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WO1986000692A1 - Machine de fabrication de glace (modele i et modele ii) - Google Patents

Machine de fabrication de glace (modele i et modele ii) Download PDF

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Publication number
WO1986000692A1
WO1986000692A1 PCT/US1985/001345 US8501345W WO8600692A1 WO 1986000692 A1 WO1986000692 A1 WO 1986000692A1 US 8501345 W US8501345 W US 8501345W WO 8600692 A1 WO8600692 A1 WO 8600692A1
Authority
WO
WIPO (PCT)
Prior art keywords
ice
solution
container
making machine
water
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.)
Ceased
Application number
PCT/US1985/001345
Other languages
English (en)
Inventor
Vladimir Goldstein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sunwell Engineering Co Ltd
Original Assignee
Sunwell Engineering Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sunwell Engineering Co Ltd filed Critical Sunwell Engineering Co Ltd
Priority to BR8506853A priority Critical patent/BR8506853A/pt
Priority to KR1019860700151A priority patent/KR930008005B1/ko
Publication of WO1986000692A1 publication Critical patent/WO1986000692A1/fr
Priority to NO860979A priority patent/NO163304C/no
Priority to FI861076A priority patent/FI861076A7/fi
Priority to DK122586A priority patent/DK122586A/da
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F25C1/00—Producing ice
    • F25C1/12—Producing ice by freezing water on cooled surfaces, e.g. to form slabs
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25C1/00—Producing ice
    • 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
    • F28F19/008—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using scrapers
    • 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
    • F25C2301/00—Special arrangements or features for producing ice
    • F25C2301/002—Producing ice slurries

Definitions

  • ⁇ USS IT UT ⁇ SHEET passes therefrom to the centre area where larger harvestable water ice crystals grow. These larger water ice crystals are removed to yield a more concentrated brew.
  • ice making is not the end object but ice is a by-product. Concentration of the brew is the object of the method.
  • the method of Svanoe is a very delicately balanced method and operating conditions must be carefully controlled. It is important that ice crystals should not form on the sidewall of the container. This would stop the process. They must be directed to the centre of the container before they reach harvestable size. If the Svanoe method is capable of doing this at all it is capable of doing it under difficult to control conditions only and only at a rate that would not give any reasonable production of ice if the method were extended as a means of producing ice as a marketable end product.
  • the applicant scours differently from Svanoe and is able thereby to maintain a critical temperature range at the heat transfer surface to effectively avoid crystalization at the surface thereby increasing the ice making efficiency to a most remarkable extent.
  • Svanoe proposed the concept of subcooling the surface layer of liquid in the container and transferring it from the surface to the interior, but he did not know how to effectively put the concept into practice to get a hight yield, rtith Svanoe the subsurface layer is cooled substantially more than one degree below the freezing point and the formation of ice crystals at the cooling system is inevitable, rthen this occurs the system breaks down and the efficiency reverts to that of Spiegl where crystals are scraped from the container wall. Applicant avoids the inevitable breakdown of the system disclosed in Svanoe and is able to maintain a high rate of heat transfer and ice crystal production.
  • Scouring will permit one to operate the system without danger of forming ice crystals on
  • Figure 1 is a schematic illustration of apparatus for practising the invention.
  • Figure 2 is an illustration of a temperature concentration curve for a brine mixture-.
  • Figure 3 is a sectional view of a second embodiment of an ice making machine.
  • HT Figure 4 is a view on the line 4-4 of Figure 3.
  • Figure 5 is an exploded perspective view of the embodiment.
  • Figure 6 is a schematic illustration of a third embodiment of ice making machine.
  • the numeral 10 refers to a freezing cylinder. It has a dasher chamber 12 through which a brine mixture is continuously circulated by means of the pump 14. The brine mixture enters the chamber as at 16, is cooled therein to form ice crystals as will be referred to later and leaves the chamber from exit port 18 as a pumpable slush-like mixture. It then proceeds to a mechanical separator 20, which in the apparatus successfully operted to date consists of a strainer that holds the ice crystals and permits the liquid of the mixture to pass
  • ice crystals are removed and the remaining mixture is conducted to the circulation tank 22.
  • Water from the supply 24 is added to the circulation tank to replace the water taken from the brine mixture by removal of the ice crystals.
  • Numeral 23 is a tank containing concentrated solute which can be added to the system as required to replace lost solute.
  • a scouring paddle is continuously rotated by motor 26 to scour the sides of the chamber and prevent a build-up of ice on them.
  • the scouring paddle is of standard design on these machines.
  • the dasher chamber is surrounded by a jacket 28 to which a condensed refrigerant is continuously supplied from condensor 30.
  • the refrigerant boils in the jacket, and as it does so cools the brine mixture in the chamber to form ice crystals therein.
  • the expanded refrigerant travels from the jacket to the compressor 32 where it is compressed and delivered to the condensor for continuous recycling as in a conventional refrigeration cycle. As indicated, the freezer, dasher chamber.
  • # --• scouring paddle and associated refrigeration circuit are standard and well known pieces of equipment and detailed reference is not made to them.
  • Reference to Figure 2 will be made to explain the invention.
  • This figure illustrates well known characteristics of a brine mixture wherein the solvent is water and the solute is NaCl.
  • This solution will freeze at the eutectic temperature or temperature of eutectic indicated on the figure.
  • the hysical phenomena that occur as the temperature of such a solution is cooled towards the freezing point depends upon its concentration. If the concentration is represented by a point to the left of the point D, on the curve ice crystals are formed and the concentration of the solution increases as the freezing temperature is approached.
  • the temperature represented by points D on the curve is known as the eutectic temperature and the concentration represented by the point D, on the curve is known as the eutectic concentration.
  • concentration x a solution of concentration x, less than the eutectic, at a
  • salt instead of water freezes out as temperature lowers, and the concentration decreases until, at the eutectic temperature, eutectic concentration is reached.
  • salt sometimes freezes out because concentration is too high.
  • the ice and the concentration mixture form a pumpable slush-like composition which is forced into the separator. Water is added to the mixture that is returned to the dasher chamber of the freezer from the supply 24 to maintain the concentration of the mixture workable for the production of ice as it is cooled.
  • the cylinder 10 is an especially
  • the scouring paddle operates at a rate of speed that is fast enough to carry the cooled layer of mixture at the side wall towards the centre of the container before the cooled layer crystalizes on the side wall of the container.
  • the paddle tends to move the cooled surface layer in a spiral path towards the longitudinal central axis of the chamber- whereby it mixes with the general body of mixture in the chamber and cools
  • the transformation of water from the liquid to the crystal or solid state takes place suddenly and requires a very substantial amount of energy.
  • the liquid brine must be cooled below its freezing point before crystalization will take place. It is so cooled in a surface layer on the side of the chamber but in the interval before crystalization takes place the so cooled surface layer is moved by the rotating scouring paddle from the side wall of the container towards the centre of the container.
  • the cooled liquid thus removed from the side wall surface of the chamber crystalizes into ice on the centers of crystalization present in the liquid.
  • the brine acts as a secondary refrigerant in the formation of ice throughout the body of the mixture.
  • the paddles rotate around the heat exchange wall of the chamber and preferably form a scoop
  • the system is a very efficient one for forming ice and provides for maximum contact of the brine with the heat exchange surface of the chamber .
  • a typical heat exchange chamber having a diameter of three inches has a heat transf er coefficient between the brine and refrig erant of 500 BTU ' s per hour per square foot per degree Farenheit and the temperature diff erence between the refrigerant and the brine is 10 degrees Farenheit .
  • 0 .000024 01119 BTU ' s per ro tation of the blade per squa re foot .
  • To form ice requires 150 BTU ' s per pound of ice.
  • the diameter of the ice crystals harvested from the unit are between..002 and .003 inches. This is 154 to 384 times the thickness of ice that could be formed on the wall between scouring so that it is clear that with this rate of scouring crystals cannot grow to a harvestable size on the side wall of the heat exchanger. The 0.09 seconds that the brine contacts the wall is not sufficient for crystal formation.
  • the scouring rate will vary with equipment and capacity but in every case the idea is to scour at a rate that avoids cooling substantially below the freezing point at the surface and crystal growth on the side of the heat exchanger chamber whereby to promote crystal growth and formation throughout the body of the mixture.
  • the mechanical scouring of the surface will achieve a high scouring rate capable of preventing crystal growth on the container wall. It gives a good yield of ice crystals. It will be apparent that for a given piece of equipment the yield of ice crystals. It will be apparent that for a given piece of equipment the yield of ice will increase with temperature rate of heat transfer. If the rate of heat transfer from the container
  • BTU's per square foot per hour of container wall the method becomes insufficient.
  • High ice output for a given size piece of equipment is the key to successful operation.
  • Rates of heat transfer of between 4000 and 5000 BTU's per square foot per hour are contemplated. The higher the rate the more efficient the operation as to capacity.
  • the method disclosed in the Svanoe patent disclosed above is not capable of operation at these production rates. Svanoe would not remove ice formation from the wall at this rate.
  • This method further achieves a vast improvement in machine capacity over a method wherein the crystals are permitted to grown on the wall of the chamber and are then harvested by scraping them from the wall with a lower speed auger. With such a method the temperature of the bulk of the mixture is always substantially above freezing and formation of ice crystals takes place only on the limited area of the wall of the chamber. It is not possible to form ice crystals in the bulk of the mixture that is above freezing temperature. Further, the place of removal of the ice is
  • SUBSTITUTESHEET not critical. It would in the apparatus illustrated be strained in the cylinder and make up water added to the cylinder.
  • Solutions other than brine could be used.
  • the solvent should, of course, be water based to make ice but the solute could be any nontoxic material that has a suitable eutectic characteristic.
  • Substitutes for salt might be glycerine, propylene glycol, ethanol or calcium chloride.
  • the ice crystals grow throughout the liquid rather than from the wall outward in a layer. Crystals that form near the wall may attach themselves to the wall but they are removed from the wall as the blades rotate.
  • the growth throughout the liquid is achieved by prevention of larger build up at the cooled surface by mechanical scouring at a rate so that the temperature at the wall is not more than one degree centigrade below freezing point and is preferably no more than 0.2 degrees centigrade less than freezing point.
  • the foregoing example is of a subcooling of about 0.2 degrees centigrade.
  • the subcooling throughout the mixture cannot be more than this.
  • the unit with a chamber diameter of three inches and three feet in length referred to above has been operated according to this invention to produce 400 pounds of ice per hour.
  • Water is preferably added at a constant rate on a continuous basis but it can be added at intervals provided that the concentration of the brine does not get too high. If the concentration gets too high the process becomes less efficient and if it becomes so high that it passes the eutectic point salt will be deposited in the tank. As concentration gets high ice yield get low. If concentration is too low one gets too much ice for easy mechanical operation of the unit. Separation of ice from the slush can be done many ways including centrifugal.
  • the ice making machine 110 includes a housing 112 having upper and lower
  • the end plates 114, 116 are square when viewed in plan and cooperate with the side walls 118 to define an enclosed housing.
  • the housing 112 is preferably made from an insulated material to reduce the heat transfer across the walls 114, 116, 118.
  • An inlet 120 is provided on the upper plate 114 to receive the secondary refrigerant, and an outlet 122 is provided in the lower plate at a diametrically opposite location. Thus, fluid entering the inlet 120 is forced to traverse the housing 112 to reach the outlet 122.
  • An agitator shaft 124 extends through the housing 112 between the plates 114 and 116 and is rotatably supported at opposite ends by bearings 126, 128 located exteriorly of the housing.
  • the shaft 124 is driven by a motor 130 that is supported on the upper plate 114.
  • a pair of heat exchanger assemblies 132, 134 is located in the housing 112.
  • the heat exchanger assemblies extend between opposite peripheral walls 118 generally parallel to the end walls 114, 116 and normal to the axis of rotation of the shaft 124.
  • SUBSTITUTE SHEfi 132, 134 is formed with a central aperture 136,
  • the heat exchanger 132 is formed from a pair of spaced parallel plates 140,
  • the plates 140, 142 are maintained in spaced relationship by a honeycomb structure 144 that has open mesh partitions to permit the flow of fluid between the plates whilst maintaining a structural connection between them.
  • An inlet 146 is associated with each heat exchanger and passes through the side wall 118 of the housing.
  • an outlet 48 is provided so that coolant may flow from the inlet 146 through the honeycomb structure between the plates 140 and 142 to the outlet 148.
  • the space between the heat exchangers 132, 134 and the walls 118 is sealed by spacers 49 located in each corner of the housing 112.
  • An aperture 151 is provided in one of the spacers associated with each heat exchanger to permit flow of fluid from one side of the heat exchanger to the other. Successive apertures 51 are arranged
  • Each of the plates 140, 142 has an outwardly directed heat exchange surface 50 that contacts the fluid provided through the inlet 120.
  • an agitator assembly is connected to the shaft 124.
  • the agitator assembly consists of a series of disks 152, 154, 156 that are secured to the shaft 124 for rotation therewith.
  • the disk 152 is located between the heat exchanger 132 and the upper end plate 114; the disk 154 is located between the two heat exchangers 132, 134 and the lower disk 156 is located between the heat exchanger 134 and the lower end plate 116.
  • each of the disks 152 toward a respective one of the surfaces 150 Extending from each of the disks 152 toward a respective one of the surfaces 150 is a pair of blades 158.
  • the blades 158 are pivotally connected to the disk 152 by a hinge 157 and in the operative position are inclined to the plane of the disk.
  • the blades 158 terminate in a bevelled edge 160 that is in a scraping relationship with the surface 150.
  • SUBSTITUTESH5ET are generally rectangular in shape and are accommodated in a rectangular slot 159 in the surface of the disk.
  • the blades 158 are biased into engagement with the surface 150 by flow of fluid past the blades up in rotation of the shaft 124.
  • Resilient biasing means such as torsion springs may be incorporated into the hinge 157 to bias the blades toward the respective surface 150.
  • the disks 152, 156 each carry a pair of blades 158 directed to the upper heat exchange surface 150 of the heat exchanger 132 and lower heat exchanger surface 150 of the heat exchanger 134 respectively.
  • the disk 154 carries two pairs of blades 158, one pair directed to the undersurface of the heat exchanger 132 ana the other pair directed to the upper heat exchange surface 150 of the heat exchange 134. Each pair of blades is aligned on a diameter of the disk with the two pairs disposed at 90° to one another.
  • brine is fed to the inlet 120 and circulates through the housing 112, around the heat exchangers 132, 134 through the apertures 151 to the outlet 122.
  • the primary refrigerant usually freon
  • freon is introduced through the inlet 146 of each of the heat exchangers 132, 134 from the condenser 30 where it flows through the heat exchanger to the outlet 44.
  • freon passes through the heat exchanger it absorbs heat through the heat exchange surfaces 150 and boils.
  • the brine in contact with the heat exchange surfaces is thus supercooled.
  • the agitator assembly is rotated by the shaft 124. Rotation of tne shaft 124 rotates the disk 152 and thereby sweeps the blades 158 over their respective heat exchange surfaces 150. The movement of the blades removes the super cooled brine from adjacent the surfaces 150 and distributes it through the body of the brine solution.
  • the super cooled brine will crystalise on centers of crystallisation present in the solution and in turn act as new centres of crystallisation to generate three dimensional crystallisation of the water within the brine solution and thus promote the formation of ice in a crystalline manner.
  • the brine solution with the crystallized ice in suspension is extracted from
  • the outlet 122 where it may be passed to a separating tower (20) for removal of the balance of the brine solution and conveyed to a storage device or directly to the induce for the ice or directed to the thermal storage heat exchanger 52.
  • the disposition of the heat exchangers in a plane normal to the axis of rotation of the shaft 124 facilitates the modular .expansion of the ice making machine for increased capacity without imposing significant additional structural loads upon the apparatus.
  • the plates 50 would typically be between 3/8 - 1 inch thick to provide good heat transfer between the coolant and the brine solution with the honeycomb partitions 144 providing the required strength.
  • the shaft 124 will be rotated at 150-400 rpm with a throughput of 9-18 gallons per minute.
  • the surfaces 150 may be coated with a release agent to inhibit the deposition of ice on the surface.
  • a release agent may typically be polytetrafluoroethylene, or a silicone water
  • SUBSTITUTE SHEET repellant liquid such as Dow Comings Latex
  • Silicone 804 or Silicone 890 may be painted and baked on in accordance with the normal use of such coatings. If coatings are utilised then the blades 158 may act as wipers rather than scrapers as the coating will in itself discourage the deposition of the crystals.
  • the blades 158 may be supported on any convenient carrier assembly connected to the shaft 124, such as a spider arrangement, rather than the discs 152, 154, 156.
  • the plates 140, 142 may be maintained in spaced relationship by studs extending between and normal to the plates 140, 142. Whilst the additional surface area provided by the honeycomb portion 44 is considered beneficial, satisfactory results may be obtained by utilising the studs and a coating on the interior of the plates to promote heat transfer. Such a coating is available from Union Carbide under the trade name High Flux coating.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Physical Water Treatments (AREA)
  • Confectionery (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Soil Working Implements (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Abstract

Une machine de fabrication de glace comporte un boîtier (112) doté d'une paroi refroidie (140, 142). Un mélange eutectique traverse la paroi (140, 142) afin d'être refroidi en dessous de son point de congélation et de former de la glace. Une lame (158) balaie continuellement la paroi afin d'écarter le fluide de la paroi et de le faire pénétrer dans le corps du fluide. Les lames sont déplacées par un mécanisme d'entraînement (130) à une vitesse telle que la surface est balayée avant la cristallisation de la glace sur la paroi.
PCT/US1985/001345 1984-07-17 1985-07-17 Machine de fabrication de glace (modele i et modele ii) Ceased WO1986000692A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
BR8506853A BR8506853A (pt) 1984-07-17 1985-07-17 Maquina produtora de gelo,processo continuo para producao de cristais de gelo e processo de formacao continua de gelo
KR1019860700151A KR930008005B1 (ko) 1984-07-17 1985-07-17 "제빙기(마크 ⅰ과 ⅱ)"
NO860979A NO163304C (no) 1984-07-17 1986-03-14 Isfremstillingsmaskin
FI861076A FI861076A7 (fi) 1984-07-17 1986-03-14 Istillverkningsmaskin.
DK122586A DK122586A (da) 1984-07-17 1986-03-17 Apparat og fremgangmaade til fremstilling af is

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US63195284A 1984-07-17 1984-07-17
US631,952 1984-07-17
US73922585A 1985-05-30 1985-05-30
US739,225 1985-05-30

Publications (1)

Publication Number Publication Date
WO1986000692A1 true WO1986000692A1 (fr) 1986-01-30

Family

ID=27091508

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1985/001345 Ceased WO1986000692A1 (fr) 1984-07-17 1985-07-17 Machine de fabrication de glace (modele i et modele ii)

Country Status (7)

Country Link
KR (1) KR930008005B1 (fr)
AU (1) AU583051B2 (fr)
BR (1) BR8506853A (fr)
DK (1) DK122586A (fr)
FI (1) FI861076A7 (fr)
NO (1) NO163304C (fr)
WO (1) WO1986000692A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0257936A3 (en) * 1986-08-19 1988-09-21 Sunwell Engineering Company Limited Corrugated plate heat exchanger
EP0382730B1 (fr) * 1987-07-20 1993-03-10 Sunwell Engineering Company Limited Procede et appareil permettant de refrigerer des poissons a bord d'un bateau
FR2872269A1 (fr) * 2004-06-29 2005-12-30 Lgl France Sa Dispositif d'echange de chaleur pour machine de production de froid
FR2914409A1 (fr) * 2007-03-26 2008-10-03 Bousquet Adrien Laude Disque refrigerant pour installation de stockage et de regeneration d'un fluide frigo-porteur
CN100582609C (zh) * 2006-12-20 2010-01-20 南通四方冷热机械设备有限公司 引射泵供液立筒式制冰机
US9267741B2 (en) 2004-06-23 2016-02-23 Icegen Patent Corp. Heat exchanger for use in cooling liquids

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1641429A (en) * 1922-05-05 1927-09-06 Wilbert A Heyman Continuous-freezing apparatus
US2259841A (en) * 1941-10-21 Refrigerant and method of provdj
US2507632A (en) * 1944-11-30 1950-05-16 Eastman Kodak Co Process for dehydrating materials under low-pressure conditions
US3191398A (en) * 1962-12-07 1965-06-29 Mueller Brass Co Apparatus for congealing liquids having a moving scraper
US3328972A (en) * 1966-08-09 1967-07-04 Struthers Scientific Int Corp Concentration of extracts by freezing
US3339372A (en) * 1964-08-13 1967-09-05 Phillips Petroleum Co Fractional crystallization
US3347058A (en) * 1966-06-21 1967-10-17 Struthers Scientific Int Corp Concentration of extracts by freezing
US3488974A (en) * 1965-01-04 1970-01-13 Carrier Corp Water purifying apparatus
US4059047A (en) * 1975-08-13 1977-11-22 Sollich Kg Conditioning machine for chocolate masses

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB736186A (en) * 1953-07-24 1955-09-07 Ohio Commw Eng Co Improvements in or relating to a method and apparatus for dehydrating liquid compositions containing water

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2259841A (en) * 1941-10-21 Refrigerant and method of provdj
US1641429A (en) * 1922-05-05 1927-09-06 Wilbert A Heyman Continuous-freezing apparatus
US2507632A (en) * 1944-11-30 1950-05-16 Eastman Kodak Co Process for dehydrating materials under low-pressure conditions
US3191398A (en) * 1962-12-07 1965-06-29 Mueller Brass Co Apparatus for congealing liquids having a moving scraper
US3339372A (en) * 1964-08-13 1967-09-05 Phillips Petroleum Co Fractional crystallization
US3488974A (en) * 1965-01-04 1970-01-13 Carrier Corp Water purifying apparatus
US3347058A (en) * 1966-06-21 1967-10-17 Struthers Scientific Int Corp Concentration of extracts by freezing
US3328972A (en) * 1966-08-09 1967-07-04 Struthers Scientific Int Corp Concentration of extracts by freezing
US4059047A (en) * 1975-08-13 1977-11-22 Sollich Kg Conditioning machine for chocolate masses

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0257936A3 (en) * 1986-08-19 1988-09-21 Sunwell Engineering Company Limited Corrugated plate heat exchanger
EP0382730B1 (fr) * 1987-07-20 1993-03-10 Sunwell Engineering Company Limited Procede et appareil permettant de refrigerer des poissons a bord d'un bateau
US9267741B2 (en) 2004-06-23 2016-02-23 Icegen Patent Corp. Heat exchanger for use in cooling liquids
US9995521B2 (en) 2004-06-23 2018-06-12 Icegen Patent Corp. Heat exchanger for use in cooling liquids
US11566830B2 (en) 2004-06-23 2023-01-31 Icegen Patent Corp. Heat exchanger for use in cooling liquids
FR2872269A1 (fr) * 2004-06-29 2005-12-30 Lgl France Sa Dispositif d'echange de chaleur pour machine de production de froid
WO2006010854A1 (fr) * 2004-06-29 2006-02-02 Lgl France Dispositif d'echange de chaleur pour machine de production de froid
CN100582609C (zh) * 2006-12-20 2010-01-20 南通四方冷热机械设备有限公司 引射泵供液立筒式制冰机
FR2914409A1 (fr) * 2007-03-26 2008-10-03 Bousquet Adrien Laude Disque refrigerant pour installation de stockage et de regeneration d'un fluide frigo-porteur
WO2008129176A3 (fr) * 2007-03-26 2009-02-19 Bousquet Adrien Laude Disque réfrigérant pour installation de stockage et de régénération d'un fluide frigo-porteur

Also Published As

Publication number Publication date
DK122586D0 (da) 1986-03-17
KR930008005B1 (ko) 1993-08-25
DK122586A (da) 1986-03-17
NO163304C (no) 1996-04-23
AU583051B2 (en) 1989-04-20
KR860700287A (ko) 1986-08-01
NO860979L (no) 1986-04-25
FI861076A0 (fi) 1986-03-14
AU4722885A (en) 1986-02-10
NO163304B (no) 1990-01-22
FI861076A7 (fi) 1986-03-14
BR8506853A (pt) 1986-09-23

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