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EP0570731B1 - Moteur Stirling avec échangeur de chaleur - Google Patents

Moteur Stirling avec échangeur de chaleur Download PDF

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Publication number
EP0570731B1
EP0570731B1 EP93106852A EP93106852A EP0570731B1 EP 0570731 B1 EP0570731 B1 EP 0570731B1 EP 93106852 A EP93106852 A EP 93106852A EP 93106852 A EP93106852 A EP 93106852A EP 0570731 B1 EP0570731 B1 EP 0570731B1
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EP
European Patent Office
Prior art keywords
housing
stirling engine
bellows
plate
engine according
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Expired - Lifetime
Application number
EP93106852A
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German (de)
English (en)
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EP0570731A1 (fr
Inventor
Eckhart Weber
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Individual
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Individual
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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
    • 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
    • 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
    • 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
    • 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
    • F02G2257/00—Regenerators
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/50—Crosshead guiding pistons

Definitions

  • the invention relates to a Stirling engine with heat exchanger, which is used for low to medium temperature operation, i.e. is designed for a small compression ratio and large displaced volume, in which a displacement plate can be moved back and forth between two housing plates of a housing that are parallel to one another and that is free of sliding friction along the circumference relative to the end faces of the housing, in which the displacement plate has two working gas volumes: expansion space and Separates compression space, which are assigned to the cooler and heater for heat exchange, in which the two working gas volumes are connected via a regenerator, and in which the reciprocating movement of the displacement plate is in phase displacement with a working piston.
  • the invention is based on a Stirling engine as is known from US-A-44 14 814.
  • the ends of the displacement plate 45 are sealed with respect to the housing end faces 10 ', for which purpose connecting strips are provided according to the drawing, which run loosely corrugated between the displacement plate 45 and the housing end face 10' and have a sealing function.
  • the displacement plate 45 is guided solely by means of the rod 20 'in the lower housing plate.
  • the loose corrugated connecting strips have no guiding effect.
  • the larger the displacement plate 45 the more difficult and complex it becomes to guide the rod 20 ′ with as little friction as possible, and to prevent tilting movements of the displacement plate relative to the leading rod. It is also difficult to prevent the displacer plate from rotating about the axis of the leading rod 20 '. Any incorrect movement of the displacement plate caused by poor guidance can lead to the loosely corrugated connecting strip becoming jammed in the gap between the front edges of the displacement plate and the housing end faces. This will lead to malfunctions in the operation of the Stirling engine, which occur more frequently the larger the displacement plate is dimensioned.
  • the housing plates and the displacement plate can be made unusually large, since the surface of the housing plates is stabilized against one another by the struts.
  • a power range of 50 - 500 W can be achieved, the housing plates being several square meters in size and working pressures of 10,000 pa and more occurring in the working gas partial volumes.
  • the struts should pass through the displacement plate as tightly as possible, so that the strut-related
  • the roller membranes enable the struts between the housing plates to be used practically.
  • connection between the displacer plate and the motor shaft can be made in the conventional way exclusively via linkage.
  • movement displacement bellows are provided for the reciprocation of the displacement plate between the latter and the one housing plate, which bellows can be actuated by means of a control bellows, which is conductively connected to the latter for supplying and removing air Motor shaft is contractible and expandable via a connecting rod.
  • the actuation of the displacement plate by means of the air bellows distributed over the surface results in an improved parallel guidance of the displacement plate. In particular, the sliding friction of guided movement rods of the connecting linkage is avoided.
  • the connection of the displacement plate to the motor shaft by means of the movement air bellows, the air supply and removal and the control bellows is important in the case of a considerably enlarged displacement plate, for which precise parallel guidance to the housing plates and low friction during movement are crucial.
  • the volume of the moving air bellows is normally 90 degrees by changing the phase position between the movement of the displacement plate, ie the movement of the control bellows and the movement of the working bellows compensated greater than 90 degrees.
  • the struts can be designed so that they can absorb tensile and compressive forces.
  • a small connection from the engine compartment to the outside ensures that the air pressure in the working bellows is on average identical to the atmospheric pressure.
  • the struts are each designed as tensioning tie rods and a check valve sets the air pressure in the working bellows to the same or greater atmospheric pressure, or the struts are each designed as stiffening supports and a check valve the air pressure in the working bellows to the same or low atmospheric pressure.
  • the function of the struts is clear and the construction work is simplified. Specifying either only pressure ratios or only suction ratios also makes special application options feasible.
  • regenerator is provided on the displacement plate and extends over its entire surface. This simplifies the sealing and guiding relationships between the end edges of the displacement plate and the end walls of the housing. There is also an adaptation of the dimension of the regenerator to the enlarged areas of the heat exchanger according to the invention and the flow resistance of the regenerator is reduced.
  • the regenerator acts through the volume of the displacement plate, which e.g. has a thickness of 0.1 m and e.g. is made of open-pore polyester foam.
  • the moving regenerator forms the heat exchangers on the surfaces facing the housing plates, which move with the housing plate and are designed to allow gas to flow through.
  • the cooler heat exchanger is usually located at the bottom with the horizontal displacement plate.
  • the present Stirling machine in the 50 - 500 W power range is particularly suitable for pumping water, generating cold and electricity or grinding grain in sunny areas. It can be made from simple materials without precision parts and is therefore suitable to be manufactured in non-industrialized countries.
  • the Stirling engine according to FIGS. 1 and 2 comprises a heat exchanger which has an essentially rectangular housing which is formed by two housing plates 1, 2 and by four rectangular housing end walls 10. Struts designed as tie rods 3 are evenly distributed over the surface of the housing plates 1, 2, which are fixed at both ends to one of the housing plates. The tie rods cross through bores 27 of a rectangular displacement plate 5, which is accommodated in the housing and the end edges of which are spaced all around from the housing end walls 10. A long side of a rolling membrane 9 is fastened to the front edges, the other long side of which is fastened directly to the associated front wall 10 of the housing.
  • the rolling membrane 9 is a strip running along the front edge, which forms a fold 21 in the direction of its longitudinal extent.
  • the displacement plate 5 forms the core of a plate-shaped regenerator 18, on the upper surface of which a heater 19 is provided for heat exchange and on the other surface of which a cooler 20 is provided for heat exchange.
  • the displacement plate 5 divides the housing into an expansion space 11 and a compression space 12 and is open at the bottom Lifting bellows 13 mounted.
  • Fluid diversions 36 originate from the lifting bellows 13 and fluid diversion 38 originates from the compression space 12, each leading to a machine part with a crank engine.
  • the fluid diversion 38 leads from the compression space 12 to a working bellows 7, the volume of which is assigned a check valve 6.
  • the working bellows 7 works via a connecting rod 47 on a crankshaft or engine shaft 15 which carries a flywheel 35.
  • the fluid diversions 36 coming from the lifting bellows 13 lead to a control bellows 14, which is connected to the motor shaft 15 via a connecting rod 16.
  • the working bellows 7 and the control bellows 14 are offset from one another by a phase position 17 which is greater than 90 degrees.
  • Fig. 2 illustrates the assignment of the housing plates, the displacement plate 5, the bores 27 and the tie rod 3 to each other.
  • the Stirling engine according to FIG. 3 is constructed to a large extent like that according to FIGS. 1 and 2.
  • the fold direction 34 of the fold formed by the roller membrane 9 runs along each end edge.
  • the regenerator plate 5 is connected to the motor part via a linearly guided push rod 28, which passes through a guide device 48 and engages the motor shaft 15 via a connecting rod 29.
  • the pressure-resistant housing is achieved in that the tie rods 3 brace the two opposite housing plates 1, 2 and the air pressure in the machine through the check valve 6, which only allows air to flow into the machine, to larger or atmospheric pressure is maintained, because tie rods can only be loaded under tension.
  • the working bellows 7 works as a pressure bellows (air pressure in the bellows> atmospheric pressure).
  • the one housing plate 1 can be made of transparent, unbreakable polycarbonate. If, according to FIG. 4, highly transparent, fragile security glass is to be used for the upper housing plate 1, it is particularly simple to take supports 4 instead of the tie rods on which the glass plate rests only loosely.
  • a work bellows 8 now works as a suction bellows (see FIGS. 5 and 6).
  • the glass pane is sucked against the supports and does not break if there is a sufficient number (approx. 25 / m) of supports.
  • the struts are designed so that they can be subjected to both tension and pressure, the pressure in the machine can be kept at atmospheric pressure on average by means of a small bore instead of the check valve which means that the machine needs a smaller flywheel.
  • the tie rods 3 or supports 4 are at right angles to the two parallel housing plates 1, 2 and go at right angles through the displacer plate 5 (FIG. 2), which must be guided exactly without wear and friction and not on the tie rods or struts should graze, although the holes 27, through which the tie rods pass, may hardly be larger than the diameters of the tie rods in order to ensure the separation of expansion and compression space.
  • the displacement plate is very heavy (approx. 30 kg / m). The displacement plate guide must absorb this weight because the machine is to work in all positions.
  • the guide according to the invention consists of the linear rolling membranes 9 (four in the case of a square or rectangular housing) which guide the displacement plate exactly and at the same time free of sliding friction against the housing end wall 10 seal.
  • the linear roller membranes are wear-free, since they are practically not subject to flexing work and, which is essential in the Stirling engine, can also work without a pressure difference between the inner and outer sides.
  • the linear fold 21 is load-bearing in the fold direction 34 and can absorb the weight of the displacement plate (when the machine is not in horizontal operation).
  • the exact seal between the displacer plate and the housing wall or regenerator is absolutely necessary in the interest of high efficiency (efficiency of the machine according to the invention measured: 60% by Carnot).
  • the known machine mentioned above has considerable gap losses between the displacer and the regenerator, so that it does not achieve any efficiency (measured: ⁇ 1% of Carnot).
  • FIGS. 5 to 7 are each enlarged compared to the representations in FIGS. 1, 3 and 4.
  • 5 and 6 each illustrate a design of a suction bellows
  • FIG. 7 illustrates a design of a pressure bellows.
  • two opposing linear rolling membranes 9 extend according to the invention into the housing corners and have a deeper fold 21 than the other two rolling membranes which abut and end on the first-mentioned rolling membranes. This arrangement guarantees the secure sealing of the working gas part volumes against each other also in the housing corners with a simple, wear-free design of the linear roller diaphragms.
  • the reciprocating movement of the displacement plate between the two housing plates can take place according to FIG. 3 by a linearly guided (Watt's parallelogram, crosshead, linear ball bearing) push rod 28, which is rigidly connected at right angles from the center of the one housing plate 2 to the displacement plate 5 and via engages the connecting rod 29 on the motor shaft 15.
  • the displacement plate moves sinusoidally, which leads to an indicator diagram according to FIG. 9 with rounded corners 30.
  • Linear guides of push rods are usually not maintenance-free.
  • a push rod on which the entire heavy displacement plate hangs limits the size of the displacement plate to approximately 2 x 2 m. Due to the harmonic movement, the displacement plate is not subject to strong acceleration forces, the machine is balanced and runs very quietly.
  • the known machine mentioned above uses a bistably pretensioned crank mechanism which contains a push rod which is pretensioned with a spring, one end of which is fastened to the push rod and the other end of which is fastened to the lever arm of a fork, between the fork prongs of which a on a lever arm of the
  • the driver arranged in the diaphragm motor part is displaceable according to the stroke of the diaphragm, two stable positions being predetermined by the spring preload.
  • This arrangement is complicated, fragile and not suitable for jerking a heavy, several square meter displacement plate back and forth.
  • the preferred lifting and lowering mechanism of the displacement plate consists of a maintenance-free, low-friction, almost wear-free low-pressure pneumatic system with toroidal diaphragms as control bellows and lifting bellows:
  • On the cold side of the displacement plate 5 are located in the corners of the displacement plate or in recesses in the housing plate 2, the lifting bellows 13, in which air is pressed and sucked back by a control bellows 14, which is contracted and expanded sinusoidally by the motor shaft via the connecting rod 16.
  • the movement of the lifting bellows and the displacement plate is not sinusoidal, since the pressure increase in the sinusoidally moving control bellows is hyperbolic and, because of its own weight, the displacement plate only begins to move with a corresponding pressure in the lifting system.
  • the displacement plate is jerkily steered to the hot side as far as it will go, remains there while the control bellows compresses the air in the lifting system a little and only suddenly falls back to the cold side when the pressure in the lifting system has dropped again (hyperbolic).
  • the displacement movement is trapezoidal according to Fig. 19.
  • the discontinuous movement of the displacement plate in the indicator diagram results in sharper corners 31, which is known to increase the power density of the machine.
  • This lifting mechanism allows the safe movement of heavy displacement plates of several meters in length (see Fig. 25).
  • the displacement housing is no longer rigidly connected to the working bellows and shaft, but is, for example, via the flexible hoses 36, 38 connected so that the displacement box can be easily tracked in one or two axes of the sun (see Fig. 22).
  • the air volume of the lifting bellows 13 initially has a detrimental effect on the Stirling process, since it leads to air being added to the working gas in the compression phase and subtracted in the expansion phase, that is to say requiring more compression work and allowing less expansion work.
  • This additional bellows volume can, however, be overlaid with the volume of the working bellows offset by 90 ° (see FIG. 12), so that as a further feature of the invention an optimal phase shift of more than 90 ° between the control bellows and working bellows occurs and the additional compensation bellows 32 does not have to be installed .
  • the displacer is an unbroken, airtight plate.
  • the regenerator is arranged as a narrow strip on the front of the housing.
  • a gap is required between the circumference of the displacer plate and the inside of the regenerator, as mentioned above, whereby the regenerator is practically ineffective because most of the air passes through the gap and not through the regenerator flows. Because of the small cross-section of the regenerator, this creates so much flow resistance that the discontinuous, jerky movement of the tuning fork generated with the bistable preload is only unsatisfactorily transmitted to the displacement plate due to the resulting damping.
  • the regenerator 18 which connects the expansion space 11 and the compression space 12, is arranged in the moving displacement plate 5 (FIGS. 1, 3, 4) and extends over its entire surface and also takes up its entire volume.
  • the regenerator has a thickness of at least about 0.1 m to isolate the hot expansion space and the cold compression space from each other, and is preferably made of open-pored polyester foam, which is temperature-resistant, has a high specific heat capacity, poorly conducts heat and is therefore an excellent regenerator for low-temperature machines.
  • the large-area regenerator does not offer any significant flow resistance, even in sudden displacement movements.
  • the housing plates are at the same time the heat exchangers through which the fluid flows.
  • these can only heat and cool the working gas unsatisfactorily, since their surface is relatively small and the working gas does not sweep over them in a forced manner.
  • the heaters 19 and coolers 20 are therefore mounted on the surfaces of the regenerator 18 facing the housing plates 1, 2 and are designed to be gas-flowable with a surface of almost any size as a fin heat exchanger. They are moved with the regenerator and are now in intimate contact with the working gas (measured temperature difference between the heat exchanger fluid and working gas known machine: 20 ° C, inventive machine: 2 ° C). Heater 19, displacer 5, cooler 20 and regenerator 18 form a moving unit in the machine according to the invention.
  • the machine can be fed from a low temperature source (e.g. hot water solar flat collector) or medium temperature source (e.g. parabolic internal collector) (see Fig. 23).
  • a machine If a machine is mechanically driven, for example by a larger or several others, it works as a chiller (see Fig. 24).
  • the heat exchangers now both work as coolers, with which the pumped heat is dissipated and the other generates the lower temperature for the cooling circuit.
  • the machines are preferably horizontal so that the cooler heat exchanger is always below to avoid convection of the working gas in the machine, which turns out to be Mechanism of loss with significant loss of efficiency has highlighted. If the machine has a transparent housing plate 1, the sun shines directly on the heat exchanger 19, which is now designed as a gas-permeable, optically black surface without a fluid tube and is generally simply the surface of the regenerator.
  • the known machine mentioned above uses normal (opaque) insulation material to isolate the outside of the heat exchanger from heat loss to the environment.
  • the machine according to the invention which is preferably operated with sunlight by means of collectors and is generally installed outdoors and is accessible to sunlight, uses a transparent insulation 22 (polycarbonate honeycomb, airgel etc.) on the according to FIG overhead housing plate 1 in contact with the working gas in order to avoid heat losses of the working gas.
  • a transparent insulation 22 polycarbonate honeycomb, airgel etc.
  • the sun shines through the transparent insulation 22 on the housing plate and keeps it hot, so that no heat flow can take place due to the lack of temperature difference between the plate and the working gas. Negative temperature differences can even support the working gas.
  • An embodiment of the Stirling engine according to the invention uses, according to FIG. 15, an upper, well heat-conducting housing plate 1, which forms a plate enlargement 33 and is larger than the displacement plate and therefore protrudes on at least one end face and at the same time is the optically black collector plate for incident sunlight and generally with a glass pane 39 is covered against heat loss.
  • the heat generated in the plate is transported by heat conduction to the plate area under which the motor housing space is located.
  • this heat transport in the plate can be supported by heat pipes which are fitted in or on the plate.
  • the plate enlargement 33 can also consist of several parts which are connected to the housing plate 1 via the heat pipes 24 (see FIG. 16).
  • the heat-conducting housing plate generally has an enlarged surface on the inside of the engine compartment, e.g. by fins 25 or rods that dip into the displacer plate or the regenerator 18 so as to ensure good heat transfer to the working gas.
  • the internal heat exchanger carried with the regenerator is not required.
  • An embodiment of the machine according to the invention can be designed particularly simply with the following restrictions in terms of operating mode: if the machine works as a power machine with a suction bellows 8 (FIG. 17), that is to say with negative pressure with respect to the atmosphere, the machine lies horizontally with the hot side (expansion space) 11 at the top, if the bellows diameter is selected correctly (they must be matched to the weight of the displacement plate and the temperature difference between the hot and cold engine side), the control bellows can be omitted, since only the pressure difference between the engine interior and surroundings are sufficient to lift the displacement plate 5.
  • the bellows 13 are now open to the atmosphere below.
  • the desired phase shift of about 90 degrees between the bellows movement and the displacement movement occurs automatically, but this is sensitive against load changes on the motor shaft.
  • the movement of the displacer plate is also discontinuous.
  • the bellows-free movement of the displacement plate is also possible if either the hot motor side is at the bottom and the lifting bellows are arranged at the top or, if desired, at the top hot engine side, the displacer plate 5 is held by springs 40 on the hot side and by the lifting bellows 13 - in this case, pulling bellows are pulled to the cold side.
  • the lifting bellows must always be arranged on the cold engine side.
  • This machine version without a bellows is used as a chiller operated, in order to avoid convection in the machine, as with the working machine, the colder heat exchanger should be below. In this case, it is the cold heat exchanger. This is possible if the machine is operated below atmospheric pressure (Fig. 17), whereby the phase shift between the displacement movement and the working bellows movement occurs automatically. As a refrigeration machine, however, a higher power density may be required than can be achieved with the suction machine.
  • an embodiment of the refrigeration machine according to the invention uses two valves between the interior of the lifting bellows and the atmosphere.
  • One 41 is spring-loaded and allows the air of the lifting bellows interior to escape into the atmosphere from a certain pressure in the lifting bellows 13.
  • the second 42 is loaded by a diaphragm 43 of the internal bellows pressure and only allows the air to flow into the lifting bellows below a specific internal bellows pressure by the membrane performing the function of a valve flap and temporarily closing the flow path.
  • This valve arrangement with the right choice of valve loads shifts the phase position by 180 ° and the cold-generating side of the machine adjusts itself below, as desired.
  • the cooling effect is considerably increased if lamellae, rods, wires or the like are immersed in the water, which are attached to the regenerator 18 and are immersed with their movement in the water and pulled out and offer the working gas to be cooled a large heat exchange surface. Care must be taken to ensure that the regenerator is not wetted with water because the regenerator effect is lost and the regenerator can no longer be flowed through by gas.
  • an embodiment according to the invention uses a mat 46 made of knitted wire, plastic fleece or the like below the regenerator, which acts as a spray water separator from the working gas, but can also separate aerosol that drips down from the wires.
  • This mat can replace the cooling fins mentioned above and immerse itself in the cooling water above the plate.
  • the mat can also be part of the regenerator itself.
  • An embodiment of the Stirling engine according to the invention does not act on a motor shaft with the bellows via a connecting rod, but instead sets a mass in vibration, for example a pendulum, which does the compression work instead of the flywheel.
  • This arrangement has the advantage that the machine operates at the same frequency over the entire power range and an increase in power manifests itself in a larger oscillation amplitude, so that, for example, the power control when driving reciprocating water pumps can be done simply by changing the stroke.
  • a particularly simple embodiment of the Stirling engine uses the water column 51 of an inertial water lifter 52 as the oscillating mass or a part thereof. When moving upwards, the water column conveys part of the water from the bottom valve 53 in the fountain 54 upwards and simultaneously compresses the working gas in the Stirling engine. The water column is pressed down during the expansion phase of the working bellows 7.

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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)
  • Other Air-Conditioning Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Diaphragms And Bellows (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Exhaust Gas After Treatment (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Basic Packing Technique (AREA)
  • Machine Tool Units (AREA)

Claims (20)

  1. Machine Stirling comprenant un échangeur de chaleur, qui est étudiée pour le fonctionnement à des températures basses à moyennes, c'est-à-dire pour un petit rapport de compression et un grand volume de refoulement,
    dans laquelle il est prévu, entre deux plaques (1, 2) d'une enveloppe qui sont parallèles entre elles, une plaque refoulement (5) mobile en mouvement alternatif qui, le long de la périphérie, est exempte de frottement de glissement contre les côtés frontaux (10) de l'enveloppe,
    dans laquelle la plaque de refoulement (15) sépare l'une de l'autre deux volumes partiels de gaz travaillant : chambre de détente (11) et chambre de compression (12), auxquelles un refroidisseur (20) et un réchauffeur (19) sont associés pour l'échange de chaleur,
    dans laquelle les deux volumes partiels de gaz travaillant (11, 12) sont reliés l'un à l'autre à travers un récupérateur (18) qui est prévu au droit de la plaque de refoulement (5),
    dans laquelle le mouvement alternatif de la plaque de refoulement (5) se trouve en synchronisme avec un piston travaillant (7), avec décalage de phase, et
    dans laquelle, le long de ses bords frontaux, la plaque de refoulement (5) est relié aux côtés frontaux (10) de l'enveloppe par des bandes de liaison linéaires (9),
    caractérisée
    en ce que les deux plaques (1, 2) de l'enveloppe sont maintenues à distance l'une de l'autre par des entretoises (3, 4) disposées dans des positions réparties, les entretoises (3, 4) s'étendant perpendiculairement à la plaque de refoulement (5) et traversant cette plaque par des guidages aussi étanches que possible, et
    en ce que les bandes de liaison linéaires sont des membranes roulantes (9) par lesquelles la plaque de refoulement (5) est guidée par rapport aux côtés frontaux (10) de l'enveloppe le long de ses bords frontaux.
  2. Machine Stirling selon la revendication 1, caractérisée en ce que, pour le mouvement alternatif de la plaque de refoulement (5) sont prévus, entre cette plaque et l'une des plaques (1, 2) de l'enveloppe, des soufflets pneumatiques de déplacement (13) qui peuvent être actionnés au moyen d'un soufflet de commande (14) en étant raccordés à ce soufflet par une liaison conductrice pour l'amenée et l'évacuation de l'air, soufflet de commande qui peut être contracté et dilaté par l'arbre (15) du moteur par l'intermédiaire d'une bielle (16).
  3. Machine Stirling selon la revendication 2, caractérisée en ce que le volume des soufflets pneumatiques de déplacement (13) est compensé par la variation de la position de phase (17) entre le mouvement du soufflet de commande et le mouvement du soufflet de travail, qui passe de 90° à plus de 90°.
  4. Machine Stirling selon la revendication 1, 2 ou 3, caractérisée en ce que les entretoises (3, 4) peuvent absorber des forces de traction aussi bien que de compression et qu'une petite ouverture dans le carter du moteur maintient la pression dans le soufflet de travail (7) en moyenne à la pression atmosphérique.
  5. Machine Stirling selon la revendication 1 ou 2, caractérisée en ce que les entretoises sont constituées par des tirants d'ancrage (3) et un clapet anti-retour (6) règle la pression de l'air dans le soufflet de travail (7) sur une valeur égale ou supérieure à la pression atmosphérique.
  6. Machine Stirling selon la revendication 1 ou 2, caractérisée en ce que les entretoises sont constituées par des étais raidisseurs (4) et un clapet anti-retour (6) règle la pression de l'air dans le soufflet de travail (7) sur une valeur égale ou supérieure à la pression atmosphérique.
  7. Machine Stirling selon une des revendications précédentes, caractérisée en ce que le récupérateur (18) entraîne, sur ses surfaces dirigées vers les plaques (1, 2) de l'enveloppe, les deux échangeurs de chaleur (19, 20) qui sont conformés de façon à pouvoir être parcourus par un gaz.
  8. Machine Stirling selon la revendication 7, caractérisée en ce que l'enveloppe de refoulement est disposée horizontalement et l'échangeur de chaleur le plus froid (20) est disposé en position basse.
  9. Machine Stirling selon une des revendications précédentes, caractérisée en ce que, dans le cas d'une enveloppe carrée ou rectangulaire, deux membranes roulantes (9) mutuellement opposées se prolongent jusque dans les coins de l'enveloppe et ont un pli (21) plus bas que les deux autres plis (9) qui sont apuyés et se terminent par leurs surfaces frontales contre les membranes roulantes citées en premier.
  10. Machine Stirling selon une des revendications 1 à 9, caractérisée en ce que la plaque opaque (1) de l'enveloppe qui appartient à la chambre chaude de l'enveloppe (chambre de détente 11) est munie, sur sa face extérieure, d'une isolation transparente 22, ou est en contact avec la face arrière d'un collecteur solaire (23).
  11. Machine Stirling selon une des revendications 1 à 10, caractérisée en ce qu'une plaque (33) de l'enveloppe est plus grande que la chambre de la plaque de refoulement, déborde au moins au droit d'un côté frontal et, en même temps, constitue la plaque collectrice optiquement noire recevant la lumière solaire incidente.
  12. Machine Stirling selon une des revendications précédentes, caractérisée en ce que le transport de chaleur dans la direction de l'extension de la plaque (33) de l'enveloppe est assisté par des tubes de chaleur (24) qui sont noyés dans cette plaque ou qui y sont fixés.
  13. Machine Stirling selon une des revendications précédentes, caractérisée en ce que la surface de la plaque (33) de l'enveloppe qui se trouve dans la chambre du moteur est agrandie par des lamelles (25) ou analogues qui peuvent plonger dans le récupérateur (18).
  14. Machine Stirling selon une des revendications précédentes, caractérisée en ce que le mouvement alternatif de la plaque de refoulement (5) est commandé par au moins un soufflet élévateur (13) dont le volume intérieur communique avec l'atmosphère.
  15. Machine Stirling selon la revendication 14, caractérisée en ce que la liaison entre les volumes intérieurs des soufflets élévateurs avec l'atmosphère est commandée au moyen de soupapes (41, 42).
  16. Machine Stirling selon une des revendications précédentes, caractérisée en ce qu'au-dessus de la plaque inférieure (2) de l'enveloppe, on fait passer de l'eau de refroidissement (4) à travers la chambre du moteur et que cette eau se trouve au-dessus de la plaque de l'enveloppe, de sorte qu'elle assure la fonction de l'échangeur de chaleur froid.
  17. Machine Stirling selon la revendication 16, caractérisée en ce qu'à la plaque de refoulement (5), sont fixées des lamelles ou analogues (45) qui plongent dans la surface de l'eau.
  18. Machine Stirling selon une des revendications précédentes, caractérisée en ce qu'un séparateur d'eau de projection ou d'aérosol (46) est fixé à la face inférieure du récupérateur.
  19. Machine Stirling selon une des revendications précédentes, caractérisée en ce que le soufflet de travail (7) n'attaque pas un arbre de moteur mais met une masse (50) en oscillation.
  20. Machine Stirling selon une des revendications précédentes, caractérisée en ce que le soufflet de travail (7) n'attaque pas un arbre de moteur mais met en oscillation la colonne d'eau (51) d'un élévateur d'eau à inertie.
EP93106852A 1992-05-21 1993-04-28 Moteur Stirling avec échangeur de chaleur Expired - Lifetime EP0570731B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4216839A DE4216839C1 (de) 1992-05-21 1992-05-21 Stirlingmaschine mit waermetauscher
DE4216839 1992-05-21

Publications (2)

Publication Number Publication Date
EP0570731A1 EP0570731A1 (fr) 1993-11-24
EP0570731B1 true EP0570731B1 (fr) 1996-02-21

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EP93106852A Expired - Lifetime EP0570731B1 (fr) 1992-05-21 1993-04-28 Moteur Stirling avec échangeur de chaleur

Country Status (19)

Country Link
US (1) US5337563A (fr)
EP (1) EP0570731B1 (fr)
JP (1) JPH074309A (fr)
KR (1) KR930023586A (fr)
CN (1) CN1085313A (fr)
AT (1) ATE134420T1 (fr)
AU (1) AU667353B2 (fr)
BR (1) BR9302017A (fr)
CA (1) CA2096762A1 (fr)
DE (1) DE4216839C1 (fr)
DK (1) DK0570731T3 (fr)
EG (1) EG20100A (fr)
ES (1) ES2085070T3 (fr)
GR (1) GR3019108T3 (fr)
IL (1) IL105532A (fr)
MX (1) MX9302940A (fr)
TR (1) TR27770A (fr)
ZA (1) ZA933017B (fr)
ZW (1) ZW5693A1 (fr)

Cited By (2)

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DE102004047054A1 (de) * 2004-09-28 2006-11-30 Hugo Post Modifikation Flachplatten-Stirlingmotor und Prozessanbindung
DE102011106466A1 (de) * 2011-07-04 2013-01-10 GPI Ges. f. Prüfstanduntersuchungen und Ingenieurdienstleistungen mbH Wärmekraftmaschine

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DE9302325U1 (de) * 1993-02-18 1993-04-15 Schager, Dieter, 6050 Offenbach Handwärmemotor
DE4322817A1 (de) * 1993-07-08 1995-01-19 Hans Josef Janetzko Stirling-Motor
DE4429659A1 (de) * 1994-08-20 1996-02-22 Eckhart Weber Flachkollektor-Stirling-Maschine
GB2296047B (en) * 1994-12-15 1998-04-08 Jonathan Maxwell Boardman Diaphragm stirling engine
DE19614359C1 (de) * 1996-04-11 1997-08-28 Karl Obermoser Wärmekraftmaschine mit bewegtem Regenerator
DE19849042A1 (de) * 1998-10-23 2000-05-04 Karl Obermoser Wärmekraftmaschine mit einem zylindrischen Gehäuse
US6688113B1 (en) 2003-02-11 2004-02-10 Superconductor Technologies, Inc. Synthetic felt regenerator material for stirling cycle cryocoolers
US7392934B2 (en) * 2004-06-09 2008-07-01 U.S. Bank National Association Transaction accounting processing system and approach
FR2927155B1 (fr) * 2007-03-05 2010-04-02 R & D Ind Sarl Capteur solaire.
DE102010013620B4 (de) 2010-04-01 2022-03-17 Hans - W. Möllmann Heißgasmotor mit rotierenden Segmentkolben
DE102011122072B3 (de) 2011-12-22 2013-02-28 Eads Deutschland Gmbh Stirlingmotor für ein emissionsfreies Fluggerät
DE102011122071B4 (de) 2011-12-22 2013-10-31 Eads Deutschland Gmbh Stirlingmotor mit Schlagflügel für ein emissionsfreies Fluggerät
ITBO20120120A1 (it) * 2012-03-09 2013-09-10 Alessandro Cima Motore volumetrico con energia termica fornita dall'esterno
ES2481345B1 (es) * 2013-01-28 2015-07-15 Deba Energy, S.L. Motor stirling equipado con cámaras en forma de fuelles
US9869180B2 (en) * 2015-04-03 2018-01-16 Synergy Power, LLC Energy harvesting heat engine and actuator
WO2016187598A1 (fr) 2015-05-20 2016-11-24 Other Lab, Llc Système d'échangeur de chaleur à membrane et procédé
CN105736266B (zh) * 2016-03-10 2018-10-16 常州大学 一种利用太阳能产生旋转驱动的方法和装置
CN105927492A (zh) * 2016-05-17 2016-09-07 李宏江 冷热气流发电方法和装置
US10845133B2 (en) 2017-10-10 2020-11-24 Other Lab, Llc Conformable heat exchanger system and method
US11173575B2 (en) 2019-01-29 2021-11-16 Treau, Inc. Film heat exchanger coupling system and method

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Publication number Priority date Publication date Assignee Title
DE102004047054A1 (de) * 2004-09-28 2006-11-30 Hugo Post Modifikation Flachplatten-Stirlingmotor und Prozessanbindung
DE102011106466A1 (de) * 2011-07-04 2013-01-10 GPI Ges. f. Prüfstanduntersuchungen und Ingenieurdienstleistungen mbH Wärmekraftmaschine
DE102011106466B4 (de) 2011-07-04 2018-08-16 GPI Ges. f. Prüfstanduntersuchungen und Ingenieurdienstleistungen mbH Wärmekraftmaschine

Also Published As

Publication number Publication date
ZW5693A1 (en) 1993-11-03
MX9302940A (es) 1995-01-31
IL105532A0 (en) 1993-08-18
TR27770A (tr) 1995-08-04
ATE134420T1 (de) 1996-03-15
AU667353B2 (en) 1996-03-21
AU3836693A (en) 1993-11-25
DE4216839C1 (de) 1993-11-04
CA2096762A1 (fr) 1993-11-22
IL105532A (en) 1996-08-04
BR9302017A (pt) 1993-11-30
GR3019108T3 (en) 1996-05-31
DK0570731T3 (da) 1996-03-18
CN1085313A (zh) 1994-04-13
KR930023586A (ko) 1993-12-21
US5337563A (en) 1994-08-16
ES2085070T3 (es) 1996-05-16
EG20100A (en) 1997-07-31
EP0570731A1 (fr) 1993-11-24
ZA933017B (en) 1993-11-05
JPH074309A (ja) 1995-01-10

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