EP1101071B1 - Procede pour detacher les cristaux de glace d'un echangeur thermique generateur d'un frigoporteur diphasique liquide-solide - Google Patents
Procede pour detacher les cristaux de glace d'un echangeur thermique generateur d'un frigoporteur diphasique liquide-solide Download PDFInfo
- Publication number
- EP1101071B1 EP1101071B1 EP00931340A EP00931340A EP1101071B1 EP 1101071 B1 EP1101071 B1 EP 1101071B1 EP 00931340 A EP00931340 A EP 00931340A EP 00931340 A EP00931340 A EP 00931340A EP 1101071 B1 EP1101071 B1 EP 1101071B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- generator
- refrigerant
- speed
- calculator
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/006—Preventing deposits of ice
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C5/00—Working or handling ice
- F25C5/02—Apparatus for disintegrating, removing or harvesting ice
- F25C5/04—Apparatus for disintegrating, removing or harvesting ice without the use of saws
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
Definitions
- the invention relates to the field of production and distribution of cold at medium of a biphasic liquid + solid solid refrigerant fluid.
- the biphasic liquid + solid solid refrigerant fluid consists of a mixture of two liquids, usually a mixture of water, and another a liquid miscible with water, namely ethanol, methanol, ammonia, calcium chloride or other. This mixture is cooled down to crystallization temperature of the water. The crystals then formed are driven by the coolant in the liquid phase.
- This mixture of crystals and liquid phase is defined by the term two-phase refrigerant or "grout of ice cream "
- Ice slurry presents, compared to refrigerants fluids monophasic, significant advantages. Changing partially in state, these two-phase liquid + solid refrigerants latent heat of transformation (solid to liquid) and allow a much larger transport of cold per unit of volume which has the advantage of reducing the flow rates in circulation. This significantly reduces the flow of the pumps and the diameter of the distribution pipes.
- the ice slurries are formed in generators that have for object of generating ice crystals that are driven by the phase liquid of the refrigerant fluid.
- These generators have walls heat exchange swept on one side by the coolant fluid and on the other side by a refrigerant.
- These heat exchange walls may be in the form of a bundle of flat tubes or cylindrical elements forming part of a first fluid circuit, this beam being disposed in a chamber forming part of a second fluid circuit.
- the refrigerant fluid flows into one of the circuits, while the fluid refrigerant flows into the other circuit.
- Ice crystals form on the face of the generator walls swept by the coolant fluid and tend to stick to these walls.
- the direct consequences are an increase in losses of load, a decrease in heat exchange; the purpose of the generator being to make crystals it is therefore necessary to provide means for detach the crystals formed on the walls.
- the object of the invention is to propose a new method to generate ice crystals and to detach part of the crystals ice forming on the walls of an ice slurry generator and which can be implemented easily on all types of exchanger whatever the geometrical shape of their heat exchange wall.
- the invention is based on the idea of creating intermittently determined by a calculator of turbulence in the refrigerant fluid by increase of the flow, therefore of the speed of circulation.
- the results of the increase in the speed of circulation are on the one hand: a increased tearing force applied to the crystals in training and on the other hand a modification of the exchange parameters which induce a slight increase in the temperature of the walls.
- triggering of these actions and their durations are variables and depend on a large number of fixed parameters and variables (difference in pressure and temperature of inlet and outlet of the exchanger) and which are transmitted to a calculator which determines the frequencies and durations.
- the invention thus relates to a method for detaching the part of generated ice crystals that stays attached to the wall surface heat exchanger of an ice slurry generator exchanger, said face being in contact with a coolant fluid of a first circuit which flows at a nominal speed into said exchanger, while the other face of said walls is in contact with a cooling fluid flowing in a second circuit.
- the two-phase process is characterized by the determination of the timing of the phase changes and their duration are a function of a number of parameters inherent to the fluid refrigerant itself (concentration of the nominal mixture, type of mixture) and some variable parameters that are the temperature the coolant inlet and outlet of the exchanger, measured by thermal probes (10) and (11), and by the evolution of the pressure drops of the fluid in the exchanger measured using a pressure switch differential.
- phase 1 During phase 1 :
- the coolant fluid is circulated by a pump and one increases on the order of a calculator or an automaton the speed of rotation of the pump.
- the pump is driven for example by a speed motor variable that allows to maintain in all phases a specific flow and constant regardless of the pressure losses of the refrigerant fluid in the exchanger.
- the basic speed of the motor and the pump, and therefore the flow rate or the nominal speed of the secondary refrigerant in the generator as well as the surface temperature of the cold wall are depending on the type of exchanger, the secondary coolant and the concentration of the mixture as well as the concentration of the solid particles that we want to obtain in the diphasic refrigerant fluid.
- the ice crystals are detached without mechanical means arranged in the generator as in the art prior.
- the frequency and duration of turbulence, as well as the speed of Refrigerant fluid during the turbulence phase can be established by test results which will serve as a basis for the programming of the calculator or PLC. They will depend on the type of exchanger, the refrigerant, mixture concentration and concentration solid particles that we want to achieve in the coolant.
- the trigger, and the phase duration are done automatically thanks to a calculator.
- a calculator we measure in continuously the pressure loss experienced by the coolant through the generator, as well as its inlet and outlet temperature, and adjust the speed of the pump as well as the power of the refrigerating plant in function of the phases.
- the temperature of the cooling fluid is increased by increasing the evaporation pressure. This can be achieved by Maneuvering the inlet and outlet valves of the generator on the second circuit and in this case the temperature rise and without external energy supply. Another device is injecting into the generator of hot gases from the gas compressor, and in this case it is with external energy supply.
- the reference numeral 1 represents ice slurry generator which has exchange walls 2 separating a first circuit 3 in which flows a fluid two-phase coolant water / ice, the second circuit 4 in which flows a cooling fluid designed to cool the coolant fluid of the first circuit 3.
- the first circuit 3 comprises outside the generator 1 a conduit 5 for supplying ice slurry for supplying in parallel with heat exchangers 6 and a return pipe 7 equipped with a circulation pump 8.
- the exchangers 6 can be connected directly between the ducts 5 and 7, or mounted on branches equipped with a bridge 9 autonomous.
- the exchangers 6 are intended for cooling premises or products, the cold being obtained by melting the ice crystals contained in the refrigerant fluid passing through them.
- the ice concentration of the fluid coolant in the return pipe 7 is thus lower than that of the fluid coolant in the delivery line 5.
- the temperature of the coolant fluid in the return duct 7 is greater than the temperature of the coolant fluid in the delivery conduit 5 of the grout of ice, and the measurement of these temperatures at the entry and exit of generator by the probes 10 and 11 allows to know with a good accuracy the crystal concentrations for a type of mixture used in as coolant fluid and the concentration of the mixture.
- a tarpaulin 12 recirculation can advantageously serve addition, must be placed between the delivery line 5 and the return duct 7.
- a circulation pump 8b is mounted on the led 5 downstream of the tarpaulin 12.
- the coolant circulating in the generator 1 is cooled by the cooling fluid, thanks to the thermal exchanges that take place through exchange walls 2. ice crystals are then formed on the face of the walls 2, which is in contact with the refrigerant fluid of the circuit 3.
- the circulation pump 8 mounted on the return duct 7 is driven in rotation by a variable speed electric motor 13.
- circulation pump 8 is driven at a substantially constant speed, what we call base speed, and the coolant fluid then flows into the generator 1 with a substantially constant flow rate which is the normal flow of the generator 1 and at a roughly constant speed that we call speed nominal Vn.
- the ice crystals which are form on one side of the heat exchange walls 2, by circulating intermittently defined by the computer 16, the coolant fluid in the generator 1 at a speed Vs greater than the nominal speed Vn in order to create in the portion of the circuit 1 located in the generator 1 of turbulence that slightly warms the walls 2 and leads to additional forces for tearing crystals.
- the speed increase of the coolant fluid is obtained by acting on the speed of rotation of the motor 13 which causes the pump 8.
- Figure 3 shows the flow velocity graph of the fluid refrigerant in the generator 1.
- the time interval T o between two phases of turbulence T1 and T2 and the duration Do of each phase of turbulence are obtained by integration into the calculator of experimentation, and are dependent on the type of generator, the type of refrigerant, the proportion of the mixture and the concentration of the crystals used.
- the electric motor is driven by an automaton 14 in the memory of which four data are introduced operating characteristics: the base speed corresponding to the nominal speed Vn, the maximum speed corresponding to the speed Vs, the time interval T 0 during which the engine is running at its speed displayed base, and the duration Do of a turbulent phase.
- the automaton 14 obviously has an internal clock.
- two probes of a differential pressure switch 15 are interposed between the inlet and the outlet of the ducts 5 and 7 in the generator.
- This pressure switch 15 measures the pressure drop experienced by the refrigerant fluid through the generator 1. This pressure drop is a function of the amount of ice crystals deposited on the walls 2 and the ice concentration of the coolant fluid.
- the measurement of the pressure switch 15 is transmitted to a calculation element 16 which compares it to a setpoint value, and when this measurement is greater than the setpoint value, the calculation unit 16 controls the motor 13 to rotate at its maximum speed. for a duration Do. Then, the computing unit 16 controls the motor 13 to rotate at its base speed.
- the measurements of the temperature probes 10 and 11 are also transmitted to the calculation element 16.
- the latter is able to correct the setpoint value as a function of the measurements of the temperature probes 10 and 11 which are representative of the concentration of the crystals in the refrigerant fluid at the inlet and outlet of the generator 1.
- the nominal pressure drop of the refrigerant fluid through the generator 1, in the absence of crystals bonded to the walls 2, is therefore a function of the temperatures measured and the nominal speed of the coolant fluid.
- the computing unit 16 controls the motor 13 to rotate at its maximum speed for a duration Do.
- the computing unit 16 acts on the circulation of the cooling fluid in the exchanger 1 in order to continuously adapt the temperature of the walls exchange 2 with a view to optimizing the efficiency of the installation, and to obtain new crystals until the concentration of desired crystals.
- the invention When the refrigerant fluid of circuit 1 flows into the generator in turbulence mode in order to detach the ice crystals formed on the walls 2, the invention further provides to increase very rapidly and simultaneously the temperature of the cold walls 2 by acting on the side of the coolant fluid. This is achieved by increasing the temperature of the fluid cooler during the period of turbulence.
- the method differs depending on the type of coolant.
- the fluid cooler flowing in the second circuit 4 is a liquid in phase evaporation in the ice slurry generator 1.
- the generator 1 plays thus the role of evaporator for the coolant fluid.
- the gases produced in the generator 1 are sucked by a gas compressor 20 mounted in the suction circuit 21 which connects the generator 1 to a condenser 22.
- a pressure regulating valve 23 is mounted on the conduit 21.
- the refrigerant in the liquid state returns to the generator 1 by a supply duct 24 on which is mounted a control valve 25 for injecting refrigerant.
- a derivation 26 is provided between the discharge outlet of the compressor 20 and the inlet of the supply circuit 24 in the generator 1.
- a valve 27 for injecting Hot gas is mounted on the bypass 26.
- the controller 14 or the calculator 16 also acts on the valves 23 and 25 or on the hot gas injection valve 27.
- the action on the valves 23 and 25 modifies the degree of closure of the evaporation pressure and thus modifies the temperature of the cooling fluid without external energy input.
- the action on the hot gas injection valve 27 also modifies the evaporation pressure and therefore the temperature but with external energy supply. In both cases, this leads, with different intensities, to the temperature rise of the cold walls 2 and favors the detachment of the ice crystals.
- the coolant fluid flowing in the second circuit 4 is itself a coolant fluid cooled in a generator 30 supplied with coolant fluid by a circuit 4b similar to the circuit 4 of FIG.
- a three-way valve 40 is mounted on the supply circuit 24 of the fluid of the circuit 4 and a bypass 41 is provided between the three-way valve 40 and the return line 42 of the fluid of the circuit 4.
- the three-way valve 41 is controlled by the controller 14 or the computing unit 16, and during the duration phase Do in the first circuit 3, the cooling fluid recirculates through the bypass duct 41, this which causes the warming of the cold walls 2.
- the second generator 30 can also be driven by another controller or another calculating organ to take off the ice crystals that form there, in the case where the cold-transfer fluid flowing in the second circuit 4 is biphasic
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Other Air-Conditioning Systems (AREA)
- Physical Or Chemical Processes And Apparatus (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Production, Working, Storing, Or Distribution Of Ice (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
- Une action thermique de décollement des cristaux de glace sous forme de modification du coefficient d'échange engendrée par l'augmentation de vitesse et de diminution de l'énergie frigorifique sur le fluide refroidisseur circulant de l'autre côté de la paroi.
- Une action hydro- mécanique d'entraínement des cristaux qui ont été détachés au préalable par l'action thermique (début de changement d'état solide vers liquide).
- Des turbulences dans le fluide figoporteur par augmentation du débit, donc de la vitesse de circulation.
- Une diminution de l'énergie frigorifique transportée par le fluide refroidisseur.
- Les conséquences de ces deux actions sont :
- 1. La diminution de la force d'accrochage des cristaux par effet thermique suite à la diminution de l'énergie frigorifique côté fluide refroidisseur et à la modification du coefficient d'échange par augmentation de la vitesse
- 2. L'augmentation de la force d'arrachement par effet hydro mécanique simultanément à la diminution de la force d'accrochage par effet thermique
- la vitesse du fluide frigoporteur est Vn
- l'énergie frigorifique fournie par le fluide refroidisseur est à son maximum
- la durée de temps est To
- la vitesse du fluide figoporteur est Vs supérieure à Vn
- l'énergie frigorifique fournie par le fluide refroidisseur est à son minimum
- la durée de temps est Do.
D'autres avantages et caractéristiques de l'invention ressortiront à la lecture de la description suivante faite à titre d'exemple et en référence aux dessins annexés dans lesquels :
Les mesures des sondes de température 10 et 11 sont également transmises à l'organe de calcul 16. Ce dernier est apte à corriger la valeur de consigne en fonction des mesures des sondes de température 10 et 11 qui sont représentatives de la concentration des cristaux dans le fluide frigoporteur à l'entrée et à la sortie du générateur 1. La perte de charge nominale du fluide frigoporteur à travers le générateur 1, en l'absence de cristaux collés sur les parois 2, est donc fonction des températures mesurées et de la vitesse nominale du fluide figoporteur. Lorsque la différence entre la perte de charge mesurée par le pressostat différentiel 15 et la perte de charge nominale est supérieure à la valeur de consigne, l'organe de calcul 16 commande le moteur 13 à tourner à sa vitesse maximum pendant une durée Do.
L'action sur les vannes 23 et 25 modifie selon leur degré de fermeture la pression d'évaporation et donc modifie la température du fluide refroidisseur sans apport d'énergie extérieure.
L'action sur la vanne 27 d'injection de gaz chaud modifie également la pression d'évaporation et donc la température mais avec apport d'énergie extérieure.
Dans les deux cas ceci entraíne avec des intensités différentes l'élévation de température des parois froides 2 et favorise le décollement des cristaux de glace.
Une vanne trois voies 40 est montée sur le circuit d'alimentation 24 du fluide du circuit 4 et une dérivation 41 est prévue entre la vanne trois voies 40 et le conduit de retour 42 du fluide du circuit 4.
Claims (7)
- Procédé pour générer des cristaux de glace utilisant un échangeur générateur et détacher la partie résiduelle des cristaux de glace qui se fixe sur une des faces de la paroi (2) d'échange thermique de l'échangeur générateur (1) la dite face étant en contact avec un fluide frigoporteur d'un premier circuit (3) qui s'écoule à une vitesse nominale (Vn) maintenue constante dans le dit échangeur (1)quelle que soit l'évolution des pertes de charges, tandis que l'autre face en contact avec un fluide refroidisseur qui s'écoule dans un deuxième circuit (4),
caractérisé par le fait que après une durée de temps de fonctionnement « To »à la vitesse (Vn) on augmente la vitesse(Vs) du fluide frigoporteur pendant une durée de temps « Do » pour modifier le coefficient d'échange thermique frigoporteur / paroi (2) et permettre le détachement de la partie résiduelle des cristaux de glace fixés sur la paroi (2), par la diminution de la force d'adhérence due à l'effet thermique auto-engendré complété simultanément par un effet hydromécanique, les paramètres de durée de temps et de vitesse de chacun des cycles de fonctionnement « To »à la vitesse(Vn) et « Do » à la vitesse (Vs) sont ajustés individuellement par un organe de calcul (16) qui en fonction des valeurs mesurées par les sondes d'un pressostat différentiel (15) mesurant la perte de charge subie par le fluide frigoporteur à travers l'échangeur générateur(1) les compare à une valeur de consigne que l'organe de calcul est apte à corriger en fonction des mesures des températures du fluide frigoporteur à l'entrée et à la sortie de l'échangeur générateur ('1) par les sondes de température(10) et(11) - Procédé selon la revendication 1 caractérisé par le fait que l'on modifie la vitesse de circulation du fluide frigoporteur à une vitesse (Vs) établie par le calculateur (16) en augmentant le débit de la pompe (8) à l'aide d'un moteur à vitesse variable (13) pendant une durée de 'Do' déterminée par le calculateur (16).
- Procédé selon la revendication 1 et 2 dans lequel le fluide refroidisseur est un liquide en phase d'évaporation dans le générateur (1) et le deuxième circuit (4) comporte un compresseur de gaz (20) caractérisé par le fait que l'on modifie la température d'évaporation pendant le temps 'Do' en modifiant la pression.
- Procédé sans apport d'énergie extérieure selon la revendication 3 caractérisée par le fait que l'on modifie la pression dans le générateur (1) en manoeuvrant les vannes d'entrée et de sortie du générateur sur le deuxième circuit (4)..
- Procédé avec apport d'énergie extérieure selon la revendication 3 caractérisée par le fait que l'on modifie la pression en injectant en plus dans le générateur (1) des gaz chauds issus de la partie refoulement du compresseur de gaz.
- Procédé selon la revendication 3 dans lequel le fluide refroidisseur est un frigoporteur liquide monophasique ou diphasique liquide /solide caractérisé par le fait que l'on augmente la température du fluide refroidisseur en recirculant le fluide refroidisseur, en dehors de l'échangeur générateur (1).
- Générateur de coulis de glace pour la mise en oeuvre du procédé selon l'une quelconque des revendications selon 1 à 6, comportant des parois (2) d'échange thermique entre un premier circuit (3) comportant une pompe de circulation (8) pour l'écoulement d'un fluide frigoporteur à une vitesse nominale (Vn) dans le générateur (1) et un deuxième circuit (4) dans lequel circule un fluide refroidisseur, caractérisé :par le fait qu'il comporte en outre des moyens (14,16) pour augmenter par intermittence la vitesse d'écoulement du fluide frigoporteur afin de créer des turbulences entraínant le détachement de la partie des cristaux de glace formés sur les parois (2) d'échange thermique par réchauffement des parois d'échange (2) sans apport d'énergie calorifique extérieure au système et par effet d'entraínement hydromécaniquepar le fait que les dits moyens comportent un capteur de pression différentielle (15), sous forme de sondes de pression placés à l'entrée et la sortie du générateur, et des sondes de température (10) et (11) à l'entrée et à la sortie du générateur reliées à un organe de calcul (16) qui comprend les moyens de calcul pour déterminer à partir des caractéristiques nominales du frigoporteur et des caractéristiques variables de pression différentielle (15) et de température (10) et (11), la durée 'To', puis augmenter le débit de la pompe afin d'atteindre une vitesse (Vs) du frigoporteur dans le générateur(1), et simultanément modifier la production frigorifique coté fluide refroidisseur pendant une durée 'Do' déterminée également par le calculateurpar le fait que les sondes de pression du pressostat différentiel(15) mesurent une différence de pression entre l'entrée et la sortie du générateur, donc une perte de charge et transmettent ces informations à l'organe de calcul(16)par le fait que les sondes de température (10) et(11) mesurent un écart de température entre l'entrée et la sortie du générateur, donc une qualité d'échange et transmettent ces informations à l'organe de calcul (16).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9906559 | 1999-05-25 | ||
FR9906559A FR2794228B1 (fr) | 1999-05-25 | 1999-05-25 | Procede pour detacher les cristaux de glace d'un echangeur thermique generateur d'un frigoporteur diphasique liquide- solide |
PCT/FR2000/001405 WO2000071945A1 (fr) | 1999-05-25 | 2000-05-23 | Procede pour detacher les cristaux de glace d'un echangeur thermique generateur d'un frigoporteur diphasique liquide-solide |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1101071A1 EP1101071A1 (fr) | 2001-05-23 |
EP1101071B1 true EP1101071B1 (fr) | 2005-10-26 |
Family
ID=9545942
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00931340A Expired - Lifetime EP1101071B1 (fr) | 1999-05-25 | 2000-05-23 | Procede pour detacher les cristaux de glace d'un echangeur thermique generateur d'un frigoporteur diphasique liquide-solide |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1101071B1 (fr) |
AT (1) | ATE308021T1 (fr) |
DE (1) | DE60023422T2 (fr) |
FR (1) | FR2794228B1 (fr) |
WO (1) | WO2000071945A1 (fr) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2835600B1 (fr) * | 2002-02-01 | 2005-09-02 | Michel Barth | Procede de detachement de cristaux hydriques sur la surface interne d'un echangeur de chaleur |
FR2960630B1 (fr) * | 2010-05-25 | 2012-05-04 | Michel Barth | Procede pour produire et separer des cristaux de glace a partir d'un frigoporteur diphasique liquide-solide |
FR3004797B1 (fr) * | 2013-04-23 | 2018-05-18 | Axima Refrigeration France | Procede de detachement de cristaux hydriques sur la surface interne d'un echangeur de chaleur sans elevation de la temperature du frigoporteur a l'entree de l'echangeur |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4075863A (en) * | 1976-08-23 | 1978-02-28 | Storm King Products, Inc. | Freeze-harvest control system for a tubular ice maker |
US4401449A (en) * | 1982-04-29 | 1983-08-30 | Refrigeration Engineering Corporation | Slush ice maker |
IN161820B (fr) * | 1983-08-26 | 1988-02-06 | Gilbertson Thomas A | |
CH673700A5 (fr) * | 1987-05-12 | 1990-03-30 | Steinemann Ag | |
JP2764046B2 (ja) * | 1988-12-13 | 1998-06-11 | 株式会社日阪製作所 | プレート式熱交換器 |
JP2560104B2 (ja) * | 1989-01-13 | 1996-12-04 | 清水建設株式会社 | 管内製氷ユニット及び管内製氷方法 |
US4936114A (en) * | 1989-06-23 | 1990-06-26 | Chicago Bridge & Iron Technical Services Company | Apparatus and method of freeze concentrating aqueous waste and process streams to separate water from precipitable salts |
US5139549A (en) * | 1991-04-05 | 1992-08-18 | Chicago Bridge & Iron Technical Services Company | Apparatus and method for cooling using aqueous ice slurry |
FR2716959B1 (fr) * | 1994-03-04 | 1996-05-15 | Thermique Generale Vinicole | Ensemble de distribution et/ou collection de froid et/ou de chaud. |
US5402650A (en) * | 1994-05-03 | 1995-04-04 | The Curators Of The University Of Missouri | Thermal storage composition for low energy ice harvesting, method of using same |
JPH09303916A (ja) * | 1996-05-14 | 1997-11-28 | Hoshizaki Electric Co Ltd | 水循環式製氷機 |
-
1999
- 1999-05-25 FR FR9906559A patent/FR2794228B1/fr not_active Expired - Fee Related
-
2000
- 2000-05-23 WO PCT/FR2000/001405 patent/WO2000071945A1/fr active IP Right Grant
- 2000-05-23 AT AT00931340T patent/ATE308021T1/de not_active IP Right Cessation
- 2000-05-23 EP EP00931340A patent/EP1101071B1/fr not_active Expired - Lifetime
- 2000-05-23 DE DE60023422T patent/DE60023422T2/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE60023422D1 (de) | 2005-12-01 |
WO2000071945A1 (fr) | 2000-11-30 |
FR2794228A1 (fr) | 2000-12-01 |
ATE308021T1 (de) | 2005-11-15 |
EP1101071A1 (fr) | 2001-05-23 |
FR2794228B1 (fr) | 2001-09-07 |
DE60023422T2 (de) | 2006-07-27 |
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