EP0244435B1 - Erzeuger von energie unterschiedlicher art mit einbezogenem wärmekreislauf - Google Patents

Erzeuger von energie unterschiedlicher art mit einbezogenem wärmekreislauf Download PDF

Info

Publication number
EP0244435B1
EP0244435B1 EP19860905867 EP86905867A EP0244435B1 EP 0244435 B1 EP0244435 B1 EP 0244435B1 EP 19860905867 EP19860905867 EP 19860905867 EP 86905867 A EP86905867 A EP 86905867A EP 0244435 B1 EP0244435 B1 EP 0244435B1
Authority
EP
European Patent Office
Prior art keywords
pistons
motor
fluid
leak
forming
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.)
Expired - Lifetime
Application number
EP19860905867
Other languages
English (en)
French (fr)
Other versions
EP0244435A1 (de
Inventor
Etienne Baudino
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 AT86905867T priority Critical patent/ATE52570T1/de
Publication of EP0244435A1 publication Critical patent/EP0244435A1/de
Application granted granted Critical
Publication of EP0244435B1 publication Critical patent/EP0244435B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B23/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01B23/08—Adaptations for driving, or combinations with, pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy

Definitions

  • the present invention relates to a device for improving energy generators with multiple functions driven by the combined application of heat sources of different temperatures acting on a sealed and motive condensing capacity.
  • thermodynamic cycle devices generate recoverable mechanical energy on a motor axis, but do not exploit the heat contained in the thermal circuit after the expansion of the volatile motor fluid, which must be evacuated through condensers suitable for this purpose, does not not having multi-compressor and mechanical assemblies.
  • French patent No. 2,462,584 did not make it possible, by its piston, a single engine, to obtain a set of several offset compressors, a set of several engine pistons, a block with reinjection cylinder and a distributor device with rotary elements increasing the yields.
  • the aim of the present invention is to at least partially remedy the drawbacks mentioned above and to provide a multifunctional device of modular type which exploits and combines for all purposes the said thermal and mechanical energies generated from a thermal motor-compressor group and its constituent elements integrally contained in a closed enclosure and connected in leaktight manner to at least one fluidic multi-stage heat transfer loop forming a heat pump with successive stages partially contained in said closed enclosure forming a set of sealed and motive capacity of modular condensation for all purposes, containing at least one motor-compressor group forming at least.
  • A a compression assembly with at least three offset compressors, of which (a) the inlet is connected to at least one multi-stage steam source, one of the elements being at least partially contained in the engine thermal circuit and of which (b ) the exhaust is connected to at least one multi-stage condensing capacity forming, in combination with the evaporation capacity, a heat transfer device with reversible cycle heat pump, (B) an engine assembly with at least three engine pistons d driving said compression assembly.
  • the engine assembly and the compression assembly each comprise three cylinders with sliding pistons, the engine pistons mounted in parallel forming a reference plane, being arranged orthogonally to the compression plane actuated by at least one cam suitably profiled, mounted on an axis forming a crankshaft driven by the engine pistons acting in combination and integral with a flywheel constituting a means of circulation of the working fluid in the sealed enclosure, of acceleration of the escape of this fluid to through a conduit provided for this purpose, connected to the axis of rotation of said flywheel:
  • the engine block assembly has at least three cylinders in which the expansion of the working fluid occurs, is tightly connected by intake and exhaust ducts respectively to a source of steam forming a pressure boiler and to the duct of acceleration of the exhaust connected to the flywheel and penetrating at least partially into a reinjection circuit containing the condensed fluid returned to the said boiler under the action of a set of three cylinders and reinjection pistons driven by at least an eccentric mounted on the axis of said crankshaft:
  • the plane of the said three reinjection cylinders is parallel to the plane of the said three compressor cylinders and orthogonal to the axis of the said crankshaft and to the plane containing the said three engine pistons.
  • a distribution device with rotary elements consists of an intake drawer designed to successively supply the three mopeds according to a very precise chronology, and an exhaust drawer designed to allow the evacuation of the expanded fluid. in the said engine cylinders, also following a well-defined chronology.
  • the said drawers are set in motion by the crankshaft
  • these drawers are driven by a chain connected to the axis of said crankshaft which acts on one of the drawers, which drives another drawer, such an embodiment allowing access to the "setting" of the distribution. .
  • the said intake and exhaust drawers are in intimate contact at the intake and exhaust ports, with capsules of suitable shape, perforated in their center to allow free passage of the working fluid, which exerts on the walls of said capsules opposite the walls in intimate contact with said drawers, a thrust which is added to an elastic means ensuring the permanence of said intimate contact.
  • the engine pistons on which the pressure of the condensing working fluid is exerted in a so-called sealed condensing capacity produce a constant pressure opposing the expansion of the working fluid in the driving cylinders.
  • the device thermal motor compressor forming a sealed condensing drive capacity described according to the invention includes various partially deformable sealed capacities on demand for recovering various vapor leaks and their reinjection on demand through various sealed conduits, by reinjection pistons positioned in a plane orthogonal to the crankshaft axis and driven by a cam integral with said crankshaft axis.
  • each vapor leakage recovery capacity forms a sealed enclosure and of condensation of these vapor leaks and of pressure balancing between the pressure contained in said enclosure which is that of the vapors at least partially condensed and the pressure from the external environment in intimate contact with said enclosure.
  • the pressure of the expanded working fluid in the expansion chambers being very slightly higher than the pressure of the condensed fluid, thrust springs or other equivalent elastic devices are generally necessary to ensure the evacuation of the working fluid.
  • the device according to the present invention by the judicious combination of three cylinders and engine pistons makes it unnecessary to use such devices because it ensures the evacuation of the working fluid by the effect of rotation of the combined flywheel.
  • the distribution of the working fluid in the said expansion chambers requires elements with compression or return springs and other mechanical connection elements slaved to the working piston, which reduces the efficiency in a way not negligible.
  • the device according to the invention overcomes this drawback thanks to the arrangement and the judicious use of the respective position of the engine pistons, the cylinders and the drawers combined with the judicious exploitation of the pressure of the condensed fluid contained in the sealed capacity. .
  • the device according to the present invention also eliminates this drawback thanks to the rational use of a cam acting simultaneously on the three compressor pistons, the profile of this cam being defined and chosen as a function of the fluid to be compressed, of the expansion of the fluid existing in the expansion chambers so that the speed of movement of said compressor pistons being inversely proportional to the pressure exerted by the compressed fluid on these pistons, allows optimization of the start-up and overall efficiency.
  • cams can be associated and arranged in such a way that each can act simultaneously on three pistons in the case of operations or applications justifying several stages of compression.
  • the device according to the invention overcomes this drawback by causing the simultaneous driving of three pistons by a judiciously profiled cam, each piston being in contact with a well-defined portion of the profile of this cam thus constituting a balanced assembly.
  • the device according to the invention also obviates this drawback because it allows the reinjection of the condensed fluid during the phase of the start of compression when the compression rate is minimum and the speed of movement of the compressor piston is at maximum.
  • the device according to the invention is designed so that the three planned reinjection pistons are driven simultaneously by the action of a suitably profiled cam mounted on the axis of the crankshaft which has been discussed above.
  • the device according to the present invention is designed in such a way that the condensed fluid is sucked in and then discharged by the reinjection pistons towards the starting boiler after having possibly previously, at least partially recovered, the heat produced at the compressor cylinders by the compression of the fluid from the heat pump cycle then, necessarily at least partially that evacuated from the exhaust of the expansion chambers of the engine pistons.
  • the quantity "Q" is thus significantly reduced, which further improves the overall yield and reduces the cost of the hot source, in particular in the case where it is constituted by solar panels.
  • the multi-stage compression assembly transferred on demand, the heat of the fluid from the interior of the sealed and motive condensing capacity towards the external medium or vice versa, by inversion of the thermal cycle, from the external medium towards the interior of said capacity or any other combination of cycles.
  • cam-compressor assembly forming the compression assembly is exchangeable, which makes it possible, among other things, to meet all needs, to use any type of product to be compressed, as well as to ensure in combination with a compression assembly. equivalent mounted externally on the axis or any other receiver performing multiple and combined functions.
  • the motive and sealed condensing capacity contains at least one evaporator forming an element of the multi-stage sealed thermal transfer capacity associated in a sealed manner at least partially with a compression assembly according to the invention which at least partially dissipates the heat. expanded working fluid, by successive compressions and successive temperature rises through the multi-stage heat transfer capacity designed and profiled on demand and according to needs;
  • the axes of displacement of the reinjection pistons and of the compression pistons lying in parallel planes are arranged with a judicious offset with respect to each other so that each cycle, the reinjection takes place in the phases of least work of . compression and maximum displacement speed of the pistons.
  • at least one cam is provided per compression assembly.
  • At least one end 11A of the crankshaft 11 passes through at least one wall 1A of the closed enclosure 1 in leaktight manner.
  • the shaft 11 comprises at least two sealing rings of the rotating type 15, 16, forming leaktight side walls with a capacity for recovering leaks 17, they are mounted without play on the shaft 11 and in the wall 1A - or any other device tightly connected to said wall 1A -allowing the free rotation of said shaft 11.
  • Said rings 15, 16 are positioned in planes orthogonal to the axis of the shaft 11, and separated by a suitable distance in order to receive the leaks in question in leaktight manner.
  • the capacity 17 is connected by at least one sealed conduit 18, to a capacity 19 deformable by pressure balancing.
  • the thermal transfer fluid loops contain a volatile refrigerant fluid in circulation under the action of the compression pistons 5A, 5B, 5C, each being at a precise compression phase given by the profile of the cam 12, forming a multi-stage heat transfer heat pump between the evaporator 20 and the condenser contained in the thermal evacuation stage 3C, successively through the fluidic loops C1, C2, C3, each of the pistons 5A, .5B, 5C providing work equivalent to the lowest possible compression ratio in order to optimize the coefficient of performance, respectively connected to the corresponding fluidic loops, preferably consisting of at least one evaporator, a condenser, a holder (possibly an oil separator) and conduits tight connections of these constituent elements to each other partially contained in capacities 21, 3A, 3B, 3C with material to, or thermal storage fluid 22A.
  • a volatile refrigerant fluid in circulation under the action of the compression pistons 5A, 5B, 5C, each being at a precise compression phase given by the profile of the cam
  • the closed enclosure 1 contains the evaporator 20, an element constituting the multi-stage heat transfer capacity 3, which can operate as a condenser by reversing the thermal cycle using a four-way valve (not shown). on the sins), as in the case of known heat pump devices, it being specified that this evaporator 20 is placed in a sealed envelope 21, comprising a material or other product 22, intended to absorb the calories of the fluid which crosses through conduits 21A, and optionally another means of communication E6, forming inertia and storage capacity, as well as a regulator of heat dissipation linked to the evaporation temperature of the fluid circulating in said evaporator 20 , or liquefaction in the condenser 20A, contained in the capacity 3A with material or fluid of identical accumulation 22A.
  • a sealed envelope 21 comprising a material or other product 22, intended to absorb the calories of the fluid which crosses through conduits 21A, and optionally another means of communication E6, forming inertia and storage capacity, as well as a regulator of
  • Capacities 3A, 3B, 3C with material 22A integrating on demand and depending on the applications, the physical phenomena linked to said evaporation or liquefaction condensation temperatures of the fluids circulating in the respective fluid loops.
  • the sealed enclosure 1, 2 is made up of various capacities forming sealed volumes GHJ K, containing at least partially an element constituting the thermal motor-compressor group, said volumes being separated on demand by watertight bulkheads E1, E3, each comprising at least one device for recovering and reinjecting leaks E2, E4 of the type described above (15 , 16, 17, 18, 19) crossed on demand by one of said constituent elements such as the motor axis 11.
  • Said capacities of type E2, E4 being positioned on demand anywhere in the device according to the invention in order to isolate as required, in particular lubrication, any functional element or constituent assembly forming the motor-compressor group.
  • This version of the heat transfer capacity 3 given by way of nonlimiting example may however be adapted for other specific applications, which may justify the use of several different heat transfer fluids, for example a refrigerant loop operating as an evacuator the two others operating in cold production.
  • each compressor piston will include a leakage recovery device directly inspired by the leakage recovery device 15, 16, 17, 18, 19 described above, possibly with a capacity containing a lubricating oil which will be recovered by a oil separator and reinjected by a reinjection piston 6.
  • the compressor pistons are provided with various elastic means allowing permanent contact with the different cams, judiciously combined with the functional exploitation of the pressures of the fluids contained in the thermal circuits and fluidic loops. acting on said compressor pistons in order to provide, in combination with the profiled cams, operation of the device at constant torque.
  • said pistons comprise, according to an advantageous embodiment, a sealed and deformable capsule 24 under the effect of a volatile fluid contained tightly in the said capsule 24, the pressure of which varies as a function of the thermal environment surrounding said piston so that it exerts a thrust on the walls of said capsule acting by deformation on the segments 25 ensuring self-regulation of friction and taking up of wear , the conduits 7A and 8 being provided with capsules 25A whose contact surface is adapted to avoid excessive friction and mounted in the upper parts of the engine cylinders as shown in Figures 1-2-3-4.
  • Such a closed enclosure 1, 2 forming motor capacity and condensation extended by a multi-stage heat transfer capacity constitutes an absolutely sealed and modular assembly which can operate according to the needs of mono-fluid, bi-fluid by the exploitation of any known heat source and provide an advantageous combination of thermal and mechanical effects available for all purposes respectively from capacity 3 and the force shaft 11A.
  • the combination of several devices according to the invention providing, on request, an assembly for optimal exploitation of thermal energy by cascade effect, each device operating by at least partial exploitation of the heat of the fluid contained in the preceding device. .
  • this type of digester with integrated thermodynamic cycle with multiple functions can equip a vehicle and operate by exploiting the heat of the engine of the vehicle which, by its usual cooling circuit, will heat supply the accumulation material 26A; When the vehicle is stopped, a battery of solar energy absorbers, combined and structured in harmony with said vehicle, will combine the solar heat recovered with that contained in the storage capacity 26.
  • a battery of solar energy absorbers When the vehicle is stopped, a battery of solar energy absorbers, combined and structured in harmony with said vehicle, will combine the solar heat recovered with that contained in the storage capacity 26.
  • several devices according to the invention can be combined for multiple purposes; grain escapes in fitted silots, in combination with the digester, and other biomass applications, production of hydrocarbons by the combination of a high calorific intake (250 ° c) and a high compression of said biomass (200 kg / cm2) and others.
  • this cold room can be adapted to a vehicle and be connected to its heat dissipation circuit from the engine, forming a mobile cold production unit intended for all purposes, in particular for demineralization of sea water by freezing.
  • the device according to the invention may give priority either to the thermal evacuation capacity assembly 3, or to the mechanical force that can be used from the shaft 11A.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (10)

1. Mehrzweck-Energieumwandlungsvorrichtung, die die simultane Erzeugung thermischer und mechanischer Energie durch Nutzung von Wärmequellen ungleicher Temperatur kombiniert, bestehend aus einer dicht schliessenden Hülle, die teilweise die Komponenten eines Verdichteraggregats mit integriertem thermischen Kreislauf aufnimmt, gebildet von einer Antriebseinheit mit mindestens einem in einem Zylinder gleitenden Kolben, der eine Verdichtereinheit mit mindestens einem in einem Verdichterzylinder gleitenden Kolben bewegt, verbunden mit einer Fluidschleife mit Kühlkreis, teilweise kondensiert in mehrstufigen Wärmetausch-Kapazitäten mit umkehrbarem Zyklus, gekennzeichnet durch eine dicht schliessende Hülle (1), gebildet aus modulierbaren Behältnissen (G, H, J, K), die in Kombination ein Verdichteraggregat mit thermischem Kreislauf assoziiert mit einer treibenden Fluidschleife (28, 28A, F1, F2), die zum einen eine Wärmequelle in Form eines ausserhalb angebrachten Boilers (26, 27, 39) und zum andern eine aus einem Wärmetauscher (2), der fester Bestandteil der dicht schliessenden Hülle (1) ist, bestehenden Quelle ungleicher Temperatur umfasst: das Verdichteraggregat ist gebildet durch die Kombination einer mindestens drei Zylinder mit zueinander parallel angeordneten Hubkolben (4A, 4B, 4C), deren Achsen eine Bezugsebene bilden, umfassenden Antriebseinheit (4) und einer angetriebenen Verdichtereinheit (5), bestehend aus mindestens drei Zylindern mit Hubkolben (5A, 5B, 5C), die sich in zueinander im Winkel angeordneten Zylindern zu der vorgenannten Bezugsebene in rechtwinkliger Ebene bewegen, und auf dichte Weise verbunden mit den Elementen einer mehrstufigen Wärmetausch-Fluidschleife (C1, C2, C3) mit umkehrbarem Zyklus, mindesten teilweise auf dichte Weise in der geschlossenen Hülle (1) enthalten, durch ein verdampfer-bildenes Element (20) einer der Fluidschleifen (C1), wobei der Wärmeaustausch mit der bzw. den Verbrauchervorrichtungen in einer aus einer oder mehreren abhängigen oder unabhängigen Hüllen (3A, 3B, 3C), mit Wärmespeicher-Material bzw. -Flüssigkeit (22A), gebildeten Einheit (3) stattfindet.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die in ihren Zylindern bewegten Verdichterkolben (5A, 5B, 5C) von einer Profilnocke (12) angetrieben werden, wobei sich jeder der um die besagte Nocke (12) im Winkel ange brachten Kolben in einer von den anderen Kolben verschiedenen Kompressionsphase befindet, während die Nocken kraftschlüssig mit einer als Kurbelwelle ausgebildeten Antriebswelle (11) sind, die durch mechanische Mittel (9) mit den Antriebskolben (4A, 4B, 4C) verbunden ist.
3. Vorrichtung nach Ansprüchen 1 und 2, dadurch gekennzeichnet, dass die Antriebseinheit (4) gleichzeitig einerseits ein drehendes Element (7A), das die einzige Zuleitung zur zeitlich geordneten Speisung der in der Einheit (4) enthaltenen Antriebskolben (4A, 4B, 4C) bildet und über eine dicht schliessende Rohrleitung (28A) mit dem ausserhalb angebrachten Boiler (26, 27) verbunden ist, und andererseits ein drehendes Element (8) umfasst, das die einzige Leitung zur zeitlich geordneten Ableitung aus den Antriebskolben (4A, 4B, 4C) bildet, durch eine Rohrleitung (8A) mit einem mit der Kurbelwelle (11) kraftschlüssigen Schwungrad (14) verbunden, und ausgerüstet mit Flügeln zur Beschleunigung des in den die besagten Antriebskolben einschliessenden Zylindern entspannten Abdampfes.
4. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der in der dicht schliessenden Hülle (1) befindliche Verdampfer (20), als wesentliches Bestandteil der mehrstufigen Wärmetauscher-Fluidschleife (3), in einem wärmespeichernden Material (22) mit einem Mantel (21) enthalten ist, das eine Wärmeleitwiderstands-und -speichereinrichtung bildet, durchdrungen von einer Rohrleitung (23), durch die mit Hilfe des Schwungrads (14) die Flüssigkeit des Antriebskreislauf (F1, F2) getrieben wird.
5. Vorrichtung nach Ansprüchen 1 und 2, dadurch gekennzeichnet, dass die Kurbelwelle (11) mindestens durch eine Wand (1A) der dicht schliessenden Hülle (1) hindurchführt und eine mit der besagten Wand formschlüssige Dichtungseinrichtung enthält, bestehend aus mindestens zwei Ringen (15, 16), die ein dicht schliessendes Behältnis zum Auffangen entweichender Flüssigkeit bilden (17), verbunden zum einen durch eine dicht schliessende Leitung (18) mit einem verformbaren, druckausgleichenden, ausserhalb der besagten dicht schliessenden Hülle (1) angebrachten, Behältnis (19) und zum andern durch eine dicht schliessende Leitung (29) mit .mindestens einem Kolben (6D) einer Auslauf-Rückführeinheit mit Hubkolben (6D, 6E, 6F), angetrieben durch eine kraftschlüssig mit der Kurbelwelle (11) verbundene Nocke (12A), wobei die besagte Rückführeinheit mit Nocke (12A) in der dicht schliessenden Hülle (1) enthalten ist und die besagten Auslauf-Rückführungskolben in paralleler Ebene zur Ebene der Verdichter (5A, 5B, 5C) und rechtwinkelig zur Bezugsebene der Achsen der Antriebskolben (4A, 4B, 4C) angeordnet sind.
6. Vorrichtung nach Ansprüchen 1 und 3, dadurch gekennzeichnet, dass die Abdampfleitung (8A) der Antriebseinheit (4) durch einen Abhitzeverwerter (8C) läuft, gebildet durch ein Behältnis (8B), gefüllt mit Wärmespeicher-Material oder -Fluid, das die Wärme der unter der Wirkung des drehenden Schwungrads (14) durchfliessenden Flüssigkeit aufnimmt, wobei der besagte Abhitzeverwerter (8C) sich durch eine Rohrleitung (8D) verlängert bis zu dem besagten Schwungrad zur Beschleunigung des in den Zylindern mit den Antriebskolben (4A, 4B, 4C) entspannten Antriebsabdampfes, und sie an die kondensierte Flüssigkeit, die den besagten Abhitzeverwerter (8C) über die Leitungen (8E) durchfliesst, wieder abgibt.
7. Vorrichtung nach Ansprüchen 1, 2 und 6, dadurch gekennzeichnet, dass die Kurbelwelle (11) eine Profilnocke (12B) beinhaltet zum Antrieb einer Rückführeinheit (6), bestehend aus Hubkolben (6A, 6B, 6C), die in einer zur Bezugsebene der Antriebskolben (4A, 4B, 4C) rechtwinkeligen Ebene angeordnet sind und die kondensierte Antriebsflüssigkeit dicht schliessend in den ausserhalb angebrachten Boiler (26, 27, 39) fördern, über eine den Abhitzeverwerter (8C) durchlaufende und durch die Röhren (8E) verlängerte Leitung (28), wobei die Hubachsen der besagten Rückführkolben und der Verdichtungskolben (5A, 5B, 5C) sich in parallelen Ebenen befinden und zueinander in einer sinnvollen Staffelung auf solche Weise angebracht sind, dass in jedem Zyklus die Rückführung in den Phasen geringster Verdichtungsarbeit und maximaler Hubgeschwindigkeit der Kolben stattfindet, um der Vorrichtung in Verbindung mit dem besonderen Profil der Antriebsnocken der Verdichterkolben (12) und der Rückführkolben (12B) einen Betrieb mit konstantem Drehmoment zu verleihen.
8. Vorrichtung nach Ansprüchen 2 und 3, dadurch gekennzeichnet, dass mindestens eine der drehbaren Leitungen (7A, 8) durch eine Kette (9A) mit einer mit der Kurbelwelle (11) kraftschlüssigen Laufrolle (9B) verbunden ist, wobei diese besagte Leitung die andere kinematisch (9C) treibt.
9. Vorrichtung nach Ansprüchen 1 und 3, dadurch gekenneichnet, dass die drehbaren Leitungen (7A, 8) in zeitlich geordneter Verbindung mit den Antriebskolben (4A, 4B, 4C) stehen, und dies über Kanäle (4D) mit Hohlkapseln (25A), deren eine Fläche in direktem Kontakt mit den besagten Leitungen steht, während die gegenüberliegende Fläche in Kontakt mit der in den Zylindern der Antriebskolben (4A, 4B, 4C) fliessenden Flüssigkeit ist.
10. Vorrichtung nach Anspruch 1, dadurch gekenneichnet, dass die Antriebs- und Verdichter-Hubkolben (4A, 4B, 4C) bzw. (5A, 5B, 5C) eine dichte und verformbare Kapsel (24) besitzen, in direktem Kontakt mit den Dichtungssegmenten (25) und gefüllt mit einer dehnbaren Flüssigkeit.
EP19860905867 1985-10-16 1986-10-16 Erzeuger von energie unterschiedlicher art mit einbezogenem wärmekreislauf Expired - Lifetime EP0244435B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86905867T ATE52570T1 (de) 1985-10-16 1986-10-16 Erzeuger von energie unterschiedlicher art mit einbezogenem waermekreislauf.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8515545A FR2588645B1 (fr) 1985-10-16 1985-10-16 Dispositif generateur d'energies multiples, a cycle thermique integre, par l'exploitation de deux sources calorifiques de temperatures differentes agissant sur une capacite etanche et motrice de condensation modulable
FR8515545 1985-10-16

Publications (2)

Publication Number Publication Date
EP0244435A1 EP0244435A1 (de) 1987-11-11
EP0244435B1 true EP0244435B1 (de) 1990-05-09

Family

ID=9324008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860905867 Expired - Lifetime EP0244435B1 (de) 1985-10-16 1986-10-16 Erzeuger von energie unterschiedlicher art mit einbezogenem wärmekreislauf

Country Status (4)

Country Link
EP (1) EP0244435B1 (de)
DE (1) DE3671065D1 (de)
FR (1) FR2588645B1 (de)
WO (1) WO1987002413A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009034238A1 (fr) 2007-09-11 2009-03-19 Franck Baudino Cabine de sante
EP2334602B1 (de) * 2008-10-02 2014-12-10 BAUDINO, Etienne Hybridmotorsystem
CN109611987B (zh) * 2018-12-07 2021-02-26 湖南达道新能源开发有限公司 一种抽取浅层地热能源供暖及制冷装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR963814A (de) * 1950-07-21
FR826278A (fr) * 1936-12-08 1938-03-28 Spiros Groupe moto-compresseur transportable pour toutes applications
CH207690A (fr) * 1938-10-10 1939-11-30 Spladis Societe Pour L Applic Procédé de chauffage et de refroidissement et installation pour sa mise en oeuvre.
US2991632A (en) * 1958-12-11 1961-07-11 John G Rogers Refrigeration system
US3196631A (en) * 1962-06-25 1965-07-27 Kenneth D Holland Portable refrigeration chest
US3519065A (en) * 1968-10-04 1970-07-07 Thermo Electron Corp Gas heating and cooling system
FR2234793A5 (de) * 1973-06-19 1975-01-17 Mengin Ets Pierre
US3960322A (en) * 1974-12-17 1976-06-01 Ruff John D Solar heat pump
FR2462584A1 (fr) * 1979-07-27 1981-02-13 Baudino Etienne Dispositif motocompresseur solaire a fonctions multiples
GB2062108B (en) * 1979-10-17 1984-05-10 Chih Kang Shao Power plant for producing power by use of a refrigerant as a working medium
EP0056786A1 (de) * 1981-01-15 1982-07-28 Karl-Heinz Schmall Wärmepumpenanordnung und Verwendung eines Kältemitteldampfmotors

Also Published As

Publication number Publication date
FR2588645B1 (fr) 1987-12-18
DE3671065D1 (de) 1990-06-13
WO1987002413A1 (fr) 1987-04-23
FR2588645A1 (fr) 1987-04-17
EP0244435A1 (de) 1987-11-11

Similar Documents

Publication Publication Date Title
Rahbar et al. Review of organic Rankine cycle for small-scale applications
EP1096209B1 (de) Wärmepumpvorrichtung, insbesondere zur Kühlung
WO2011077248A2 (en) Combined cycle solar power generation
FR2948990A1 (fr) Dispositif thermodynamique multi-energie modulaire
FR3042857B1 (fr) Chaudiere thermodynamique a compresseur thermique
EP2816013B1 (de) Hybridmotorsystem, das eine Kombination aus zwei komplementären Motorkreisläufen umfasst
EP3274639B1 (de) Solare einrichtung zur autonomen adsorptionskälteherstellung
EP2580458A1 (de) Wärmetauschender zylinderkopf
EP0244435B1 (de) Erzeuger von energie unterschiedlicher art mit einbezogenem wärmekreislauf
GB1593100A (en) Thermodynamic installation
JP4161978B2 (ja) 外燃機関
US20090211223A1 (en) High efficient heat engine process using either water or liquefied gases for its working fluid at lower temperatures
US11852382B2 (en) Heating and cooling system powered by renewable energy and assisted by geothermal energy
KR101391994B1 (ko) 작동유체의 회수를 이용한 베인터빈엔진 및 이를 가지는 발전장치
US20150337729A1 (en) Multi-staged thermal powered hydride generator
CA3187771A1 (en) Thermoelectric device for energy storage or energy conversions
BE1013535A3 (fr) Dispositif de refroidissement combinant l'utilisation d'une boucle diphasique et d'un systeme de refrigeration a absorption, notamment applicable pour le reffroidissement de l'air d'admission d'un moteur a combustion interne.
CN1180790A (zh) 负温差热力发动机
FR2523221A1 (fr) Procede et dispositif pour la production d'une energie directement utilisable a partir de deux sources de chaleur chaude et froide, situees dans une zone de temperature relativement basse
FR2914696A1 (fr) Systeme hybride motorise
FR2851796A1 (fr) Pompe hydraulique et installation hydraulique comportant une telle pompe.
WO2011128520A1 (fr) Moteur thermique sans carburant adaptable notamment a l'automobile et au nucleaire
FR2585457A1 (fr) Chaudiere thermodynamique a compression thermique et puissance evaporatrice interne au systeme
FR2586091A1 (fr) Dispositif d'echange de chaleur parcouru par deux fluides a circuits independants
FR3135514A1 (fr) Système de génération de froid et de fourniture d’énergie électrique à partir de l’eau de mer et du soleil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19870618

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE GB IT LI LU NL SE

17Q First examination report despatched

Effective date: 19880509

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 52570

Country of ref document: AT

Date of ref document: 19900515

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3671065

Country of ref document: DE

Date of ref document: 19900613

ITF It: translation for a ep patent filed

Owner name: STUDIO INGG. FISCHETTI & WEBER

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19901031

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19901227

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19901228

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19910408

Year of fee payment: 5

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19911016

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19911017

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19911031

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19920415

Year of fee payment: 6

BERE Be: lapsed

Owner name: BAUDINO ETIENNE

Effective date: 19911031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19920501

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19921016

REG Reference to a national code

Ref country code: CH

Ref legal event code: AEN

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19921016

ITTA It: last paid annual fee
EPTA Lu: last paid annual fee
EUG Se: european patent has lapsed

Ref document number: 86905867.7

Effective date: 19920510

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: CH

Ref legal event code: AEN

Free format text: LA POURSUITE DE LA PROCEDURE REQUISE LE 05.07.1996A ETE ACCORDEE. LE BREVET EST REACTIVE.

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021016

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20030430

Year of fee payment: 17

Ref country code: CH

Payment date: 20030430

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 20030502

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040501

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051016