elements primary and secondary heat pipes, the engines cylinders are located V-shapely; the secondary heat machine embraces the heater pipes and the heat-absorbing areas of the primary heat pipes.
  • the heating space with a combustion chamber and a primary heat pipes block are placed in the cavity between the cylinders.(SU, Al 1617173 ).
  • This Stirling engine of double action is characterized by complication in the production technology of the heatexchanger of a primary and secondary circuit, and the applied heating scheme to be realized in this engine does not allow to achieve the efficiency above 0.25.
  • a power plant including a piston-type pump, a cylinder, a butt- end partition dividing an engine cylinder into two volumes, one of them is a pump chamber; inside the cylinders there is a displacing piston and a working piston connected with a pump piston; including also an expansion cavity, a compression cavity and a buffer cavity, thereby, the expansion cavity and the compression cavity are connected with fixed in sequence a heater, regenerator and cooler, made in the form of a heating pipe, fixed into a central hole of the partition and secured on the cylinder, heat ⁇ i j g pipe condensation area is located in the pump chamber, and the heating pipe evaporation area is located in the compression cavity; the pump chamber is equipped with the valves to input and output the overpumped liquid.(SU, Al, 1671930).
  • This device is an engine working on a Stirling cycle, containing six cylinders, in each cylinder there is fixed a piston with a piston -rod dividing the cylinder volume into a hot and a cold cavities, the pistons of all cylinders are connected through the crankshaft by the drive mechanism to be placed in the crankcase, the drive mechanism is made as a rodless power mechanism with a four- support crankshaft, including three worm journals, located relatively one to another at the angle of 120, on each of them two intermediate links are mounted by a socket joint, which ones are jointly connected with the corresponding slider connected with the piston- rod and fixed in guides made in the crankcase co-axialy with the cylinder.
  • This device is characterized by troubles in keeping balance, by vague bounds of a hot and a cold cavities due to heat overflow, what finally decreases the efficiency.
  • the efficiency of the machines, working in this way is restricted by value 0.2
  • the compression cylinders are fixed to be divided into not less than two groups, thereby, a volume of the cylinders of the first in the direction of the working body movement group is larger , than the volume of the last group; the expansion cylinders are fixed to be divided into not less than two groups; thereby, the volume of the first in the direction of the working body movement group is smaller than the cylinders volume of the last group, and between these groups the intermediate heat exchangers are fixed.
  • the compression cylinders and expansion cylinders may be fixed to be divided into two groups, thereby, the volumes ratio of the compression cylinders groups is 4:1-1.5:1 and that one of the expansion cylinders is relatively 1 :1.5 - 1 :4 in the direction of the working body movement.
  • the engine as to this invention contains an additional heat exchanger fixed in the upper part of the combustion chamber, the outlet of which is connected with the block supplied the air into the combustion chamber, and the inlet is connected with the outlet of the heat-absorbing circuit of the working body heat exchanger-cooler.
  • the engine according to the invention can contain adjustable holes, located between the outlet of the additional heat-exchanger- heater and the block supplied the air into the combustion chamber.
  • the heat machines piping can contain the screw areas, in particular, star-shaped in cross-section.
  • An additional heat exchanger-heater fixed in the upper part of the combustion chamber is required for extra heating up of the air, preheated in the heat-absorbing circuit of the heat exchanger-cooler of the working body. Moreover, in this way the exhausting block of combustion products is being cooled and in consequence its premature combustion is being prevented and its durability increases.
  • Adjustable holes located between the outlet of the additional heat exchanger- heater, and a block to supply the air into the combustion chamber provide the possibility to regulate the amount of heated air supplied into the combustion chamber.
  • This additional air having a higher temperature than the external air supplied for combustion allows to provide a higher efficiency of the fuel combustion without additional energy supply for the air preheating and, in consequence, rises the device efficiency in the whole. Since these holes are adjustable, the optimum regime of the fuel combustion can be provided via the variable throughpass cross-section.
  • Screw areas are required to create a torque flow of the working body in the piping relatively to its axis what provides the flow movement in the piping to be stable. It is especially important, if the piping have on their internal surfaces the screw areas, star-shaped in cross-section, the latter are required to decrease the friction resistance under the following movement of the working body in the piping of a round cross- section.
  • This problem was also solved by another invention, namely by a method to run the engine with the external heat exchanger of the working body, which is a way to increase the economy and to improve the environment ecology in heat machines.
  • the execution of the working cycle with the working body cooling by blowing off the heat-absorbing medium through the heat exchanger the fuel combustion is carried out when the heat-absorbing medium having been heated in the heat exchanger is being supplied to the fuel. If this method is carried out in the cylinder-piston machines with the outlet valves, when the working body is being exhausted from the cylinder, the outlet valves are being closed until the cylinder piston reaches the dead point and by the following movement of the piston to the dead point, the pressure is formed in a bad volume above the piston mirror in the range from the initial pressure in the cylinder up to the working pressure.
  • the working body travel can be carried out in the form of a flow with a cross- section shape different from a cross-section shape of the piping, in particular, with a star-shaped flow cross-section with the flow rotation around the axis of travel.
  • This temperature rise allows to use additionally the energy of the combustion products with the aim to produce extra heat and electric energy, what promotes the efficiency rise of this device working by this method. Thereby, the conversion of low potential heat of the cooling air at the outlet from the heat exchanger-cooler of the working body into high potential heat actually takes place. Moreover, due to supply of extra air into the combustion chamber, the completeness of the fuel combustion is enhanced.
  • this method allows to provide ecological improvement. Actually, if the surrounding air contains pollution in a drop-liquid state, preheating of such an air allows to convert partially these pollution from the drop-liquid state into gaseous form, what .provides their complete combustion after supply into the combustion chamber. Thus, dangerous admixtures prior to be contained in the surrounding air burn out what finally promotes the purification of the surrounding air. If the method of the energy conversion is carried out in the cylinder-piston machines with the outlet valves, when the working body is being exhausted from the cylinder its required part is preferably being preserved in the cylinder, which is sufficient to create the working pressure in a bad volume above the piston mirror in the range from the initial pressure in the cylinder up to the working pressure.
  • valve movement control can be carried out by means of a profiled cam, connected with the crankshaft of the cylinder- piston machine.
  • the working body travel along the engine piping can be carried out in the regime of the flow with the cross-section shape different from the cross-section shape of the piping, what sufficiently decreases the resistance of air flow movement in the piping due to the friction against the piping walls.
  • the star-shaped flow cross-section is preferable, as providing the minimum loss by friction. To stabilize this flow, the flow rotation around the axes of travel can be created.
  • Fig.l shows the main engine scheme.
  • Fig.2 shows the engine thermodynamic cycle.
  • Fig.3 shows star-shaped cross-section of piping.
  • the engine contains two groups of expansion cylinders 1 and 2,3., two groups of compression cylinders 4,5 and 6, fixed on the common crankshaft 7, a heat exchanger 8 and an intermediate external heater of the working body 9, a fuel combustion chamber 10 with a fuel burner 11, a regenerator 12, an intermediate cooler 13, a cooler 14, a fan 15.
  • Position 16 shows an additional heat exchanger- heater fixed in the upper part of the combustion chamber 10. Between the entrance of the additional heat exchanger 16 and the block pumping the air into the combustion chamber there is an adjustable hole 17 with a throttle 18.
  • the piping areas marked with (*) are made with the screw areas star-shaped in cross-section.
  • a thermodynamic cycle shown in T-S coordinates includes a compression process 1-2, from the pressure Pi to the pressure P 2 , a heat-absorbing process from the temperature T 2 , to the temperature T 3 , a compression process from the pressure P 2 to the pressure P 3 and temperature T , than a heating process in the regenerator from the temperature T to the temperature Ts, a heating process in the heat exchanger of the combustion chamber from the burning temperature Ts to the temperature TO, an expansion process from the pressure P 3 to the pressure P 2 , a heating process in the additional heater from the temperature T 7 to the temperature T 8 , an expansion process from the pressure P 2 to the pressure Pi and to the temperature T9, a cooling in the regenerator from the temperature T9 to the temperature T10 and a cooling in the cooler from the temperature T10 to the temperature Ti. Further this process is repeated.
  • the engine runs in the following way. Compressed up to the pressure P 2 , the working body from the first group of the cylinders 4 and 5 is supplied into the intermediate cooler 13, where it is cooled down to the temperature T 3 , after that it travels into the second group of the cylinders 6, where it is compressed up to the pressure P 4 and temperature T . From the cylinder 6 the working body goes into the regenerator 12, where it is heated up to the temperature T5 and then passes into the heat exchanger 8 of the combustion chamber 10, where it is heated up to the temperature TO at the account of the energy of the fuel, supplied along the pipe.
  • the working body enters the first group of the expansion cylinders 1 where it is expanded up to the pressure P 2 and the temperature T , after that it follows into the intermediate heater 9, where it is heated up to the temperature T 8 . Then the working body goes into the second group of the expansion cylinders 2 and 3, where it is expanded up to the pressure Pi and the temperature T9.
  • the efficient work of all the expansion cylinders is sufficiently higher than the work of its compression in all the compression cylinders, due to that a positive torque moment occurs on the crankshaft 7. From the cylinders 2 and 3 the working body goes into the regenerator 12 where it is being cooled down to the temperature Tio.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

Cette invention se rapporte à l'industrie de la production d'énergie électrique et, plus particulièrement, à des centrales électriques possédant un moteur d'alimentation externe en énergie thermique. Cette invention peut être utilisée dans la production de chaleur, de froid, d'énergie électrique, ainsi que dans d'autres branches des techniques où des installations de ce type peuvent être utilisées. Un moteur assurant l'échange thermique externe du milieu de travail comprend des cylindres de compression (4, 5, 6) et des cylindres d'expansion (1, 2, 3) dudit milieu de travail, ainsi que des échangeurs de chaleur. Les cylindres de compression (4, 5, 6) sont fixes et se divisent en au moins deux groupes (4, 5 et 6). Le volume du premier groupe, dans le sens du déplacement du milieu de travail, est supérieur au volume du dernier groupe. Les cylindres d'expansion (1, 2, 3) sont fixes et se divisent en au moins deux groupes (1 et 2, 3). Le volume du premier groupe, dans le sens du déplacement du milieu de travail, est inférieur au volume du dernier groupe. Des échangeurs de chaleur (9, 13) intermédiaires sont montés entre ces groupes. Cette invention concerne également un procédé qui permet d'améliorer les caractéristiques économiques et écologiques de moteurs assurant l'échange thermique externe du milieu de travail lors de la combustion du carburant. Pendant le cycle de fonctionnement, le milieu de travail est refroidi en soufflant le milieu absorbant la chaleur à travers l'échangeur de chaleur. La combustion du carburant se fait lorsque le milieu absorbant la chaleur, qui a été chauffé dans l'échangeur de chaleur, est envoyé dans le carburant.
PCT/RU1997/000144 1997-05-08 1997-05-08 Moteur a echange thermique externe et procede de fonctionnement Ceased WO1998050693A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/RU1997/000144 WO1998050693A1 (fr) 1997-05-08 1997-05-08 Moteur a echange thermique externe et procede de fonctionnement
AU37890/97A AU3789097A (en) 1997-05-08 1997-05-08 Engine with external heat exchanging and method of operating

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/RU1997/000144 WO1998050693A1 (fr) 1997-05-08 1997-05-08 Moteur a echange thermique externe et procede de fonctionnement

Publications (1)

Publication Number Publication Date
WO1998050693A1 true WO1998050693A1 (fr) 1998-11-12

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PCT/RU1997/000144 Ceased WO1998050693A1 (fr) 1997-05-08 1997-05-08 Moteur a echange thermique externe et procede de fonctionnement

Country Status (2)

Country Link
AU (1) AU3789097A (fr)
WO (1) WO1998050693A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB446768A (en) * 1934-11-23 1936-05-06 Wilhelm Mauss Improvements in or relating to heat engines
GB650934A (en) * 1941-11-08 1951-03-07 John Kreitner Improvements relating to a method of producing power in heat engines through cyclic changes of a gaseous working fluid
US3841136A (en) * 1972-03-07 1974-10-15 Universal Oil Prod Co Method of designing internally ridged heat transfer tube for optimum performance
FR2288856A1 (fr) * 1974-06-12 1976-05-21 Kovacs Andre Machine thermodynamique a cycle de carnot
SU785570A2 (ru) 1978-07-10 1980-12-07 Брестский Завод Газовой Аппаратуры "Газаппарат" Планетарный шариковый редуктор
EP0223534A2 (fr) * 1985-11-22 1987-05-27 Pentagon Radiator (Stafford) Limited Echangeurs de chaleur
SU1617173A1 (ru) 1988-02-29 1990-12-30 Брянский Институт Транспортного Машиностроения Многоцилиндровый двигатель Стирлинга двойного действи
SU1671930A1 (ru) 1989-05-30 1991-08-23 Мгту Им.Н.Э.Баумана Силова установка
DE4343405A1 (de) * 1993-12-18 1995-06-22 Friedrich Ambs Gmbh & Co Kg Ap Rohr, insbesondere zur Verwendung als Wärmetauschrohr für Rohrbündelwärmeübertrager
US5590528A (en) * 1993-10-19 1997-01-07 Viteri; Fermin Turbocharged reciprocation engine for power and refrigeration using the modified Ericsson cycle

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB446768A (en) * 1934-11-23 1936-05-06 Wilhelm Mauss Improvements in or relating to heat engines
GB650934A (en) * 1941-11-08 1951-03-07 John Kreitner Improvements relating to a method of producing power in heat engines through cyclic changes of a gaseous working fluid
US3841136A (en) * 1972-03-07 1974-10-15 Universal Oil Prod Co Method of designing internally ridged heat transfer tube for optimum performance
FR2288856A1 (fr) * 1974-06-12 1976-05-21 Kovacs Andre Machine thermodynamique a cycle de carnot
SU785570A2 (ru) 1978-07-10 1980-12-07 Брестский Завод Газовой Аппаратуры "Газаппарат" Планетарный шариковый редуктор
EP0223534A2 (fr) * 1985-11-22 1987-05-27 Pentagon Radiator (Stafford) Limited Echangeurs de chaleur
SU1617173A1 (ru) 1988-02-29 1990-12-30 Брянский Институт Транспортного Машиностроения Многоцилиндровый двигатель Стирлинга двойного действи
SU1671930A1 (ru) 1989-05-30 1991-08-23 Мгту Им.Н.Э.Баумана Силова установка
US5590528A (en) * 1993-10-19 1997-01-07 Viteri; Fermin Turbocharged reciprocation engine for power and refrigeration using the modified Ericsson cycle
DE4343405A1 (de) * 1993-12-18 1995-06-22 Friedrich Ambs Gmbh & Co Kg Ap Rohr, insbesondere zur Verwendung als Wärmetauschrohr für Rohrbündelwärmeübertrager

Also Published As

Publication number Publication date
AU3789097A (en) 1998-11-27

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