EP0435842A1 - Heating process using heat pumps - Google Patents
Heating process using heat pumps Download PDFInfo
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- EP0435842A1 EP0435842A1 EP19900870240 EP90870240A EP0435842A1 EP 0435842 A1 EP0435842 A1 EP 0435842A1 EP 19900870240 EP19900870240 EP 19900870240 EP 90870240 A EP90870240 A EP 90870240A EP 0435842 A1 EP0435842 A1 EP 0435842A1
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- heat pump
- heat
- heat pumps
- enthalpy
- pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B23/00—Heating arrangements
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- the invention relates to a method of heating by heat pumps, used particularly in drying installations with recovery of the enthalpy of the air extracted from the dryer, or any application where recovery of enthalpy is possible, for example on fumes.
- a significant part of the enthalpy recoverable in the extracted air is in this case available at a relatively high temperature; for example, if the humid temperature of the extracted air is 53 °, 60% of the enthalpy which is recoverable up to a temperature of 22 °, is in fact available between 53 ° and 40 °, a level which constitutes a a particularly appreciable heat source in the case of the heat pump heating process.
- thermodynamic fluid is either a pure body or an azeotropic mixture, for which the isobars are also isotherms.
- thermodynamic cycle it is therefore important to seek, by all available technical means, any solution capable of reducing the difference between the extreme temperatures, and therefore the extreme pressures which are imposed on the thermodynamic cycle, in order to improve the coefficient of performance which is directly linked to the gap between these extreme pressures.
- the present invention makes it possible to achieve this result and a high performance coefficient, by the use of several thermodynamically independent heat pumps instead of a single heat pump, in order to greatly reduce for each of these heat pumps. , the differences between the extreme temperatures.
- thermodynamic cycle of this first heat pump By sharing the circuits of external fluids constituting the hot and cold sources of thermodynamic cycles, in as many zones as there are heat pumps, and by connecting the evaporator of the coldest zone of the enthalpy recovery circuit , with the condenser of the same heat pump also installed in the coldest zone of the enthalpy supply circuit, the difference between the extreme temperatures of the thermodynamic cycle of this first heat pump is greatly reduced.
- the average temperatures between the extreme temperatures of each cycle will range from the first to the last heat pump.
- the method of heating by heat pumps comprises the use of two thermodynamically independent heat pumps, for which the circuits of the external fluids common to the two heat pumps, are divided into two zones so as to relate in the first heat pump, the evaporator installed in the coldest zone of the cold source, with the condenser of the same heat pump installed in the coldest zone of the hot source, and in the second heat pump , the evaporator installed in the hottest area of the cold source, with the condenser installed in the hottest area of the hot source.
- thermodynamic fluids In order to optimize the overall coefficient of performance obtained by the heating process by at least two thermodynamically independent pumps, non-azeotropic mixtures are used as thermodynamic fluids, the compositions of which vary from one heat pump to another, depending on the temperature zones of the thermodynamic cycles.
- thermodynamic fluid imposes a counter-current circulation of the thermodynamic fluid and of the external fluid, respecting throughout the exchange. , a small difference between the temperature of the thermodynamic fluid and the temperature of the external fluid.
- They are particularly suitable for performing an efficient exchange against the current, by installing the necessary exchange surface in a sufficient number of panels, and by adapting a structure of the fabrics such that the difference between the temperature of the gases and of the thermodynamic fluid in change of state, can be reduced to a few degrees, for example 2 °, even 1.5 °.
- thermodynamically independent heat pumps makes it possible to greatly reduce the 'difference between the condensation and evaporation pressures for each thermodynamic cycle, and to improve the coefficient of performance in the same proportions, also in the case where the external fluids are gases.
- the heat pump assemblies are used for drying installations with recovery of the enthalpy of the extracted air.
- the exergy By involving the temperature level where the enthalpy is recovered in the cold source, or brought to the hot source, the exergy makes it possible to measure the quality of these enthalpies.
- the combination of these three means allows the heat pumps to better fulfill their function which is to raise the exergy of enthalpies recovered at temperatures lower than those of their use. But simultaneously, the compression work brings an inevitable complement of costly enthalpy that the process makes it possible to greatly reduce through low compression rates, avoiding any waste of exergy.
- Such an installation can, for example, be usefully envisaged behind sufficiently large natural gas boilers fitted with building heaters, since it provides the very significant advantage with respect to condensing boilers, greatly improving the rate of recovery of enthalpy whatever the temperature of the returns, and bringing to the generally required level of 70 ° or more if necessary the totality of the recovered enthalpy.
- the power of the installation would be easily adjustable in parallel with the power required from the boiler; it is likely that even partial recovery of the higher calorific value will very quickly amortize the cost of the installation, which will however be sensitive to the condensate return temperature.
- FIG. 1 The diagrams of FIG. 1 give for a humid temperature of 53 ° of the air extracted from a dryer which represents an excellent cold source, a very representative image of the part taken by each of these means in the valorization of the exergy of the enthalpy recovered.
- thermodynamic fluid corresponds to the use of a pure body or an azeotropic mixture as thermodynamic fluid.
- Diagram 1-c of FIG. 1 relates to the use of non-azeotropic mixtures as thermodynamic fluid, and to the use of efficient exchangers, such as metal mesh exchangers in the case where the external fluids are gases , exchangers mentioned above which allow, by operating against the current, to fully exploit the fact that the isobars of evaporation (and condensation) are no longer isotherms, and that these isobars can cover temperature ranges above 15 °.
- thermodynamically optimum solution that can be achieved, and which is likely to provide an excellent coefficient of performance.
- thermodynamically independent heat pumps obviously implies the use of at least two compressors and two pressure reducers, providing together the same thermal power, while consuming a greatly reduced total mechanical power vis-à-vis that would require the use of a single heat pump.
- FIG. 2 represents the evolution as a function of the transferred enthalpies, of the temperatures of the non-azeotropic mixtures shown in solid lines, while those of the extracted air and those of the drying air are shown in broken lines, the arrows representing the enthalpy transfers.
- the extracted air then enters directly into the evaporator 4 of the heat pump A which it leaves in 5 at 25 °. Its enthalpy is reduced from 179 to 76 kJ / kg of dry air, or a withdrawal of 103 kJ / kg of dry air.
- the non-azeotropic mixture expanded in the heat pump A evaporates against the current between 23 ° and 39.5 ° in the evaporator 4, before being sucked by the compressor 6.
- the condensation of the non-azeotropic mixing takes place between 66 ° and 46 °; it is followed by sub-cooling 8 to 33 ° by exchange against the current with the fresh air entering at 20 ° into the condenser 7 to exit at 64 °.
- the non-azeotropic mixture heated against the current in the evaporator 4 becomes entirely gaseous from 23 ° to 39.5 °.
- the non-azeotropic mixture is sucked gas by the compressor 10 at 51 °; in the condenser 11, it becomes entirely liquid between 76 ° and 58 °, while the air is heated from 56 ° to 74 °.
- the regulator 12 supplies the evaporator 2 at a temperature of 36 °, while the air leaves this evaporator at 41.5 °.
- the enthalpy recovery rate of the extracted air is close to 90% in the case of this dryer.
- thermodynamically independent heat pumps use of at least two thermodynamically independent heat pumps, non-azeotropic mixtures as thermodynamic fluids, and d exchangers of the metal cloth type operating against the current.
Abstract
Description
L'invention concerne un procédé de chauffage par pompes à chaleur, utilisé particulièrement dans les installations de séchage avec récupération de l'enthalpie de l'air extrait du séchoir, ou toute application où la récupération d'enthalpie est possible, par exemple sur des fumées.The invention relates to a method of heating by heat pumps, used particularly in drying installations with recovery of the enthalpy of the air extracted from the dryer, or any application where recovery of enthalpy is possible, for example on fumes.
Il existe notamment de nombreux séchoirs où la température de l'air extrait dépasse 50°, avec la présence d'une quantité importante de vapeur d'eau qui peut atteindre 100 g/kg d'air extrait.There are in particular many dryers where the temperature of the extracted air exceeds 50 °, with the presence of a significant amount of water vapor which can reach 100 g / kg of extracted air.
Or, une partie importante de l'enthalpie récupérable dans l'air extrait est dans ce cas disponible à une température relativement élevée; par exemple, si la température humide de l'air extrait est de 53°, 60% de l'enthalpie qui est récupérable jusqu'à une température de 22°, est en fait disponible entre 53° et 40°, niveau qui constitue une source de chaleur particulièrement appréciable dans le cas du procédé de chauffage par pompes à chaleur.However, a significant part of the enthalpy recoverable in the extracted air is in this case available at a relatively high temperature; for example, if the humid temperature of the extracted air is 53 °, 60% of the enthalpy which is recoverable up to a temperature of 22 °, is in fact available between 53 ° and 40 °, a level which constitutes a a particularly appreciable heat source in the case of the heat pump heating process.
Actuellement dans la plupart des cas, on utilise une pompe à chaleur dont le fluide thermodynamique est soit un corps pur, soit un mélange azéotropique, pour lesquels les isobares sont aussi des isothermes.Currently in most cases, a heat pump is used whose thermodynamic fluid is either a pure body or an azeotropic mixture, for which the isobars are also isotherms.
Il importe donc de chercher par tous les moyens techniques disponibles, toute solution susceptible de réduire l'écart entre les températures extrêmes, et donc les pressions extrêmes qui sont imposées au cycle thermodynamique, afin d'améliorer le coefficient de performance qui est directement lié à l'écart entre ces pressions extrêmes.It is therefore important to seek, by all available technical means, any solution capable of reducing the difference between the extreme temperatures, and therefore the extreme pressures which are imposed on the thermodynamic cycle, in order to improve the coefficient of performance which is directly linked to the gap between these extreme pressures.
La présente invention permet d'arriver à ce résultat et à un coefficient de performance élevé, par l'utilisation de plusieurs pompes à chaleur thermodynamiquement indépendantes au lieu d'une seule pompe à chaleur, afin de réduire fortement pour chacune de ces pompes à chaleur, les écarts entre les températures extrêmes.The present invention makes it possible to achieve this result and a high performance coefficient, by the use of several thermodynamically independent heat pumps instead of a single heat pump, in order to greatly reduce for each of these heat pumps. , the differences between the extreme temperatures.
En partageant les circuits des fluides externes constituant les sources chaudes et froides des cycles thermodynamiques, en autant de zones qu'il y a de pompes à chaleur, et en reliant l'évaporateur de la zone la plus froide du circuit de récupération d'enthalpie, au condenseur de la même pompe à chaleur également installé dans la zone la plus froide du circuit d'apport d'enthalpie, on réduit fortement l'écart entre les températures extrêmes du cycle thermodynamique de cette première pompe à chaleur.By sharing the circuits of external fluids constituting the hot and cold sources of thermodynamic cycles, in as many zones as there are heat pumps, and by connecting the evaporator of the coldest zone of the enthalpy recovery circuit , with the condenser of the same heat pump also installed in the coldest zone of the enthalpy supply circuit, the difference between the extreme temperatures of the thermodynamic cycle of this first heat pump is greatly reduced.
La même disposition est prise successivement pour toutes les pompes à chaleur en terminant par la dernière dont l'évaporateur est situé dans la zone la plus chaude du circuit de récupération d'enthalpie, et le condenseur dans la zone la plus chaude du circuit d'apport d'enthalpie.The same arrangement is made successively for all heat pumps, ending with the last one whose evaporator is located in the hottest zone of the enthalpy recovery circuit, and the condenser in the hottest zone of the heat circuit. intake of enthalpy.
Il s'ensuit pour chaque pompe à chaleur, une réduction importante de l'écart entre les températures et les pressions extrêmes de leur cycle thermodynamique, le partage des circuits externes en autant de zones qu'il y a de pompes à chaleur, étant réalisé de manière à équilibrer les écarts pour tous les cycles thermodynamiques en les ajustant toutefois en fonction du programme de chauffage à réaliser.It follows for each heat pump, a significant reduction in the difference between the temperatures and the extreme pressures of their thermodynamic cycle, the division of the external circuits into as many zones as there are heat pumps, being carried out so as to balance the differences for all the thermodynamic cycles, however adjusting them according to the heating program to be carried out.
Les températures moyennes entre les températures extrêmes de chaque cycle, s'échelonneront en croissant de la première à la dernière pompe à chaleur.The average temperatures between the extreme temperatures of each cycle will range from the first to the last heat pump.
Suivant une réalisation préférentielle, le procédé de chauffage par pompes à chaleur comprend l'emploi de deux pompes à chaleur thermodynamiquement indépendantes, pour lesquelles les circuits des fluides externes communs aux deux pompes à chaleur, sont partagés en deux zones de manière à mettre en relation dans la première pompe à chaleur, 1' évaporateur installé dans la zone la plus froide de la source froide, avec le condenseur de la même pompe à chaleur installé dans la zone la plus froide de la source chaude, et dans la deuxième pompe à chaleur, l'évaporateur installé dans la zone la plus chaude de la source froide, avec le condenseur installé dans la zone la plus chaude de la source chaude.According to a preferred embodiment, the method of heating by heat pumps comprises the use of two thermodynamically independent heat pumps, for which the circuits of the external fluids common to the two heat pumps, are divided into two zones so as to relate in the first heat pump, the evaporator installed in the coldest zone of the cold source, with the condenser of the same heat pump installed in the coldest zone of the hot source, and in the second heat pump , the evaporator installed in the hottest area of the cold source, with the condenser installed in the hottest area of the hot source.
De manière à optimiser le coefficient de performance global obtenu par le procédé de chauffage par au moins deux pompes thermodynamiquement indépendantes, on utilise comme fluides thermodynamiques des mélanges non azéotropiques, dont les compositions varient d'une pompe à chaleur à l'autre, selon les zones de température des cycles thermodynamiques.In order to optimize the overall coefficient of performance obtained by the heating process by at least two thermodynamically independent pumps, non-azeotropic mixtures are used as thermodynamic fluids, the compositions of which vary from one heat pump to another, depending on the temperature zones of the thermodynamic cycles.
Mais comme on pourra le constater dans l'analyse ultérieure des diagrammes de la figure 1, l'emploi avantageux de mélanges non azéotropiques impose une circulation à contre-courant du fluide thermodynamique et du fluide externe, en respectant tout au long de l'échange, un faible écart entre la température du fluide thermodynamique et la température du fluide externe.However, as will be seen in the subsequent analysis of the diagrams in FIG. 1, the advantageous use of non-azeotropic mixtures imposes a counter-current circulation of the thermodynamic fluid and of the external fluid, respecting throughout the exchange. , a small difference between the temperature of the thermodynamic fluid and the temperature of the external fluid.
La solution de ce problème particulièrement délicat lorsque le ou les fluides externes sont des gaz, par exemple de l'air dans le cas des séchoirs, est apportée par les échangeurs à toiles métalliques, objet de la demande de brevet européen n° 89870108.1 déposée par Econergie, échangeurs qui sont parfaitement capables de réaliser ces échanges dans les conditions imposées.The solution of this particularly delicate problem when the external fluid or fluids are gases, for example air in the case of driers, is provided by the metal cloth exchangers, object of European patent application n ° 89870108.1 filed by Energy efficient, exchangers which are perfectly capable of carrying out these exchanges under the conditions imposed.
Ces échangeurs disposent d'une caractéristique importante, à savoir de conserver un bon coefficient d'échange même à faible vitesse de passage des gaz, tout en fonctionnant avec de faibles pertes de charge.These exchangers have an important characteristic, namely to maintain a good exchange coefficient even at low gas passage speed, while operating with low pressure drops.
Ils sont particulièrement aptes à réaliser un échange efficace à contre-courant, en implantant la surface d'échange nécessaire en un nombre de panneaux en quantité suffisante, et en adaptant une structure des toiles telle que l'écart entre la température des gaz et du fluide thermodynamique en changement d'état, puisse être réduite à quelques degrés, par exemple 2°, voire 1,5°.They are particularly suitable for performing an efficient exchange against the current, by installing the necessary exchange surface in a sufficient number of panels, and by adapting a structure of the fabrics such that the difference between the temperature of the gases and of the thermodynamic fluid in change of state, can be reduced to a few degrees, for example 2 °, even 1.5 °.
Suivant une variante préférentielle, la combinaison de ces trois moyens, à savoir l'utilisation de plusieurs pompes à chaleur thermodynamiquement indépendantes, le choix de mélanges non azéotropiques bien adaptés, et l'utilisation d'échangeurs à toiles métalliques, permet de réduire fortement l'écart entre les pressions de condensation et d'évaporation pour chaque cycle thermodynamique, et d'améliorer le coefficient de performance dans les mêmes proportions, également dans le cas où les fluides externes sont des gaz.According to a preferred variant, the combination of these three means, namely the use of several thermodynamically independent heat pumps, the choice of well-suited non-azeotropic mixtures, and the use of metal fabric exchangers, makes it possible to greatly reduce the 'difference between the condensation and evaporation pressures for each thermodynamic cycle, and to improve the coefficient of performance in the same proportions, also in the case where the external fluids are gases.
Suivant une application particulière du procédé de chauffage par pompes à chaleur, les ensembles de pompes à chaleur sont utilisés pour les installations de séchage avec récupération de l'enthalpie de l'air extrait.According to a particular application of the heat pump heating process, the heat pump assemblies are used for drying installations with recovery of the enthalpy of the extracted air.
La combinaison des trois moyens cités ci-avant est susceptible de donner un résultat remarquable dans de nombreuses installations de séchage, lesquelles dans leur ensemble, utilisent environ 20% de l'énergie fossile consommée par l'industrie.The combination of the three means mentioned above is likely to give a remarkable result in many drying installations, which as a whole use around 20% of the fossil energy consumed by industry.
Il est important de remarquer que le progrès très substantiel apporté par la combinaison de ces trois moyens, résulte en fait pour chacun de ces moyens, de la recherche d'une meilleure valorisation de l'exergie de l'enthalpie disponible dans le ou les fluides externes où l'enthalpie est récupérée, et simultanément, d'économies d'exergie dans les apports d'enthalpie aux fluides externes des sources chaudes.It is important to note that the very substantial progress brought by the combination of these three means, results in fact for each of these means, from the search for a better valorization of the exergy of the enthalpy available in the fluid (s) external where the enthalpy is recovered, and simultaneously, energy savings in the enthalpy contributions to the external fluids of the hot springs.
En faisant intervenir le niveau de température où l'enthalpie est récupérée dans la source froide, ou apportée à la source chaude, l'exergie permet de mesurer la qualité de ces enthalpies.By involving the temperature level where the enthalpy is recovered in the cold source, or brought to the hot source, the exergy makes it possible to measure the quality of these enthalpies.
Dans le procédé objet de la présente invention, la combinaison de ces trois moyens permet aux pompes à chaleur de mieux remplir leur fonction qui est de relever l'exergie d'enthalpies récupérées à des températures plus basses que celles de leur utilisation. Mais simultanément, le travail de compression apporte un complément inévitable d'enthalpie coûteux que le procédé permet de réduire fortement par le biais de faibles taux de compression, en évitant tout gaspillage d'exergie.In the process which is the subject of the present invention, the combination of these three means allows the heat pumps to better fulfill their function which is to raise the exergy of enthalpies recovered at temperatures lower than those of their use. But simultaneously, the compression work brings an inevitable complement of costly enthalpy that the process makes it possible to greatly reduce through low compression rates, avoiding any waste of exergy.
Au même titre que l'air extrait des séchoirs, les fumées de toute installation de chauffage au gaz naturel, grâce à leur forte teneur en vapeur d'eau - les fumées de la combustion neutre du méthane ont la même teneur en eau que de l'air saturé d'humidité à 57° - se prêtent particulièrement bien à une récupération non seulement de la marge existant entre les pouvoirs calorifique supérieur et inférieur, soit par exemple 9,8 - 8,8 = 1 kWh/m³ pour les gaz de Groeningen, mais aussi de la fraction du rendement sur pouvoir calorifique inférieur que l'installation de chauffage n'a pas pu récupérer.As with the air extracted from driers, the fumes of any natural gas heating installation, thanks to their high water vapor content - the fumes from the neutral combustion of methane have the same water content as l air saturated with humidity at 57 ° - lend themselves particularly well to recovery not only of the margin existing between the upper and lower calorific values, for example 9.8 - 8.8 = 1 kWh / m³ for Groeningen, but also of the fraction of the yield on lower calorific value that the heating installation could not recover.
En saturant éventuellement en vapeur d'eau les fumées de ces installations par transformation de leur chaleur sensible en chaleur latente, et en éliminant simultanément à contre-courant toute impureté majeure dans une tour équipée de corps de remplissage et arrosée d'eau en renouvellement permanent par l'adjonction des condensats des évaporateurs des deux pompes à chaleur, on obtient un gaz saturé d'humidité dont les caractéristiques sont très voisines de celles de l'air extrait d'un séchoir.By possibly saturating the fumes of these installations with water vapor by transforming their sensible heat into latent heat, and simultaneously eliminating against the current any major impurity in a tower equipped with filling and sprinkled bodies of water in permanent renewal by the addition of the condensates of the evaporators of the two heat pumps, a gas saturated with humidity is obtained whose characteristics are very similar to those of the air extracted from a dryer.
Une telle installation peut par exemple, être utilement envisagée derrière des chaudières au gaz naturel suffisamment importantes équipant des chauffages d'immeubles, car elle apporte l'avantage très important vis-à-vis des chaudières à condensation, d'améliorer fortement le taux de récupération d'enthalpie quelle que soit la température des retours, et de porter au niveau généralement requis de 70° ou plus si nécessaire la totalité de l'enthalpie récupérée.Such an installation can, for example, be usefully envisaged behind sufficiently large natural gas boilers fitted with building heaters, since it provides the very significant advantage with respect to condensing boilers, greatly improving the rate of recovery of enthalpy whatever the temperature of the returns, and bringing to the generally required level of 70 ° or more if necessary the totality of the recovered enthalpy.
En particulier dans les installations de chauffage urbain qui ne sont en général pas équipées de turbines à contre-pression pour produire simultanément de l'électricité, il suffirait de prévoir une légère surchauffe de la vapeur produite dans la chaudière, pour donner à la vapeur vive le très faible complément d'énergie vis-à-vis de l'énergie globale mise en oeuvre, qui serait requis pour alimenter deux petites turbines à contre-pression, couplées sur les compresseurs, pour apporter à ceux-ci l'énergie mécanique qui serait d'ailleurs finalement récupérée par les condenseurs des pompes à chaleur, mais il est vrai, avec une exergie fortement réduite.In particular in district heating installations which are generally not equipped with back-pressure turbines to simultaneously produce electricity, it would suffice to provide for a slight overheating of the steam produced in the boiler, to give live steam. the very low complement of energy vis-à-vis the overall energy used, which would be required to supply two small back-pressure turbines, coupled on the compressors, to provide them with the mechanical energy which would also be finally recovered by the condensers of the heat pumps, but it is true, with a greatly reduced exergy.
Par variation de la vitesse des turbines, la puissance de l'installation serait aisément ajustable en parallèle avec la puissance demandée à la chaudière; il est vraisemblable qu'une valorisation même partielle du pouvoir calorifique supérieur, permettra d'amortir très rapidement le coût de l'installation, amortissement qui sera cependant sensible à la température de retour des condensats.By varying the speed of the turbines, the power of the installation would be easily adjustable in parallel with the power required from the boiler; it is likely that even partial recovery of the higher calorific value will very quickly amortize the cost of the installation, which will however be sensitive to the condensate return temperature.
Les diagrammes de la figure 1 donnent pour une température humide de 53° de l'air extrait d'un séchoir qui représente une excellente source froide, une image très représentative de la part prise par chacun de ces moyens dans la valorisation de l'exergie de l'enthalpie récupérée.The diagrams of FIG. 1 give for a humid temperature of 53 ° of the air extracted from a dryer which represents an excellent cold source, a very representative image of the part taken by each of these means in the valorization of the exergy of the enthalpy recovered.
Des diagrammes semblables auraient pu être établis pour l'apport d'enthalpie à l'air de séchage, mais la diversité des méthodes et des températures de l'air utilisé dans les séchoirs est telle qu'il n'est pas possible d'envisager valablement un cas particulier; cependant les diagrammes auraient des allures semblables à ceux qui sont présentés pour la récupération sur l'air extrait, diagrammes qui à la seule exception de la variation de la température humide de l'air extrait, sont identiques pour tous les séchoirs.Similar diagrams could have been drawn for the enthalpy supply to the drying air, but the variety of methods and temperatures of the air used in the dryers is such that it is not possible to validly consider a particular case; however, the diagrams would look similar to those presented for recovery on the extract air, diagrams which with the only exception of the variation of the wet temperature of the extract air, are identical for all the dryers.
Dans le diagramme 1-a de la figure 1 qui correspond à l'emploi d'une pompe à chaleur unique, l'aire hachurée est relative à de l'enthalpie dont l'exergie croissante entre 23° et 53°, n'a été en fait valorisée qu'au niveau exergétique de 23°.In diagram 1-a of figure 1 which corresponds to the use of a single heat pump, the hatched area is relative to enthalpy whose exergy increasing between 23 ° and 53 °, has was actually valued only at the exergy level of 23 °.
Ce diagramme correspond à l'emploi d'un corps pur ou d'un mélange azéotropique comme fluide thermodynamique.This diagram corresponds to the use of a pure body or an azeotropic mixture as thermodynamic fluid.
Dans le diagramme 1-b qui correspond à l'emploi de deux pompes à chaleur thermodynamiquement indépendantes, utilisant les mêmes fluides thermodynamiques que les précédents, on constate que la zone importante du rectangle non hachuré, est relative à une part notable de l'enthalpie dont on a évité de perdre l'exergie grâce à l'emploi de deux pompes à chaleur thermodynamiquement indépendantes; toute l'enthalpie de cette zone est récupérée par la deuxième pompe à chaleur avec l'exergie qui lui est propre depuis le niveau de 40°, au lieu de seulement 23° dans le diagramme 1-a.In diagram 1-b which corresponds to the use of two thermodynamically independent heat pumps, using the same thermodynamic fluids as the previous ones, it can be seen that the large area of the unshaded rectangle is relative to a significant part of the enthalpy which was avoided losing the exergy through the use of two thermodynamically independent heat pumps; all the enthalpy of this zone is recovered by the second heat pump with its own exergy from the level of 40 °, instead of only 23 ° in diagram 1-a.
Pour les deux pompes à chaleur du diagramme 1-b, l'écart final entre la température de l'air sortant de l'évaporateur, et celle du fluide thermodynamique entrant dans l'évaporateur, est supposé réduit à 2°, soit un pincement relativement faible; par contre, à l'autre extrémité de ces circuits d'échange, ces écarts restent importants, 53° - 39,5° = 13,5° et 41,5° - 23° = 18,5°, ce qui permet d'employer dans la plus grande partie des évaporateurs, des échangeurs relativement peu performants.For the two heat pumps in diagram 1-b, the final difference between the temperature of the air leaving the evaporator and that of the thermodynamic fluid entering the evaporator is assumed to be reduced to 2 °, i.e. a pinch relatively weak; on the other hand, at the other end of these exchange circuits, these differences remain significant, 53 ° - 39.5 ° = 13.5 ° and 41.5 ° - 23 ° = 18.5 °, which allows d '' use in most evaporators, relatively inefficient exchangers.
Le diagramme 1-c de la figure 1 est relatif à l'utilisation de mélanges non azéotropiques comme fluide thermodynamique, et à l'emploi d'échangeurs performants, tels que les échangeurs à toiles métalliques dans le cas où les fluides externes sont des gaz, échangeurs mentionnés ci-avant qui permmettent en fonctionnant à contre-courant, de valoriser pleinement le fait que les isobares d'évaporation (et de condensation) ne sont plus des isothermes, et que ces isobares peuvent couvrir des plages de températures supérieures à 15°.Diagram 1-c of FIG. 1 relates to the use of non-azeotropic mixtures as thermodynamic fluid, and to the use of efficient exchangers, such as metal mesh exchangers in the case where the external fluids are gases , exchangers mentioned above which allow, by operating against the current, to fully exploit the fact that the isobars of evaporation (and condensation) are no longer isotherms, and that these isobars can cover temperature ranges above 15 °.
On remarque dans ce diagramme 1-c que les zones hachurées ne correspondent pratiquement plus qu'à l'exergie minimum qui est nécessaire pour assurer avec un pincement faible de 2°, le transfert d'enthalpie au cours des échanges successifs entre l'air extrait et le fluide thermodynamique des deux pompes à chaleur.We note in this diagram 1-c that the hatched zones practically correspond only to the minimum exergy which is necessary to ensure with a weak nip of 2 °, the transfer of enthalpy during the successive exchanges between the air extract and the thermodynamic fluid of the two heat pumps.
Le même principe de valorisation maximum de l'exergie de l'enthalpie de condensation des mélanges non azéotropiques tout au long de l'échange à contre-courant, par le biais d'un pincement très réduit entre la température du fluide thermodynamique et celle de l'air chauffé par les pompes à chaleur, doit être soigneusement respecté.The same principle of maximum recovery of the exergy of the enthalpy of condensation of non-azeotropic mixtures throughout the exchange against the current, by means of a very reduced pinching between the temperature of the thermodynamic fluid and that of the air heated by heat pumps must be carefully observed.
Les dispositions adoptées, et l'ensemble des trois moyens mis en oeuvre, apportent donc la solution thermodynamiquement optimum que l'on peut réaliser, et qui est de nature à procurer un excellent coefficient de performance.The provisions adopted, and all three means implemented, therefore provide the thermodynamically optimum solution that can be achieved, and which is likely to provide an excellent coefficient of performance.
L'emploi d'au moins deux pompes à chaleur thermodynamiquement indépendantes implique évidemment l'emploi d'au moins deux compresseurs et deux détendeurs, fournissant ensemble la même puissance thermique, tout en consommant une puissance mécanique totale fortement réduite vis-à-vis de celle qu'exigerait l'emploi d'une seule pompe à chaleur.The use of at least two thermodynamically independent heat pumps obviously implies the use of at least two compressors and two pressure reducers, providing together the same thermal power, while consuming a greatly reduced total mechanical power vis-à-vis that would require the use of a single heat pump.
De même, la nécessité d'assurer avec un pincement faible, un échange à contre-courant suivant l'évolution des températures de condensation et d'évaporation des mélanges non azéotropiques, conduit à prévoir des échangeurs largement dimensionnés susceptibles d'assurer ce pincement faible.Similarly, the need to ensure with a weak pinch, a countercurrent exchange according to the evolution of the condensation and evaporation temperatures of the non-azeotropic mixtures, leads to the provision of large-sized exchangers capable of ensuring this weak pinch. .
Mais l'importance du progrès apporté par la combinaison de ces trois moyens permet non seulement de compenser la charge de l'amortissement et du financement du surcoût de l'investissement, mais aussi de réaliser simultanément une économie très substantielle dans l'exploitation de ce procédé de chauffage par au moins deux pompes à chaleur thermodynamiquement indépendantes.But the importance of the progress brought by the combination of these three means not only makes it possible to offset the cost of depreciation and the financing of the additional cost of the investment, but also to simultaneously realize a very substantial saving in the exploitation of this heating process by at least two thermodynamically independent heat pumps.
L'invention exposée ci-avant sera mieux comprise à l'aide d'une réalisation non limitative se rapportant à un procédé de séchage correspondant aux conditions thermiques de séchoirs existants.The invention described above will be better understood with the aid of a nonlimiting embodiment relating to a drying process corresponding to the thermal conditions of existing dryers.
La figure 2 représente l'évolution en fonction des enthalpies transférées, des températures des mélanges non azéotropiques figurées en traits continus, tandis que celles de l'air extrait et celles de l'air de séchage sont figurées en traits interrompus, les flèches représentant les transferts d'enthalpie.FIG. 2 represents the evolution as a function of the transferred enthalpies, of the temperatures of the non-azeotropic mixtures shown in solid lines, while those of the extracted air and those of the drying air are shown in broken lines, the arrows representing the enthalpy transfers.
L'air extrait du séchoir, lavé et saturé d'eau à 53°, pénètre en 1 dans l'évaporateur 2 de la pompe à chaleur B, avec une enthalpie de 319 kJ/kg d'air sec; l'air y est refroidi avec une forte récupération de chaleur latente de condensation de la vapeur d'eau, mais avec une diminution relativement modérée de sa température entre 53° et 41,5° à la sortie de l'évaporateur en 3. Son enthalpie est par contre fortement réduite de 319 à 179 kJ/kg d'air sec, soit un prélèvement de 140 kJ/kg d'air sec.The air extracted from the dryer, washed and saturated with water at 53 °, enters 1 into the
L'air extrait pénètre alors directement dans l'évaporateur 4 de la pompe à chaleur A qu'il quitte en 5 à 25°. Son enthalpie est réduite de 179 à 76 kJ/kg d'air sec, soit un prélèvement de 103 kJ/kg d'air sec.The extracted air then enters directly into the
Le mélange non azéotropique détendu dans la pompe à chaleur A s'évapore à contre-courant entre 23° et 39,5° dans l'évaporateur 4, avant d'être aspiré par le compresseur 6. Dans le condenseur 7, la condensation du mélange non azéotropique a lieu entre 66° et 46°; elle est suivie d'un sous-refroidissement 8 jusqu'à 33° par échange à contre-courant avec l'air frais entrant à 20° dans le condenseur 7 pour en sortir à 64°.The non-azeotropic mixture expanded in the heat pump A evaporates against the current between 23 ° and 39.5 ° in the
Après passage dans le détendeur 9 de la pompe à chaleur A, le mélange non azéotropique réchauffé à contre-courant dans l'évaporateur 4, devient entièrement gazeux en passant de 23° à 39,5°.After passing through the
De même dans la pompe à chaleur B, thermodynamiquement indépendante de la pompe à chaleur A, le mélange non azéotropique est aspiré gazeux par le compresseur 10 à 51°; dans le condenseur 11, il devient entièrement liquide entre 76° et 58°, tandis que l'air est réchauffé de 56° à 74°.Similarly in the heat pump B, thermodynamically independent of the heat pump A, the non-azeotropic mixture is sucked gas by the
Le détendeur 12 alimente l'évaporateur 2 à une température de 36°, tandis que l'air quitte cet évaporateur à 41,5°.The regulator 12 supplies the
On peut apprécier les progrès que permet la présente invention en comparant les écarts entre les températures du mélange non azéotropique qui déterminent les niveaux de pression de condensation et d'évaporation, à savoir 76° - 51,5° = 25° et 66° - 39,5° = 26,5° au lieu de 76° - 39,5° = 36,5° en utilisant une seule pompe à chaleur avec un mélange non azéotropique, ou 76° - 23° = 53° pour une seule pompe à chaleur utilisant selon la technique généralement employée actuellement, des corps purs ou des mélanges azéotropiques.The progress made by the present invention can be appreciated by comparing the differences between the temperatures of the non-azeotropic mixture which determine the levels of pressure of condensation and evaporation, namely 76 ° - 51.5 ° = 25 ° and 66 ° - 39.5 ° = 26.5 ° instead of 76 ° - 39.5 ° = 36.5 ° using a single heat pump with a non-azeotropic mixture, or 76 ° - 23 ° = 53 ° for a single pump using heat using the technique generally used today, pure substances or azeotropic mixtures.
De plus, le taux de récupération de l'enthalpie de l'air extrait est voisin de 90% dans le cas de ce séchoir.In addition, the enthalpy recovery rate of the extracted air is close to 90% in the case of this dryer.
Ces constatations permettent d'escompter de fortes améliorations du coefficient de performance global qui pourra atteindre un niveau exceptionnel dans le cas de la combinaison préférentielle : utilisation d'au moins deux pompes à chaleur thermodynamiquement indépendantes, de mélanges non azéotropiques comme fluides thermodynamiques, et d'échangeurs du type à toiles métalliques fonctionnant à contre-courant.These observations make it possible to expect significant improvements in the overall coefficient of performance which may reach an exceptional level in the case of the preferred combination: use of at least two thermodynamically independent heat pumps, non-azeotropic mixtures as thermodynamic fluids, and d exchangers of the metal cloth type operating against the current.
Claims (6)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| BE8901374 | 1989-12-22 | ||
| BE8901374A BE1003595A5 (en) | 1989-12-22 | 1989-12-22 | Process heating heat pumps. |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0435842A1 true EP0435842A1 (en) | 1991-07-03 |
| EP0435842B1 EP0435842B1 (en) | 1995-06-28 |
Family
ID=3884432
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP19900870240 Expired - Lifetime EP0435842B1 (en) | 1989-12-22 | 1990-12-14 | Heating process using heat pumps |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0435842B1 (en) |
| BE (1) | BE1003595A5 (en) |
| DE (1) | DE69020528T2 (en) |
| ES (1) | ES2077057T3 (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2347087A1 (en) * | 1976-04-06 | 1977-11-04 | Syrec Systemes Recuper Chaleur | Drying of gases, e.g. air from factory or process - using several heat pumps with heat recycle, saving energy |
| US4124177A (en) * | 1977-04-21 | 1978-11-07 | Timmerman Robert W | Heating system |
| FR2402844A1 (en) * | 1977-09-08 | 1979-04-06 | Girodin Tech | Pump with multiple heat producing circuits - having compressor and drive of same capacity, and evaporator and condenser of same surface area |
| FR2453373A1 (en) * | 1979-04-02 | 1980-10-31 | Valmet Oy | HEAT RECOVERY METHOD BASED ON THE USE OF A HEAT PUMP |
| DE3013820A1 (en) * | 1980-04-10 | 1981-10-15 | Jürgen Dipl.-Ing. 8026 Irschenhausen Lambrecht | Drying system with energy recuperation - uses main heat pump followed by auxiliary modular heat pump units in axial arrangement |
| DE3319348A1 (en) * | 1982-05-28 | 1983-12-01 | Valmet Oy, 00130 Helsinki | Heat recovery process |
| EP0165848A1 (en) * | 1984-05-28 | 1985-12-27 | Institut Français du Pétrole | Method for the production of heat and/or cold by means of a compression machine using a mixed working medium |
| EP0354892A1 (en) * | 1988-07-29 | 1990-02-14 | Société Anonyme ECONERGIE | Heat exchanger for use between a gas and a fluid, with increased thermal exchange properties |
-
1989
- 1989-12-22 BE BE8901374A patent/BE1003595A5/en not_active IP Right Cessation
-
1990
- 1990-12-14 DE DE1990620528 patent/DE69020528T2/en not_active Expired - Fee Related
- 1990-12-14 ES ES90870240T patent/ES2077057T3/en not_active Expired - Fee Related
- 1990-12-14 EP EP19900870240 patent/EP0435842B1/en not_active Expired - Lifetime
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2347087A1 (en) * | 1976-04-06 | 1977-11-04 | Syrec Systemes Recuper Chaleur | Drying of gases, e.g. air from factory or process - using several heat pumps with heat recycle, saving energy |
| US4124177A (en) * | 1977-04-21 | 1978-11-07 | Timmerman Robert W | Heating system |
| FR2402844A1 (en) * | 1977-09-08 | 1979-04-06 | Girodin Tech | Pump with multiple heat producing circuits - having compressor and drive of same capacity, and evaporator and condenser of same surface area |
| FR2453373A1 (en) * | 1979-04-02 | 1980-10-31 | Valmet Oy | HEAT RECOVERY METHOD BASED ON THE USE OF A HEAT PUMP |
| DE3013820A1 (en) * | 1980-04-10 | 1981-10-15 | Jürgen Dipl.-Ing. 8026 Irschenhausen Lambrecht | Drying system with energy recuperation - uses main heat pump followed by auxiliary modular heat pump units in axial arrangement |
| DE3319348A1 (en) * | 1982-05-28 | 1983-12-01 | Valmet Oy, 00130 Helsinki | Heat recovery process |
| EP0165848A1 (en) * | 1984-05-28 | 1985-12-27 | Institut Français du Pétrole | Method for the production of heat and/or cold by means of a compression machine using a mixed working medium |
| EP0354892A1 (en) * | 1988-07-29 | 1990-02-14 | Société Anonyme ECONERGIE | Heat exchanger for use between a gas and a fluid, with increased thermal exchange properties |
Also Published As
| Publication number | Publication date |
|---|---|
| DE69020528D1 (en) | 1995-08-03 |
| BE1003595A5 (en) | 1992-04-28 |
| EP0435842B1 (en) | 1995-06-28 |
| ES2077057T3 (en) | 1995-11-16 |
| DE69020528T2 (en) | 1996-03-21 |
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