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EP0149057A1 - Apparatus for the conversion of electric energy into thermal energy - Google Patents

Apparatus for the conversion of electric energy into thermal energy Download PDF

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Publication number
EP0149057A1
EP0149057A1 EP84114054A EP84114054A EP0149057A1 EP 0149057 A1 EP0149057 A1 EP 0149057A1 EP 84114054 A EP84114054 A EP 84114054A EP 84114054 A EP84114054 A EP 84114054A EP 0149057 A1 EP0149057 A1 EP 0149057A1
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EP
European Patent Office
Prior art keywords
pump
heat transfer
immersed
transfer fluid
enclosure
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Granted
Application number
EP84114054A
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German (de)
French (fr)
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EP0149057B1 (en
Inventor
Michel Porcellana
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Individual
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Individual
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Priority to AT84114054T priority Critical patent/ATE35180T1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/0018—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using electric energy supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D7/00—Central heating systems employing heat-transfer fluids not covered by groups F24D1/00 - F24D5/00, e.g. oil, salt or gas

Definitions

  • the present invention relates to an apparatus for converting electrical energy into thermal energy, usable in particular for space heating and for the production of domestic hot water.
  • the systems currently used for space heating or the production of domestic hot water comprise a circuit of a heat-transfer fluid, respectively domestic hot water, heated directly or indirectly by a heat source constituted by a liquid fuel boiler or gaseous or more rarely by an electric resistance or electrode boiler. All these systems have well-known advantages and disadvantages and depend essentially on the energy source used.
  • the aim of this invention consists in providing a new electrothermomechanical device for the conversion of electrical energy into thermal energy, with partial intermediate conversion into mechanical energy, which has a reduced bulk and better energy efficiency compared to known systems.
  • the apparatus according to the invention aimed at achieving the above-mentioned aim, is characterized by the fact that it comprises an insulated enclosure filled with a diathermic heat transfer fluid, in which an electric motor and a hydraulic pump actuated by said motor are immersed. and whose suction and discharge lines are also immersed in the heat transfer fluid, the discharge line of said pump being provided with means for reducing the discharge flow.
  • the solution recommended by the invention therefore involves the intermediate transformation of electrical energy into mechanical energy, since the source of electrical energy is used to actuate a motor, itself driving a hydraulic pump whose delivery flow is voluntarily reduced, so that the electric motor is in overheating condition and thus functions as a heat generator, the latter being directly and completely transmitted to the heat transfer fluid in which it is immersed.
  • each device can include several electric motor-hydraulic pump groups.
  • the electric motor driving the hydraulic pump is equipped with a cos f compensation capacitor.
  • the means for reducing the discharge flow can be produced in different ways, for example as will be described later with reference to the accompanying drawings.
  • the illustrated installation comprises an enclosure 1 thermally insulated and filled with a heat transfer diathermic fluid 2, consisting for example of an oil or of a suitable oil mixture, a motor electric 3 associated with a hydraulic pump 4 (of a common type, with gears, with membranes, etc.), this motor and this pump being immersed directly in the heat transfer fluid 2.
  • a heat transfer diathermic fluid 2 consisting for example of an oil or of a suitable oil mixture
  • a motor electric 3 associated with a hydraulic pump 4 (of a common type, with gears, with membranes, etc.), this motor and this pump being immersed directly in the heat transfer fluid 2.
  • the suction line 5 of the pump 4 is immersed in the heat transfer fluid, while the discharge line 6 thereof communicates on the one hand with a bypass line 7 provided with an adjustment valve 8 and on the other hand with a valve 9 for reducing the discharge flow controlled by a motor 10 controlled by means for measuring the temperature T1 of the heat transfer fluid 2.
  • the outlet orifices of the valves 8, 9 communicate directly with said fluid 2.
  • the valves 8, 9 must first of all be fully open at the time of starting the electric motor 3, so as to ensure for a limited time the operating conditions of said motor 3 and of the pump 4 coupled to it.
  • the bypass valve 8 is closed, so that all of the oil flow 2 is sent by the pump 4 in the reduction valve 9, the opening of which is automatically adjusted by the motor 10, in order to create a constriction in the flow discharged into the oil bath.
  • This constriction previously dimensioned, causes a lamination of the oil and an overload of the pump 4 and consequently of the motor 3, which is then in a condition of overheating, the thermal energy thus created being directly and completely transmitted to the coolant. 2.
  • the laminatiôn oil discharged into the bath by the throttle valve releases heat, which is also transmitted to the heat transfer fluid.
  • the automatic adjustment of the temperature of the heat transfer fluid 2 is ensured by the adjustment of the heating provided by the motor 3, which depends on the opening of the reduction valve 9, which is controlled by a motor 10 slaved to an element of measurement T 1 of said temperature, as a function of a predetermined desired value.
  • obtaining a temperature also predetermined regime and / or safety is controlled by a thermostat T 2 , and causes the engine to stop 3. This stop also automatically controls the opening of the valve 9 in view a subsequent start of said engine.
  • the apparatus as just described can be used to heat the heat transfer fluid 2 for the direct use thereof in an external heating circuit, or for its indirect use which involves the presence of '' a heat exchanger immersed in said fluid and which is connected to an external heating circuit for another heat transfer fluid or for producing domestic hot water.
  • FIG. 1 is illustrated the first possibility mentioned above.
  • the oil operating temperature 2 having been reached, a thermostat T 3 controls a circulation pump 12, the suction line 13 of which is immersed in the oil 2 and the discharge line 14 is connected, outside from enclosure 1, to the flow pipe 15 of an external heating circuit passing through radiators 11.
  • the circulation pump 12 and its drive motor being immersed in the oil bath 2, they also contribute positively to the overall energy balance by providing said bath with heat from their respective operation.
  • thermostat T 4 can be provided, connected with the pump 12, for regulating the external circulation as a function of the predetermined temperature variations of the oil in the radiators 11, and this regulation can be coupled with the oil temperature control in enclosure 1 controlled by thermostats T 2 and T 3 .
  • the outlet pipe 6 of the primary hydraulic pump 4 is directly connected to the suction pipe 22 of a second hydraulic pump 24 associated with a second electric motor 23, and the outlet pipe 25 of this second pump 24 is directly in communication with the heat transfer fluid 2 in the insulated enclosure 1.
  • valves 8, 9 of the first embodiment are replaced by a simple valve 26 on the branch line 7.
  • the secondary motor 23 starts first and it makes the oil suck up by the pump. 24 through valve 26.
  • the main motor 3 can be started and it is then the primary pump 4 which sends the oil to the secondary pump 23.
  • the valve 26 is hydraulically closed, which causes an increase in the suction, as well as a mechanical drive of the secondary motor 24 which is no longer electrically supplied. It can then work as an electric generator and produce current usable outside the enclosure 1 via a socket 27.
  • This second embodiment requires a specific reciprocal dimensioning of the pumps 4, 24 and of the motors 3.23 so that the flow rate of the secondary pump 24 is less than the flow rate of the primary pump 4 in order to thus achieve the throttling of the discharge flow of oil and its cavitation as the valve 8 of the apparatus described above.
  • the primary motor 3 must therefore have characteristics that are oversized compared to those of the secondary motor 23 to avoid the latter an excess of initial masses when it starts to drive it.
  • FIG. 3 the embodiment illustrated in a simplified and schematic manner in FIG. 3 is distinguishes from the previous ones in that it comprises a hydraulic accumulator 37 and a group of hydraulic pistons 38, 39a, 39b disposed between the discharge line 36 of the hydraulic pump 34, the latter being actuated by an electric motor 33 equipped with a cos compensation capacitor 40 and the reduction valves 41a, 41b.
  • the hydraulic accumulator 37 is equipped with a pressure switch 41 regulating the distribution of the heat transfer fluid 2, brought into said accumulator through a valve 42, to a distribution valve 43; this consists of a three-way valve with two directions of distribution without an intermediate rest position, and which is self-controlled in a manner known per se with regard to the direction of distribution as a function of the pressure encountered.
  • the valve 43 for alternating distribution communicates with the group of cylinders 44, 45a, 45b, by means of two three-way valves 46a, 46b, in each of which a piston 38 moves back and forth, 39a and 39b, the latter two being connected to each other by a rod 47 and therefore moving simultaneously, the piston 38 of an upper surface sliding on this rod 47 according to a stroke less than that of the lateral pistons 39a, 39b.
  • the central cylinder 44 has at its ends two outlet pipes which each lead to a reduction valve 41a, 41b via a three-way valve 48a, 48b.
  • the three-way valves 46a, 46b and 48a, 48b which have been designed specially for the invention, have two operating positions without closed intermediate position and include a sleeve 49 sliding inside. of the rectilinear part 50 of the valve, between the orifices A and B, more particularly between the constriction presented by the end A of said straight portion 50 and a stop ring 52 located near the end B thereof.
  • This socket 49 has at its end situated on the side of the end A of the valve a throttle intended to retain a ball 51 disposed inside this socket. and being able to move freely inside the latter, and a grid 53 at its other end in order to prevent the ball 51 from coming out from the side of the orifice B.
  • the heat transfer fluid 2 is therefore sent by the distribution valve 43 into the cylinder 45a through the valve 46a (then in the position of Figure 4A) , which has the effect of pushing the piston 39a, and thereby the associated pistons 38 and 39b, in the direction of arrow Fl, the fluid being consequently discharged into the bath 2 by the valve 48b (then in the position of FIG. 4B), and the reduction valve 41b; the valve 48a is then in the position illustrated in FIG. 4A, and the valve 46b in that of FIG. 4B.
  • the distribution valve 43 changes the direction of the flow of coolant, so that the associated pistons 38, 39a and 39b move according to arrow F2 and that the fluid 2 is discharged into the bath by the valves 48a and 41a, the position of the respective valves then being reversed.
  • an external circuit 53 can be provided, with a circulation pump 54 and a drive motor 55 thereof immersed in the heat transfer fluid 2; this circuit 53 is closed and forced and can have heat exchangers, radiators, etc.
  • an external closed circuit with heat exchanger inside the enclosure 1 can also be provided. Thermostats 56, 57 allow the control and regulation of the installation according to the external demand for heat.
  • the apparatus can be suitably provided with means for measuring the temperature, associated with thermostats, the external circuit (outward and return) and the heat transfer fluid in the insulated enclosure, so as to control, according to indications previously given, the operation of the various elements of the apparatus (electric motors, hydraulic pumps, reduction valves, etc.).
  • the apparatus according to the invention makes it possible with a reduced footprint to obtain a better energy balance, thanks to the recovery of an optimal quantity of the energy produced in the form of heat, either directly from electrical energy, either indirectly by intermediate conversion into mechanical energy; in the latter case, it has been more particularly observed that the lamination of the fluid discharged into the enclosure by the throttling of the valve makes it possible to recover a quantity of heat, obtained by friction and by release of internal energy, which increases the overall yield in unexpectedly high proportions.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Silicon Compounds (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Hybrid Cells (AREA)

Abstract

1. Apparatus used to convert electric power into thermic power, characterized by the fact it includes an isolated dewar (1) filled up with a diathermic heat-conveying fluid (2) in which a first electric engine (3) is immersed as well as a first hydraulic pump (4) which works with the aforesaid engine and the inflow and outflow pipes of which are also immersed in the heat-conveying fluid, the outflow pipe of the aforesaid pump being equipped with means of reducing the outflow, and by the fact that these means of reducing the outflow consist of a second hydraulic pump (24) the inflow pipe (22) of which is connected to the aforesaid outflow pipe (6) of the first pump (4), the second pump (24) being associated with a second electric engine (23), and this second pump and this second engine being immersed in the heat-conveying fluid and characterized by smaller dimensions as compared to the first pump and the first engine respectively.

Description

La présente invention se rapporte à un appareillage pour la conversion d'énergie électrique en énergie thermique, utilisable notamment pour le chauffage de locaux et pour la production d'eau chaude sanitaire.The present invention relates to an apparatus for converting electrical energy into thermal energy, usable in particular for space heating and for the production of domestic hot water.

Les systèmes actuellement utilisés pour le chauffage de locaux ou la production d'eau chaude sanitaire comportent un circuit d'un fluide caloporteur, respectivement d'eau chaude sanitaire, chauffé directement ou indirectement par une source de chaleur constitué par une chaudière à combustible liquide ou gazeux ou plus rarement par une chaudière électrique à résistance ou à électrodes. Tous ces systèmes présentent des avantages et des inconvénients bien connus et dépendant essentiellement de la source d'énergie mise en oeuvre.The systems currently used for space heating or the production of domestic hot water comprise a circuit of a heat-transfer fluid, respectively domestic hot water, heated directly or indirectly by a heat source constituted by a liquid fuel boiler or gaseous or more rarely by an electric resistance or electrode boiler. All these systems have well-known advantages and disadvantages and depend essentially on the energy source used.

Le but de cette invention consiste à fournir un nouvel appareillage électrothermomécanique pour la conversion d'énergie électrique en énergie thermique, avec conversion intermédiaire partielle en énergie mécanique, qui présente par rapport aux systèmes connus un encombrement réduit et un meilleur rendement énergétique.The aim of this invention consists in providing a new electrothermomechanical device for the conversion of electrical energy into thermal energy, with partial intermediate conversion into mechanical energy, which has a reduced bulk and better energy efficiency compared to known systems.

L'appareil selon l'invention, visant à atteindre le but précité, est caractérisé par le fait qu'il comporte une enceinte isolée remplie d'un fluide caloporteur diathermique, dans lequel sont immergés un moteur électrique et une pompe hydraulique actionnée par ledit moteur et dont les conduites d'aspiration et de refoulement sont également immergées dans le fluide caloporteur, la conduite de refoulement de ladite pompe étant munie de moyens de réduction du flux de refoulement.The apparatus according to the invention, aimed at achieving the above-mentioned aim, is characterized by the fact that it comprises an insulated enclosure filled with a diathermic heat transfer fluid, in which an electric motor and a hydraulic pump actuated by said motor are immersed. and whose suction and discharge lines are also immersed in the heat transfer fluid, the discharge line of said pump being provided with means for reducing the discharge flow.

La solution préconisée par l'invention fait donc intervenir la transformation intermédiaire de l'énergie électrique en énergie mécanique, puisque la source d'énergie électrique est utilisée pour actionner un moteur, entraînant lui-même une pompe hydraulique dont le flux de refoulement est volontairement réduit, de manière à ce que le moteur électrique se trouve en condition de surchauffe et fonctionne ainsi comme générateur de chaleur, celle-ci étant directement et complètement transmise au fluide athermique caloporteur dans lequel il est immergé. Bien entendu, chaque appareillage peut comporter plusieurs groupes moteur électrique-pompe hydraulique.The solution recommended by the invention therefore involves the intermediate transformation of electrical energy into mechanical energy, since the source of electrical energy is used to actuate a motor, itself driving a hydraulic pump whose delivery flow is voluntarily reduced, so that the electric motor is in overheating condition and thus functions as a heat generator, the latter being directly and completely transmitted to the heat transfer fluid in which it is immersed. Of course, each device can include several electric motor-hydraulic pump groups.

De préférence, le moteur électrique entraînant la pompe hydraulique est équipé d'un condensateur de compensation du cos f.Preferably, the electric motor driving the hydraulic pump is equipped with a cos f compensation capacitor.

Les moyens de réduction du flux de refoulement peuvent être réalisés de différentes manières, par exemple comme cela sera décrit plus loin en référence aux dessins annexés.The means for reducing the discharge flow can be produced in different ways, for example as will be described later with reference to the accompanying drawings.

Les dessins annexés illustrent schématiquement et à titre d'exemples plusieurs formes d'exécutions de l'appareillage de conversion d'énergie selon l'invention.

  • La figure 1 est un schéma général d'une installation de chauffage de locaux comportant une première forme d'exécution de l'appareillage de conversion d'énergie.
  • La figure 2 est un schéma illustrant une seconde réalisation de l'appareil de conversion d'énergie.
  • La figure 3 est un schéma général simplifié d'une installation de chauffage comportant une troisième forme d'exécution de l'appareillage de conversion d'énergie.
  • Les figures 4A et 4B sont des vues en coupe d'une vanne dans deux positions de fonctionnement.
The accompanying drawings illustrate schematically and by way of examples several forms of execution of the energy conversion apparatus according to the invention.
  • Figure 1 is a general diagram of a space heating installation comprising a first embodiment of the energy conversion apparatus.
  • FIG. 2 is a diagram illustrating a second embodiment of the energy conversion apparatus.
  • Figure 3 is a simplified general diagram of a heating installation comprising a third embodiment of the energy conversion apparatus.
  • Figures 4A and 4B are sectional views of a valve in two operating positions.

En référence tout d'abord à la figure 1, l'installation illustrée comporte une enceinte 1 isolée thermiquement et remplie d'un fluide diathermique caloporteur 2, constitué par exemple d'une huile ou d'un mélange d'huile approprié, un moteur électrique 3 associé à une pompe hydraulique 4 (d'un type courant, à engrenages, à membranes, etc.), ce moteur et cette pompe étant immergés directement dans le fluide caloporteur 2.Referring firstly to FIG. 1, the illustrated installation comprises an enclosure 1 thermally insulated and filled with a heat transfer diathermic fluid 2, consisting for example of an oil or of a suitable oil mixture, a motor electric 3 associated with a hydraulic pump 4 (of a common type, with gears, with membranes, etc.), this motor and this pump being immersed directly in the heat transfer fluid 2.

La conduite d'aspiration 5 de la pompe 4 est immergée dans le fluide caloporteur, alors que la conduite de refoulement 6 de celle-ci communique d'une part avec une conduite de dérivation 7 munie d'une vanne de réglage 8 et d'autre part avec une vanne de réduction 9 du flux de refoulement commandée par un moteur 10 asservi à des moyens de mesure de la température Tl du fluide caloporteur 2. Les orifices de sortie des vannes 8,9 communiquent directement avec ledit fluide 2.The suction line 5 of the pump 4 is immersed in the heat transfer fluid, while the discharge line 6 thereof communicates on the one hand with a bypass line 7 provided with an adjustment valve 8 and on the other hand with a valve 9 for reducing the discharge flow controlled by a motor 10 controlled by means for measuring the temperature T1 of the heat transfer fluid 2. The outlet orifices of the valves 8, 9 communicate directly with said fluid 2.

En ce qui concerne le fonctionnement de cet appareillage, les vannes 8,9 doivent tout d'abord être complètement ouvertes au moment du démarrage du moteur électrique 3, de manière à assurer pour un temps limité les conditions de régime dudit moteur 3 et de la pompe 4 accouplée à celui-ci. Une fois le démarrage du moteur 3 effectué et le régime précité atteint, la vanne de dérivation 8 est fermée, de telle sorte que la totalité du flux d'huile 2 soit envoyée par la pompe 4 dans la vanne de réduction 9, dont l'ouverture est réglée automatiquement par le moteur 10, afin de créer un étranglement au flux refoulé dans le bain d'huile. Cet étranglement, préalablement dimensionné, provoque une lamination de l'huile et une surcharge de la pompe 4 et par conséquent du moteur 3, lequel se trouve alors en condition de surchauffe, l'énergie thermique ainsi créée étant directement et complètement transmise au fluide caloporteur 2. De plus, la laminatiôn de l'huile refoulée dans le bain par l'étranglement de la vanne libère de la chaleur, qui est également transmise au fluide caloporteur.As regards the operation of this apparatus, the valves 8, 9 must first of all be fully open at the time of starting the electric motor 3, so as to ensure for a limited time the operating conditions of said motor 3 and of the pump 4 coupled to it. Once the engine 3 has started and the above speed is reached, the bypass valve 8 is closed, so that all of the oil flow 2 is sent by the pump 4 in the reduction valve 9, the opening of which is automatically adjusted by the motor 10, in order to create a constriction in the flow discharged into the oil bath. This constriction, previously dimensioned, causes a lamination of the oil and an overload of the pump 4 and consequently of the motor 3, which is then in a condition of overheating, the thermal energy thus created being directly and completely transmitted to the coolant. 2. In addition, the laminatiôn oil discharged into the bath by the throttle valve releases heat, which is also transmitted to the heat transfer fluid.

Le réglage automatique de la température du fluide caloporteur 2 est assuré par le réglage de l'échauffement apporté par le moteur 3, qui dépend de l'ouverture de la vanne de réduction 9, laquelle est commandée par un moteur 10 asservi à un élément de mesure T1 de ladite température, en fonction d'une valeur désirée prédéterminée. De plus, l'obtention d'une température également prédéterminée de régime et/ou de sécurité est contrôlée par un thermostat T2, et provoque l'arrêt du moteur 3. Cet arrêt commande également automatiquement l'ouverture de la vanne 9 en vue d'un démarrage subséquent dudit moteur.The automatic adjustment of the temperature of the heat transfer fluid 2 is ensured by the adjustment of the heating provided by the motor 3, which depends on the opening of the reduction valve 9, which is controlled by a motor 10 slaved to an element of measurement T 1 of said temperature, as a function of a predetermined desired value. In addition, obtaining a temperature also predetermined regime and / or safety is controlled by a thermostat T 2 , and causes the engine to stop 3. This stop also automatically controls the opening of the valve 9 in view a subsequent start of said engine.

L'appareillage tel qu'il vient d'être décrit peut être utilisé pour chauffer le fluide caloporteur 2 en vue de l'utilisation directe de celui-ci dans un circuit externe de chauffage, ou bien de son utilisation indirecte qui implique la présence d'un échangeur de chaleur immergé dans ledit fluide et qui est relié à un circuit de chauffage extérieur d'un autre fluide caloporteur ou de production d'eau chaude sanitaire.The apparatus as just described can be used to heat the heat transfer fluid 2 for the direct use thereof in an external heating circuit, or for its indirect use which involves the presence of '' a heat exchanger immersed in said fluid and which is connected to an external heating circuit for another heat transfer fluid or for producing domestic hot water.

Sur la figure 1 est illustrée la première possibilité précitée. La température de régime de l'huile 2 étant atteinte, un thermostat T3 commande une pompe de circulation 12, dont la conduite d'aspiration 13 est immergée dans l'huile 2 et la conduite de refoulement 14 est raccordée, à l'extérieur de l'enceinte 1, à la tubulure d'aller 15 d'un circuit extérieur de chauffage traversant des radiateurs 11. La pompe de circulation 12 et son moteur d'entrainement étant immergés dans le bain d'huile 2, ils contribuent également positivement au bilan énergétique global en fournissant audit bain de la chaleur provenant de leur fonctionnement respectif.In Figure 1 is illustrated the first possibility mentioned above. The oil operating temperature 2 having been reached, a thermostat T 3 controls a circulation pump 12, the suction line 13 of which is immersed in the oil 2 and the discharge line 14 is connected, outside from enclosure 1, to the flow pipe 15 of an external heating circuit passing through radiators 11. The circulation pump 12 and its drive motor being immersed in the oil bath 2, they also contribute positively to the overall energy balance by providing said bath with heat from their respective operation.

Il est nécessaire de disposer d'un système de contrôle de la circulation extérieure de l'huile 2 dans les radiateurs 11 qui, autant pour la continuité du service et la sécurité de l'installation, que pour une meilleure efficacité dans le transport de chaleur, doivent demeurer pleins d'huile et à une pression à peu près uniforme. Un tel système est réalisé ici par un circuit hydraulique dérivé 16, en liaison avec la conduite de refoulement 14 de la pompe 12 équipée d'une soupape de sécurité 17 étalonnée, et qui reconduit l'huile 2 dans le bain lorsque la pression de refoulement 14 atteint une valeur excessive. Ce circuit hydraulique 16 se termine par un raccordement sur la tubulure de retour 18 du circuit externe, à travers une vanne de contrôle 19 de la pression du circuit externe. Cette vanne 19 voit son ouverture de déflection dans l'enceinte 1 réglée pour l'huile en retour par la canalisation 16 au moyen de la pression existante de l'huile elle-même; elle est structurellement conçue avec un entraînement hydraulique par un petit piston 20 en opposition avec un ressort 21 préalablement étalonné, réglant l'ouverture et la fermeture de la tubulure de retour 18 de la pression d'huile dans le circuit 16 et ainsi de la pression à la sortie de la pompe 12. De plus, un thermostat T4 peut être prévu, connecté avec la pompe 12, pour la régulation de la circulation extérieure en fonction des variations de température prédéterminées de l'huile dans les radiateurs 11, et cette régulation peut être couplée avec le contrôle de la température de l'huile dans l'enceinte 1 commandé par les thermostats T2 et T3.It is necessary to have a control system for the external circulation of oil 2 in the radiators 11 which, as much for the continuity of the service and the safety of the installation, as for a better efficiency in the transport of heat must remain full of oil and at approximately uniform pressure. Such a system is produced here by a derivative hydraulic circuit 16, in connection with the discharge line 14 of the pump 12 equipped with a calibrated safety valve 17, which returns the oil 2 to the bath when the discharge pressure 14 reaches an excessive value. This hydraulic circuit 16 ends with a connection to the return pipe 18 of the external circuit, through a valve 19 for controlling the pressure of the external circuit. This valve 19 sees its deflection opening in the enclosure 1 adjusted for the oil returning via the pipe 16 by means of the existing pressure. oil itself; it is structurally designed with a hydraulic drive by a small piston 20 in opposition with a spring 21 previously calibrated, regulating the opening and closing of the return pipe 18 of the oil pressure in the circuit 16 and thus of the pressure at the outlet of the pump 12. In addition, a thermostat T 4 can be provided, connected with the pump 12, for regulating the external circulation as a function of the predetermined temperature variations of the oil in the radiators 11, and this regulation can be coupled with the oil temperature control in enclosure 1 controlled by thermostats T 2 and T 3 .

- En pratigue- dans le cas donné ici à titre d'exemple d'une petite installation destinée au chauffage d'une maison individuelle, on peut utiliser une enceinte contenant environ 50 litres de fluide caloporteur et dans laquelle sont immergés deux moteurs de 2 kW actionnant chacun une pompe oléodynamique à engrenages, par exemple du type "Lamborghini type L gr. 05". Le fluide caloporteur utilisé peut être par exemple une huile diathermique de type "Aerotherm 320" (de Rol Oil, Italie), dont les caractéristiques principales sont les suivantes : chaleur spécifique : 0,51 kcal/kg.°C à 75°C; poids spécifique : 0,81-0,83 kg/dm3 à 75oC; conductibilité thermique : 0,11 kcal/ mh°C; viscosité : 2,9° angles à 50°C; et température d'inflammabilité : 210°C.- In practice - in the case given here as an example of a small installation intended for the heating of an individual house, one can use an enclosure containing approximately 50 liters of heat transfer fluid and in which two 2 kW motors are immersed each actuating an oleodynamic gear pump, for example of the "Lamborghini type L gr. 05" type. The heat transfer fluid used can be, for example, a diathermic oil of the "Aerotherm 320" type (from Rol Oil, Italy), the main characteristics of which are as follows: specific heat: 0.51 kcal / kg. ° C to 75 ° C; specific weight: 0.81-0.83 kg / dm 3 at 75 o C; thermal conductivity: 0.11 kcal / mh ° C; viscosity: 2.9 ° angles at 50 ° C; and flammability temperature: 210 ° C.

Dans la seconde réalisation illustrée sur la figure 2, la conduite de sortie 6 de la pompe hydraulique primaire 4 est directement reliée à la conduite d'aspiration 22 d'une seconde pompe hydraulique 24 associée à un second moteur électrique 23, et la conduite de sortie 25 de cette seconde pompe 24 est directement en communication avec le fluide caloporteur 2 dans l'enceinte isolée 1.In the second embodiment illustrated in FIG. 2, the outlet pipe 6 of the primary hydraulic pump 4 is directly connected to the suction pipe 22 of a second hydraulic pump 24 associated with a second electric motor 23, and the outlet pipe 25 of this second pump 24 is directly in communication with the heat transfer fluid 2 in the insulated enclosure 1.

Dans une telle solution, les vannes 8,9 de la première réalisation sont remplacées par une simple vanne 26 sur la conduite dérivée 7. En phase initiale, le moteur secondaire 23 s'enclenche le premier et il fait aspirer l'huile par la pompe 24 à travers la vanne 26. Après un intervalle de temps fixé, qui peut toujours être contrôlé au moyen de la variation de température de l'huile 2 par un thermostat, le moteur principal 3 peut être enclenché et c'est alors la pompe primaire 4 qui envoie l'huile à la pompe secondaire 23. On ferme hydrauliquement la vanne 26, ce qui provoque une.augmentation de l'aspiration, ainsi qu'un entraînement mécanique du moteur secondaire 24 qui n'est plus électriquement alimenté. Il peut alors travailler en générateur électrique et produire du courant utilisable à l'extérieur de l'enceinte 1 par l'entremise d'une prise 27.In such a solution, the valves 8, 9 of the first embodiment are replaced by a simple valve 26 on the branch line 7. In the initial phase, the secondary motor 23 starts first and it makes the oil suck up by the pump. 24 through valve 26. After a fixed time interval, which can always be controlled by means of the oil temperature variation 2 by a thermostat, the main motor 3 can be started and it is then the primary pump 4 which sends the oil to the secondary pump 23. The valve 26 is hydraulically closed, which causes an increase in the suction, as well as a mechanical drive of the secondary motor 24 which is no longer electrically supplied. It can then work as an electric generator and produce current usable outside the enclosure 1 via a socket 27.

Cette seconde réalisation exige un dimensionnement réciproque particulier des pompes 4, 24 et des moteurs 3,23 pour que le débit de la pompe secondaire 24 soit inférieur au débit de la pompe primaire 4 afin de réaliser ainsi l'étranglement du flux de refoulement d'huile et sa cavitation comme la vanne 8 de l'appareillage décrit précédemment. Le moteur primaire 3 doit donc présenter des caractéristiques surdimensionnées par rapport à celles du moteur secondaire 23 pour éviter à ce dernier un excès de masses initiales quant il se met à l'entraîner.This second embodiment requires a specific reciprocal dimensioning of the pumps 4, 24 and of the motors 3.23 so that the flow rate of the secondary pump 24 is less than the flow rate of the primary pump 4 in order to thus achieve the throttling of the discharge flow of oil and its cavitation as the valve 8 of the apparatus described above. The primary motor 3 must therefore have characteristics that are oversized compared to those of the secondary motor 23 to avoid the latter an excess of initial masses when it starts to drive it.

Enfin, la forme d'exécution illustrée de manière simplifiée et schématique sur la figure 3 se distingue des précédantes en ce qu'elle comporte un accumulateur hydraulique 37 et un groupe de pistons hydrauliques 38, 39a, 39b disposés entre la conduite de refoulement 36 de la pompe hydraulique 34, celle-ci étant actionnée par un moteur électrique 33 équipé d'un condensateur 40 de compensation du cos et les vannes de réduction 41a, 41b.Finally, the embodiment illustrated in a simplified and schematic manner in FIG. 3 is distinguishes from the previous ones in that it comprises a hydraulic accumulator 37 and a group of hydraulic pistons 38, 39a, 39b disposed between the discharge line 36 of the hydraulic pump 34, the latter being actuated by an electric motor 33 equipped with a cos compensation capacitor 40 and the reduction valves 41a, 41b.

L'accumulateur hydraulique 37 est équipé d'un pressostat 41 réglant la distribution du fluide caloporteur 2, amené dans ledit accumulateur par l'entremise d'une vanne 42, vers une vanne de distribution 43; celle-ci consiste en une vanne trois voies à deux directions de distribution sans position intermédiaire de repos, et qui est auto-commandée de manière connue en soi en ce qui concerne la direction de distribution en fonction de la pression rencontrée.The hydraulic accumulator 37 is equipped with a pressure switch 41 regulating the distribution of the heat transfer fluid 2, brought into said accumulator through a valve 42, to a distribution valve 43; this consists of a three-way valve with two directions of distribution without an intermediate rest position, and which is self-controlled in a manner known per se with regard to the direction of distribution as a function of the pressure encountered.

La vanne 43 de distribution alternée communique avec le groupe de cylindres 44, 45a, 45b, par l'entremise de deux vannes trois voies 46a, 46b, dans chacun desquels se déplace en un mouvement de va-et-vient un piston respectivement 38, 39a et 39b, les deux derniers étant reliés l'un à l'autre par une tige 47 et se déplaçant donc simultanément, le piston 38 d'une surface supérieure coulissant sur cette tige 47 selon une course inférieure à celles des pistons latéraux 39a, 39b. Le cylindre central 44 présente à ses extrémités deux conduites de sortie qui aboutissent chacune à une vanne de réduction 41a, 41b par l'entremise d'une vanne trois voies 48a, 48b.The valve 43 for alternating distribution communicates with the group of cylinders 44, 45a, 45b, by means of two three-way valves 46a, 46b, in each of which a piston 38 moves back and forth, 39a and 39b, the latter two being connected to each other by a rod 47 and therefore moving simultaneously, the piston 38 of an upper surface sliding on this rod 47 according to a stroke less than that of the lateral pistons 39a, 39b. The central cylinder 44 has at its ends two outlet pipes which each lead to a reduction valve 41a, 41b via a three-way valve 48a, 48b.

Comme illustré sur les figures 4A et 4B, les vannes trois voies 46a, 46b et 48a, 48b, qui ont été conçues spécialement pour l'invention, présentent deux positions de fonctionnement sans position intermédiaire fermée et comportent une douille 49 coulissant à l'intérieur de la partie rectiligne 50 de la vanne, entre les orifices A et B, plus particulièrement entre l'étranglement que présente l'extrémité A de ladite partie rectiligne 50 et une bague d'arrêt 52 située à proximité de l'extrémité B de celle-ci. Cette douille 49 présente à son extrémité situé du côté de l'extrémité A de la vanne un étranglement destiné à retenir une bille 51 disposée à l'intérieur de cette douille . et pouvant se déplacer librement à l'intérieur de celle-ci, et une grille 53 à son autre extrémité afin d'empêcher la bille 51 d'en ressortirdu côté de l'orifice B. Dans la position illustrée à la figure 4A, le passage du fluide n'est possible que dans le sens A→B, la voie C étant fermée par la présence de la douille 49 poussée par le fluide contre la bague de retenue 52. Dans. la position illustrée sur la figure 4B, le passage du fluide se fait dans la direction B→C, la douille 49 étant poussée contre l'étranglement de la voie A et la bille 51 fermant celui-ci.As illustrated in FIGS. 4A and 4B, the three-way valves 46a, 46b and 48a, 48b, which have been designed specially for the invention, have two operating positions without closed intermediate position and include a sleeve 49 sliding inside. of the rectilinear part 50 of the valve, between the orifices A and B, more particularly between the constriction presented by the end A of said straight portion 50 and a stop ring 52 located near the end B thereof. This socket 49 has at its end situated on the side of the end A of the valve a throttle intended to retain a ball 51 disposed inside this socket. and being able to move freely inside the latter, and a grid 53 at its other end in order to prevent the ball 51 from coming out from the side of the orifice B. In the position illustrated in FIG. 4A, the passage of the fluid is only possible in the direction A → B, the path C being closed by the presence of the sleeve 49 pushed by the fluid against the retaining ring 52. In. the position illustrated in FIG. 4B, the passage of the fluid takes place in the direction B → C, the sleeve 49 being pushed against the throttle of the path A and the ball 51 closing the latter.

Dans la position du dispositif illustrée sur le schéma de la figure 3, le fluide caloporteur 2 est donc envoyé par la vanne de distribution 43 jusque dans le cylindre 45a par l'entremise de la vanne 46a (alors dans la position de la figure 4A), ce qui a pour effet de pousser le piston 39a, et par là les pistons associés 38 et 39b, dans le sens de la flèche Fl, le fluide étant par conséquent refoulé dans le bain 2 par la vanne 48b (alors dans la position de la figure 4B), et la vanne de réduction 41b; la vanne 48a est alors dans la position illustrée à la figure 4A, et la vanne 46b dans celle de la figure 4B.In the position of the device illustrated in the diagram of Figure 3, the heat transfer fluid 2 is therefore sent by the distribution valve 43 into the cylinder 45a through the valve 46a (then in the position of Figure 4A) , which has the effect of pushing the piston 39a, and thereby the associated pistons 38 and 39b, in the direction of arrow Fl, the fluid being consequently discharged into the bath 2 by the valve 48b (then in the position of FIG. 4B), and the reduction valve 41b; the valve 48a is then in the position illustrated in FIG. 4A, and the valve 46b in that of FIG. 4B.

Une fois la course maximale atteinte dans la direction Fl, et sous l'effet de la pression supplémentaire ainsi rencontrée, la vanne de distribution 43 change le sens du flux de fluide càloporteur, de telle sorte que les pistons associés 38, 39a et 39b se déplacent selon la flèche F2 et que le fluide 2 soit refoulé dans le bain par les vannes 48a et 41a, la position des vannes respectives étant alors inversée.Once the maximum stroke has been reached in the direction F1, and under the effect of the additional pressure thus encountered, the distribution valve 43 changes the direction of the flow of coolant, so that the associated pistons 38, 39a and 39b move according to arrow F2 and that the fluid 2 is discharged into the bath by the valves 48a and 41a, the position of the respective valves then being reversed.

Comme précédemment, un circuit extérieur 53 peut être prévu, avec une pompe de circulation 54 et un moteur d'entrainement 55 de celle-ci immergés dans le fluide caloporteur 2; ce circuit 53 est fermé et forcé et peut présenter des échangeurs de chaleur , radiateurs, etc. De même, un circuit extérieur fermé avec échangeur de chaleur à l'intérieur de l'enceinte 1 peut également être prévu. Des thermostats 56, 57 permettent la commande et la régulation de l'installation en fonction de la demande extérieure de chaleur.As before, an external circuit 53 can be provided, with a circulation pump 54 and a drive motor 55 thereof immersed in the heat transfer fluid 2; this circuit 53 is closed and forced and can have heat exchangers, radiators, etc. Likewise, an external closed circuit with heat exchanger inside the enclosure 1 can also be provided. Thermostats 56, 57 allow the control and regulation of the installation according to the external demand for heat.

D'une manière générale, et avec l'une ou l'autre des réalisations possibles de l'appareillage selon l'invention, celui-ci peut être muni de manière appropriée de moyens de mesures de la température, associés à des thermostats, du circuit extérieur (à l'aller et au retour) et du fluide caloporteur dans l'enceinte isolée, de manière à commander selon des indications données préalablement le fonctionnement des différents éléments de l'appareillage (moteurs électriques, pompes hydrauliques, vannes de réduction, etc.).In general, and with one or other of the possible embodiments of the apparatus according to the invention, it can be suitably provided with means for measuring the temperature, associated with thermostats, the external circuit (outward and return) and the heat transfer fluid in the insulated enclosure, so as to control, according to indications previously given, the operation of the various elements of the apparatus (electric motors, hydraulic pumps, reduction valves, etc.).

Par rapport aux dispositifs actuellement utilisés, l'appareillage selon l'invention permet avec un encombrement réduit d'obtenir un meilleur bilan énergétique, grâce à la récupération d'une quantité optimale de l'énergie produite sous forme de chaleur, soit directement à partir de l'énergie électrique, soit indirectement par conversion intermédiaire en énergie mécanique; dans ce dernier cas, il a été plus particulièrement constaté que la lamination du fluide refoulé dans l'enceinte par l'étranglement de la vanne permettait de récupérer une quantité de chaleur, obtenue par frottement et par libération d'énergie interne, qui augmente le rendement global dans des proportions inattendument élevées.Compared to the devices currently in use, the apparatus according to the invention makes it possible with a reduced footprint to obtain a better energy balance, thanks to the recovery of an optimal quantity of the energy produced in the form of heat, either directly from electrical energy, either indirectly by intermediate conversion into mechanical energy; in the latter case, it has been more particularly observed that the lamination of the fluid discharged into the enclosure by the throttling of the valve makes it possible to recover a quantity of heat, obtained by friction and by release of internal energy, which increases the overall yield in unexpectedly high proportions.

Claims (10)

1. Appareillage pour la conversion d'énergie électrique en énergie thermique, caractérisé par le fait qu'il comporte une enceinte isolée (1,31) remplie d'un fluide caloporteur diathermique (2,32) dans lequel sont immergés un moteur électrique (3,23,33) et une pompe hydraulique (4,24,34) actionnée par ledit moteur et dont les conduites d'aspiration et de refoulement sont également immergées dans le fluide caloporteur, la conduite de refoulement de ladite pompe étant munie de moyens de réduction du flux de refoulement.1. Apparatus for converting electrical energy into thermal energy, characterized in that it comprises an insulated enclosure (1.31) filled with a diathermic heat transfer fluid (2.32) in which an electric motor is immersed ( 3,23,33) and a hydraulic pump (4,24,34) actuated by said motor and whose suction and discharge lines are also immersed in the heat transfer fluid, the discharge line of said pump being provided with means reduction of the discharge flow. 2. Appareillage selon la revendication 1, caractérisé par le fait que les moyens de réduction du flux de refoulement sont constitués par une vanne réglable (9).2. Apparatus according to claim 1, characterized in that the means for reducing the discharge flow consist of an adjustable valve (9). 3. Appareillage selon la revendication 2, caractérisé par le fait que la vanne réglable (9) est actionnée par un servomoteur de commande (10) asservi à un organe de mesure de la température T1 du fluide caloporteur.3. Apparatus according to claim 2, characterized in that the adjustable valve (9) is actuated by a control servomotor (10) controlled by a member for measuring the temperature T 1 of the heat transfer fluid. 4. Appareillage selon la revendication 1, caractérisé par le fait que les moyens de réduction du flux de refoulement sont constitués par une seconde pompe hydraulique (23) dont la conduite d'aspiration ,(22) est reliée à ladite conduite de refoulement (6) de-la première pompe (4), la seconde pompe (24) étant associée à un second moteur électrique (23), et cette seconde pompe et ce second moteur ayant des caractéristiques sous-dimensionnées par rapport à celles de la première pompe respectivement du premier moteur.4. Apparatus according to claim 1, characterized in that the means for reducing the discharge flow consist of a second hydraulic pump (23), the suction line (22) is connected to said discharge line (6 ) of the first pump (4), the second pump (24) being associated with a second electric motor (23), and this second pump and this second motor having characteristics dimensions undersized compared to those of the first pump respectively of the first motor. 5. Appareillage selon la revendication 4, caractérisé par le fait que le second moteur électrique (23) est entraîné par le flux de refoulement de la seconde pompe (24), de telle sorte qu'il fonctionne pour reconvertir une partie de l'énergie mécanique en énergie électrique réutilisable.5. Apparatus according to claim 4, characterized in that the second electric motor (23) is driven by the discharge flow of the second pump (24), so that it operates to reconvert part of the energy mechanical into reusable electrical energy. 6. Appareil selon l'une des revendications 1 à 3, caractérisé par le fait qu'il comporte, disposés entre la conduite de refoulement (36) de la pompe hydraulique (34) et les moyens de réduction (41a, 41b) du flux de refoulement, un dispositif accumulateur hydraulique (37) et un piston hydraulique (38) à double action.6. Apparatus according to one of claims 1 to 3, characterized in that it comprises, disposed between the discharge line (36) of the hydraulic pump (34) and the means for reducing (41a, 41b) the flow discharge, a hydraulic accumulator device (37) and a double action hydraulic piston (38). 7. Appareil selon la revendication 6, caractérisé par le fait que le dispositif accumulateur hydraulique (37) est équipé d'un pressostat de réglage (41) et qu'il est relié à une vanne trois voies (43) à deux directions de distribution, chaque direction aboutissant par l'entremise d'une vanne (46a, 46b) au cylindre (44) dans lequel le piston (38) se déplace en un mouvement de va-et-vient, ce cylindre présentant chacune de ses extrémités une conduite de sortie reliée à des moyens de réduction du flux de refoulement (41a, 41b) par l'entremise d'une vanne (48a, 48b).7. Apparatus according to claim 6, characterized in that the hydraulic accumulator device (37) is equipped with an adjustment pressure switch (41) and that it is connected to a three-way valve (43) with two directions of distribution , each direction terminating via a valve (46a, 46b) in the cylinder (44) in which the piston (38) moves back and forth, this cylinder having each of its ends a pipe outlet connected to means for reducing the discharge flow (41a, 41b) via a valve (48a, 48b). 8. Appareil selon l'une des revendications 1 à 7, caractérisé par le fait que-le moteur électrique (3,23,33) actionnant la pompe hydraulique (4,24,34) est équipé d'un condensateur de compensation.8. Apparatus according to one of claims 1 to 7, characterized in that-the electric motor (3,23,33) actuating the hydraulic pump (4,24,34) is equipped with a compensation capacitor. 9. Appareillage selon l'une des revendications 1 à 8 pour le chauffage de locaux, caractérisé par le fait qu'il comporte une pompe de circulation dont la conduite d'aspiration est immergée dans le fluide caloporteur de l'enceinte et la conduite de refoulement raccordée à la tubulure d'aller d'un circuit extérieur, celui-ci se terminant par une tubulure de retour dont l'extrémité est immergée dans le fluide caloporteur de l'enceinte, et par le fait que la pompe de circulation et son moteur électrique d'entraînement sont également immergés dans le fluide caloporteur de l'enceinte.9. Apparatus according to one of claims 1 to 8 for space heating, characterized in that it comprises a circulation pump whose suction line is immersed in the heat transfer fluid of the enclosure and the line of delivery connected to the flow pipe of an external circuit, the latter ending in a return pipe whose end is immersed in the heat transfer fluid of the enclosure, and by the fact that the circulation pump and its electric drive motor are also immersed in the heat transfer fluid of the enclosure. 10. Appareil selon l'une des revendications 1 à 8 pour le chauffage de locaux ou la production d'eau chaude sanitaire, caractérisé par le fait qu'elle comporte, immergé dans le fluide caloporteur de l'enceinte un échangeur de chaleur relié à un circuit externe de chauffage, respectivement de distribution d'eau, et par le fait que la pompe de circulation associée à ce circuit, ainsi que son moteur électrique d'entrainement sont immergés dans le fluide caloporteur de l'enceinte.10. Apparatus according to one of claims 1 to 8 for space heating or domestic hot water production, characterized in that it comprises, immersed in the heat transfer fluid of the enclosure a heat exchanger connected to an external heating circuit, respectively for water distribution, and by the fact that the circulation pump associated with this circuit, as well as its electric drive motor are immersed in the heat transfer fluid of the enclosure.
EP84114054A 1983-12-02 1984-11-21 Apparatus for the conversion of electric energy into thermal energy Expired EP0149057B1 (en)

Priority Applications (1)

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AT84114054T ATE35180T1 (en) 1983-12-02 1984-11-21 DEVICE FOR CONVERTING ELECTRICAL ENERGY INTO THERMAL ENERGY.

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CH647683 1983-12-02
CH6476/83 1983-12-02

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EP0149057A1 true EP0149057A1 (en) 1985-07-24
EP0149057B1 EP0149057B1 (en) 1988-06-15

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995014896A1 (en) * 1993-11-22 1995-06-01 Sebacur Ag Process and device for converting electric power into useful heat
CN105370639A (en) * 2015-12-23 2016-03-02 北京航天益森风洞工程技术有限公司 Large-load minitype hydraulic servo system utilized in high temperature environment

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DE3472157D1 (en) 1988-07-21
DE149057T1 (en) 1985-10-24
ATE35180T1 (en) 1988-07-15
EP0149057B1 (en) 1988-06-15

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