EP2037113A2 - Machine à énergie thermique - Google Patents

Machine à énergie thermique Download PDF

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Publication number
EP2037113A2
EP2037113A2 EP20080014610 EP08014610A EP2037113A2 EP 2037113 A2 EP2037113 A2 EP 2037113A2 EP 20080014610 EP20080014610 EP 20080014610 EP 08014610 A EP08014610 A EP 08014610A EP 2037113 A2 EP2037113 A2 EP 2037113A2
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EP
European Patent Office
Prior art keywords
cylinder
working
heat engine
additional
piston
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.)
Withdrawn
Application number
EP20080014610
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German (de)
English (en)
Inventor
Schlager Leopold
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Individual
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Individual
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Publication date
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Publication of EP2037113A2 publication Critical patent/EP2037113A2/fr
Withdrawn legal-status Critical Current

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    • 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
    • F02G1/045—Controlling
    • F02G1/05—Controlling by varying the rate of flow or quantity of the working gas

Definitions

  • the present invention relates to a heat engine for generating mechanical energy with a first cylinder and a working cylinder in which a working piston is movably mounted, wherein between the first cylinder and the working cylinder at least one connection is provided, via which a working medium between the first cylinder and the Working cylinder is replaceable, and wherein a heater for heating the working fluid in the first cylinder and a cooling for cooling the working fluid in the first cylinder are provided, wherein at least one additional cylinder is provided, which is connectable via a shut-off valve with the first cylinder, wherein by opening the valve an overflow possibility for the working medium between the first cylinder and the additional cylinder can be provided
  • Such heat engines are in the prior art z. B. known as Stirling engines. These are heat engines, in which a closed working medium - usually a gas, such as air or helium - is heated from the outside to two different locations and cooled to generate mechanical energy.
  • the Stirling engines operate in a closed loop process and can be powered by any external heat source. With the Stirling engine, the working fluid stays inside the engine and is not replaced. This means that it operates without the emission of exhaust gases except for an optional external combustion heat source.
  • the working piston of the Stirling engine usually drives a crankshaft via a corresponding crank mechanism. This has the disadvantage that only in a small work area, the maximum torque is transmitted to the crankshaft.
  • the Stirling engines have the problem of very low efficiency. In addition, the control is usually difficult.
  • the object of the invention is to improve generic heat engines to the effect that a better efficiency can be achieved.
  • the valve By opening the valve, it is possible, in contrast to conventional Stirling engines, to bring about a sudden tearing off of the pressure difference. In this case, after opening the valve not only the pressure between the two cylinders but also temperature and mass between the two pressure ranges of the heat engine is moved. This makes it possible to bring the working piston to a standstill, which allows the desired, with respect to the efficiency favorable angular control.
  • the pressure compensation has the advantage that the cold pressureless working fluid is preheated in the one cylinder by the incoming pressurized and warm working fluid from the other cylinder and pre-compressed, so that during subsequent heating of the working medium in the first-mentioned cylinder less energy or heat must be introduced.
  • the mass transport also has the advantage that a high degree of filling in the cylinder is achieved.
  • heat is removed from the remaining in the second-mentioned cylinder working fluid by the pressure equalization, which leads there in addition to a very rapid pressure reduction to a pre-cooling, whereby less heat must be removed from the working fluid by means of cooling.
  • the system retains energy.
  • less heat must be supplied and on the other side less heat has to be dissipated. Overall, this leads to a significant increase in the efficiency of the heat engine.
  • the negative effect of dead spaces in the machine by the pre-compression or pre-relaxation is significantly reduced.
  • the additional cylinder has a heater for heating the working medium and a cooling for cooling the working medium.
  • heating and cooling are to be understood very broadly. Virtually any source of cooling or heat can be used. A heating but also a cooling can z. B. by appropriate heating or cooling devices. But it is also possible to realize the heating or cooling by the ambient temperature of the heat engine, when on the other hand, the desired temperature difference is provided by a corresponding cooling or heating.
  • a cooling z. B. a known per se water cooling or air cooling can be provided.
  • any heat source such. B. waste heat from power plants, solar energy o. The like. Be used.
  • a particular advantage is that the heat engine according to the invention can generate mechanical energy even at comparatively small temperature differences between the warm and the cool side.
  • the temperature difference between heating and cooling is favorably at least 100 ° C.
  • the heat source usually does not have to be modified to this end. It is sufficient if the heat engine according to the invention to the (Ab-) heat-emitting part so quasi attached to the exhaust of an existing power plant or the like.
  • the concept of the cylinder in the context of the invention must be understood very general. Basically, this is a closed up to the necessary supply and discharge container in which the working medium is located. Although this is a preferred embodiment, the cylinder does not necessarily have a cylindrical shape in the sense of the invention.
  • the cylinder and / or the additional cylinder as so-called displacer cylinders with a displacer mounted movably therein.
  • the displacer can then, as known from the Stirling engine, displace the working fluid from the heated portion and move it into the cooled portion of each displacement cylinder and vice versa.
  • so-called regenerators can be used for temporary storage of heat in the displacer.
  • a flexible transmission device z. B. is provided in the form of a chain or a belt which the movement of the Working piston on at least one wheel, preferably two wheels transmits.
  • this transmission device is guided around the wheel or the wheels in certain areas on a lateral surface of the wheel. This ensures that over a large part of the stroke of the working piston, a constant and maximum possible torque is generated at the wheel or wheels.
  • at least one bearing shaft of one of the wheels is used as the output and brought into contact with a corresponding transmission. It is possible to run the heat engine itself with a low operating speed, which creates space for correspondingly long time intervals for the heat exchange. Higher speeds or faster movements can then be generated by corresponding transmission gear.
  • a working medium are conveniently gases such. B. air used. But it can also be used as a working fluid liquids. It is favorable to set an increased base pressure in the working medium before the first heating and cooling of the heat engine. This is depending on the size of the heat engine conveniently between 10 bar and 80 bar. By building up this basic pressure, a particularly large amount of gas or working medium is present in the cycle of the heat engine.
  • the heat engine illustrated in the figures has a first cylinder in the form of the displacement cylinder 1a and an additional cylinder in the form of the additional displacement cylinder 1b. Both cylinders as well as the working cylinder 6 are filled with working fluid. In all figures, the heated working medium is shown dotted. The cooled working medium is illustrated by crosses. Between the displacement cylinders 1a and 1b, a direct transfer for the working fluid is provided, which can be closed and opened by the valve or pressure compensation valve 4. In the closed state, an exchange of working medium between the displacement cylinders 1a and 1b on this Wegsamkeit is not possible. In the open state of the valve 4, an overflow possibility for the working medium is provided between these two cylinders.
  • the valve 4 can basically be embodied in various forms known per se.
  • the actuator 27 may, for. B. electric, electromagnetic, pneumatic, hydraulic or operated by another engine.
  • the actuator 27 may, for. B. electric, electromagnetic, pneumatic, hydraulic or operated by another engine.
  • separate heaters 14 and 15 are provided in this example. These can also be coupled with each other.
  • the inlets 31 and 33 each have a heating medium such. As hot water or steam supplied.
  • the heat to be used can, for. B. by solar energy, waste heat o. The like. Be provided. But it is also possible any other type of heating.
  • the respective upper portion of the interior of the displacement cylinder 1a and 1b of the respective heated area can, for. B. electric, electromagnetic, pneumatic, hydraulic or operated by another engine.
  • a respective cooling 12 and 13 is provided in the lower region of the two displacement cylinders. These two coolings are coupled together.
  • the cooling medium such. B. cooling water enters in this embodiment through the inlet 29 and through the drain 30 again.
  • This type of cooling is just one embodiment. It can also be replaced by any other suitable type of cooling.
  • a displacement piston 2 a and 2 b is provided in each case.
  • these are movable up and down between a first position and a second position. In one of these positions they displace the working fluid from the heated area in the cooled area in the opposite position, they displace the working fluid from the respective cooled area in the heated area. It is favorable to support the displacer piston 2a and the additional displacer 2b in each case by way of a suspension in a freely suspended manner in the displacer cylinders 1a or 1b. It can be provided that the two displacer 2 a and 2 b are forcibly coupled with each other about their suspensions with respect to their mobility.
  • Both displacement pistons 2 a and 2 b have overflow openings 22 through which the working medium can flow. These run in the exemplary embodiment shown both through the displacement piston and laterally past them.
  • the overflow openings 22 serve to allow the working medium to flow through them or past them when the displacers 2a and 2b are displaced.
  • regenerators 23 for the intermediate storage of heat. These are preferably in heat-conducting connection with the overflow openings 22.
  • regenerators 23 are known for Stirling engines. Also for the embodiments according to the invention such types of regenerators can be used.
  • the design-related large and heavy displacement pistons 2a and 2b positively coupled via the timing chain 16 connected to each other in the stationary displacement cylinders 1a and 1b.
  • they compensate their own weight, whereby only a small amount of force has to be expended for displacing the displacement pistons 2a and 2b.
  • the piston rods 17 can be made very thin, since without exception tensile loads occur.
  • the piston rod seals 26 generate little friction. A floating of the displacers 2a and 2b can not occur due to the high internal operating pressure. Due to the described forced coupling of the displacement piston 2a and 2b and the weight compensation achieved thereby reaches a relatively weak drive for moving the displacer 5 off. In the embodiment shown this is - shown schematically - designed as a pneumatic control cylinder.
  • Both displacement cylinders 1a and 1b are connected via the respective lines 3a and 3b in the form of the working cylinder 6 that can flow through the connecting lines 3a and 3b working fluid from the displacement cylinders 1a and 1b in the working cylinder 6.
  • the displaceably arranged in the working cylinder 6 working piston 7 and arranged in the counter-cylinder 18 opposed piston 8 and the closed valve 4 separate the two pressure ranges 19 and 20 from each other.
  • the working piston 7 is designed as a double-acting piston by being acted upon in the working cylinder 6 of two opposite sides with working medium.
  • the reference numerals 24 and 25 denote the two dead center positions or reversal points of the working piston 7. Between these points, it is movable back and forth.
  • the working piston 7 is, as is known, sealed against the wall of the working cylinder 6.
  • the working cylinder 6 is conveniently formed as long as possible to allow the largest possible stroke of the working piston. It is advantageous if this maximum possible stroke of the working piston 7 in the working cylinder 6 is at least twenty times, preferably up to fifty times, the maximum diameter of the inner opening width of the working cylinder. Preferably, a bore to stroke ratio in the range between 1:20 and 1:50 is thus provided. It is thought of lengths of the working cylinder of at least 2m or more.
  • the working volume in the working cylinder is favorably about 10% to 50% of the total volume of the heat engine to be filled by the working medium.
  • the working cylinder 6 is designed in the embodiment shown in the form that the working piston 7 can make as long as possible stroke and is moved relatively slowly (eg., 2m / Sec.), But on a large part of his stroke, a constant force and thus transmits a constant torque to the wheels 10 and 11. At such a low piston speed, the winding losses would be at an output via a - in the prior art usually used - crankshaft and the very uniform working pressure significantly above 40%. In addition, a truly angular control would not be possible without the realizable here standstill of the working piston, because also for the displacement of the displacer 2a and 2b time is needed. These disadvantages of a crankshaft drive are avoided by the chain drive shown here. The mass and the speed of the moving parts in the working cylinder 6 are so small that immediately after the settling of the pressure difference between the pressure areas 19 and 20 of the working piston 7 comes to a standstill solely by the friction of the necessary seals or piston rings.
  • the working piston 7 is forcibly coupled in the embodiment shown here with a flexible transmission device which transmits the movement of the working piston 7 to the wheels 10 and 11.
  • the flexible transmission device is formed in the embodiment shown as a chain 9. But this can also be replaced by a band o. The like. It is advantageous if the transmission device does not experience any relevant strain in the forces acting on it.
  • the transmission device is located on the lateral surfaces 37 of the wheels 10 and 11 in regions and is so around the wheels 10 and 11 led around.
  • the transfer device should be so taut that no slippage occurs.
  • the distance between the point 38, on which the transmission device impinges on the lateral surface 37 of the respective wheel 10 or 11, and the point 39, at which the transmission device leaves the lateral surface 37 of the respective wheel 10 or 11 substantially corresponds to Diameter of the respective wheel 10 or 11. Essentially, in this sense, it should be understood that said distance is at least 90%, preferably at least 95%, of the wheel diameter.
  • the provided in the transmission device or chain 9 opposed piston 8 is a seal in the counter-cylinder 18, which essentially serves to separate the two pressure regions 19 and 20.
  • the counter-piston 8 is preferably forcibly coupled to the chain 9 and movable according to the stroke of the working piston 7 in the counter-cylinder 18 back and forth.
  • the minimum diameter of the counter-cylinder 18 is determined by the required thickness of the transmission device or the chain 9, which in turn results from the tensile force of the working piston 7.
  • each serving as an output shaft 21 may be coupled to a corresponding gear.
  • the transmission can also perform a rectifier function, which translates the reciprocating motion of the working piston 7 and thus also the chain 9 in a same direction rotational or linear movement. Suitable transmissions are known in the art, so that a separate representation of this transmission can be omitted here.
  • the working cylinder heater 28 shown here can be provided on the working cylinder 6. It has in the illustrated embodiment, an inlet 35 and a drain 36 for a corresponding heating medium and is used for additional heating of the working fluid in the working cylinder. 6
  • the working medium under elevated temperature and pressure moves the working piston 7 to the left until it reaches the first dead or reverse point 24, in which the working piston 7 comes to a standstill.
  • the pressure difference between the two pressure areas 19 and 20 is caused by the opening of the pressure compensation valve 4 and allows the stoppage of the working piston 7.
  • By opening the pressure compensation valve 4 not only pressure but also temperature and mass between the pressure ranges 19 and 20 is shifted.
  • Part of the pressurized hot working medium from the displacement cylinder 1b is conveyed or blown into the displacement cylinder 1a, which in addition to the pressure equalization, which brings the working piston 7 to a standstill, also preheats the cold pressureless working fluid in the displacement cylinder 1a and precompressed.
  • Fig. 3 shows the time at which the displacers 2a and 2b have reached their opposite end positions.
  • the working piston 7 has traversed depending on the design already 10% to 20% of its stroke between its dead and reverse points 24 and 25.
  • the heat exchange surfaces in the displacement cylinders 1a and 1b have had time for about 2 to 5 seconds, ie more than a hundred times as long as in conventional Stirling series types, in order to effectively transmit even small temperature differences.
  • the incipient continuous volume expansion pushes the working piston 7 approximately uniformly until shortly before reaching the second dead center 25, the pressure valve 4 is opened again and a new power stroke is initiated.
  • the times for opening the pressure compensation valve 4 can be determined by not explicitly drawn here sensors, which detect when the working piston 7 has reached a corresponding position shortly before the respective dead center 24 or 25.
  • the closing of the valve 4 as well as the right time to move the displacer 2 a and 2 b may, depending on this time such. B. be specified by specifying appropriate time differences. But it is also a pressure measurement in the pressure ranges 19 and / or 20 for determining these times possible.
  • the standing time of the working piston 7 in its dead centers 24 and 25 is about 1/10 of the time in which he performs one of his strokes on the way between the two dead centers 24 and 25.
  • the working medium or gas remains inside the heat engine and is not replaced. The shown heat engine thus does not produce exhaust gases or emissions itself.

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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)
EP20080014610 2007-09-11 2008-08-18 Machine à énergie thermique Withdrawn EP2037113A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT14212007A AT505645B1 (de) 2007-09-11 2007-09-11 Wärmekraftmaschine

Publications (1)

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EP2037113A2 true EP2037113A2 (fr) 2009-03-18

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EP20080014610 Withdrawn EP2037113A2 (fr) 2007-09-11 2008-08-18 Machine à énergie thermique

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AT (1) AT505645B1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010034780A3 (fr) * 2008-09-24 2010-08-05 Wuerz Raimund Machine thermique et procédé permettant de la faire fonctionner
DE102016122156A1 (de) * 2016-08-10 2018-02-15 Yves-Michael Kiffner Wärmezyklusmaschine
DE112010006142B3 (de) 2009-10-28 2022-03-24 Global Cooling, Inc. Schmiermittelfreie Freikolben-Stirlingmaschine reduzierter Masse mit hin- und her gehendem Kolben, antriebskoppelnd verbunden mit rotierendem elektromagnetischem Wandler, der sich rotatorisch schwingend bewegt
WO2022198246A1 (fr) * 2021-03-26 2022-09-29 Hofbauer Fritz Machine à fluide chaud

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3248870A (en) 1960-07-29 1966-05-03 Morgenroth Henri Stirling cycle engine divided into a pressure generating unit and energy converting unit
EP1116872A1 (fr) 2000-01-17 2001-07-18 Claassen Energy Systems Dispositif de conversion d'énergie thermique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB769368A (en) * 1955-03-30 1957-03-06 James Windrum Improvements in hot gas reciprocating engines
US3407593A (en) * 1967-04-10 1968-10-29 Donald A. Kelly Reciprocating stirling cycle engine with dual wave cam drive

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3248870A (en) 1960-07-29 1966-05-03 Morgenroth Henri Stirling cycle engine divided into a pressure generating unit and energy converting unit
EP1116872A1 (fr) 2000-01-17 2001-07-18 Claassen Energy Systems Dispositif de conversion d'énergie thermique

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010034780A3 (fr) * 2008-09-24 2010-08-05 Wuerz Raimund Machine thermique et procédé permettant de la faire fonctionner
DE112010006142B3 (de) 2009-10-28 2022-03-24 Global Cooling, Inc. Schmiermittelfreie Freikolben-Stirlingmaschine reduzierter Masse mit hin- und her gehendem Kolben, antriebskoppelnd verbunden mit rotierendem elektromagnetischem Wandler, der sich rotatorisch schwingend bewegt
DE102016122156A1 (de) * 2016-08-10 2018-02-15 Yves-Michael Kiffner Wärmezyklusmaschine
WO2018028735A1 (fr) 2016-08-10 2018-02-15 Kiffner Yves Michael Machine à cycle de chaleur
DE102016122156B4 (de) 2016-08-10 2018-06-14 Yves-Michael Kiffner Wärmezyklusmaschine
US10738734B2 (en) 2016-08-10 2020-08-11 Yves-Michael Kiffner Heat cycle machine
WO2022198246A1 (fr) * 2021-03-26 2022-09-29 Hofbauer Fritz Machine à fluide chaud

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Publication number Publication date
AT505645B1 (de) 2009-05-15
AT505645A1 (de) 2009-03-15

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