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US3822566A - Portable utility system - Google Patents

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US3822566A
US3822566A US00271457A US27145772A US3822566A US 3822566 A US3822566 A US 3822566A US 00271457 A US00271457 A US 00271457A US 27145772 A US27145772 A US 27145772A US 3822566 A US3822566 A US 3822566A
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tube
evaporator
seawater
refrigerant
condenser
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A Lowi
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/022Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/14Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically both tubes being bent
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05Compression system with heat exchange between particular parts of the system
    • F25B2400/051Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05Compression system with heat exchange between particular parts of the system
    • F25B2400/052Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle

Definitions

  • ABSTRACT A portable utility system particularly useful for drastically cooling seawater and/or forming an ice/brine slurry for application to fish.
  • a tube-in-tube evaporator is provided for cooling the seawater while it is drawn into the evaporator by means of a positive displacement brine pump.
  • Seawater is drawn into a tubein-tube condenser by a coolant pump to remove heat from the system refrigerant and is continuously discharged after it is passed through the condenser coils.
  • a compressor is provided to raise the pressure and temperature of the gaseous refrigerant.
  • a reversible valve enables the flow of refrigerant through the system to be reversed, producing hot water at the output of the evaporator, when desired.
  • the evaporator is formed of a first tube for conveying refrigerant and a second tube positioned in heat exchange relation within the first tube, the second tube conveying seawater to be refrigerated.
  • the condenser may also be formed of a tube within a tube wherein the refrigerant is conveyed in the inner tube and the cooling seawater is conveyed in the outer tube.
  • An in-1ine dispenser for bacteriostatic agents, or the like, can be provided.
  • the system can supply electrical as well as hydraulic needs and can be used onshore with air cooling in place of water cooling. 1
  • Typical fishing boats without refrigeration can keep their catch on the boat for up to a maximum of 24 hours. Thus, fish caught early in the trip may spoil be fore a full load has been caught.
  • Custom refrigeration systems for such fishing boats have been relatively expensive, often costing more than the market value of the'boat itself.
  • the use of the customrefrigeration systerns has been limited to shrimp boats of greater than .60 feet in length and this guideline has only been found acceptable in recent years, as the price of shrimp has greatly increased.
  • inexpensive refrigeration systemscould substantially boost the yield for a fishing boat by increasing the amount of marketable fish and, by preserving quality, assuring a higher price per pound of fish at the time of sale.
  • the present invention provides an economical, portable source of refrigeration suitable for use in commercial fishing operations by small craft.
  • the refrigeration system can also be used on large boats andshore facilities and requires only seawater and ordinary motor fuel for its operation. Refrigeration occurs by the direct contact of the seafood with a stream of refrigerated seawater or an ice/brine slurry.
  • An advantage of the system is that immediate chilling of the fish occurs, which is superior to ice or other conventional refrigeration methods.
  • the refrigerated seawater is lowered to about 31-39F, thereby reducing spoilage from enzymatic attack and suppressing the activity of mesophillic bacteria of these waters which are substantially dormant at temperatures below 50F.
  • the system is designed to produce ice/brine slurrys, without additional salt requirement, from recycled refrigerated seawater at temperatures as low as 15F.
  • the system thus has the capability of freezing aswell as chillingthe fish.
  • the refrigeration system is designed to produce an ice/ brine slurry by taking advantage of the fact that seawater has no definite freezing point. Due to its dissolved minerals, the seawater does not solidify at once, but forms ice (fresh water) crystals suspended in the residual brine as its temperature is reduced, the first crystals being formed at about 29F. With further reduction of temperature, more and more crystals form, taking water out of the solution and leaving a brine of higher and higher salt content as the matrix. The slurry of ice crystals and brine becomes more and more vis- 4
  • the pump is of a positive displacement configuration so that ice crystals are pushed through a tube by increasing pressure as the ice/brine slurry becomes more viscous.
  • the evaporator of the system is formed of a first tube for conveying a refrigerant and a second tube member positionedwithin the first tube member through which the seawater is pumped.
  • a pump is provided forcontinuouslly dischargingwater through a condenser so as, to remove heat from the compressed refrigerant.
  • the condenser is also constructed tube-in-tube. Cooling seawater passes-through the inner tube, Heat is removed from the condenser by seawater in the outer tube.
  • a reversible valve is provided for reversing the flow of refrigerant through the system, thereby producing hot water at the output of the evaporator.
  • the engine constituting the pump motor can be used to provide electrical power withappropriate takeofis.
  • the ice slurry capability can be used to provide drinking water by the freezing method of desalination. Hot water can be provided as noted above. Accordingly, a complete utility ered in connection with the accompanying drawing in whichlike referenced numerals designate like parts throughout the figures.
  • FIG. 1 is a schematic illustration of a refrigeration system made in accordance with the present invention.
  • FIG. 2 is a detailed view, partly in section, of the evaporator utilized in the refrigeration system of FIG.
  • the refrigeration system comprises a motor 12 which normally may be air-cooled and can be conveniently mounted on a deck of a, small boat.
  • the motor 12 can be a fossil, and fuel internal combustion engine, such as spark ignition or diesel can be electrically or hydraulically driven or driven by a belt driving mechanism.
  • the motor 12 is used to drive a shaft 14 having a pulley l6 thereon.
  • the shaft 14 in addition is connected through a clutch member 18 to a compressor 22 and is used to drive the compressor 22.
  • the compressor 22 comprises a suction input section 24 and discharge output section 26.
  • the pulley 16 has a belt 28 thereon which is used to drive a second pulley 32.
  • the pulley 32 is mounted on a shaft 34 which is used to drive a brine pump 36 and also is connected through a coupling 38 to a coolant pump 42.
  • the brine and coolant pumps 36 and 42 can be tandemly disposed on the same shaft and/or driven off the same belt as the compressor.
  • the refrigeration system is normally utilized to chill seawater or if desired, to recycle the chilled seawater, reducing the temperature of the seawater sufficiently that a slurry is produced.
  • Seawater is positively drawn into the refrigeration system by means of the brine pump 36 through a strainer 44.
  • the suction prime of the seawater to the pumps is maintained by a check valve 45 once operation is established in order to avoid dry sucking by the pumps.
  • the strainer 44 prevents gross entrained solids in the seawater from entering the system.
  • the seawater is pumped through a tube 46 by the brine pump 36 into the evaporator 48 of the refrigeration system.
  • the chilled seawater emerges from the evaporator 48 through a hose outlet 52 where it can be used as desired.
  • the outlet 52 can be connected, to a treating tank which, in turn, is connected through a valve to the inlet of the brine pump strainer.
  • Other means of distributing the flow can be used such as high velocity spray, fog, and the like.
  • Liquid refrigerant which may be any conventional refrigerant such as any common halogenated hydrocarbon refrigerant, e.g., Freon, leaves a capillary expansion tube 64 and enters the evaporator 48 through a line 54 where it boils at a low temperature to produce cooling and emerges therefrom into an output refrigerant line 56.
  • the refrigerant is then conveyed through a reversing valve 58 into a line 60 and then to an accumulator vessel 62 as shownby the arrows.
  • Such heat transfer causes the vaporization of any remaining refrigerant liquid trapped in the accumulator providing protection to the compressor 22 from liquid entrainment.
  • the heat transfer also provides a high degree of thermal efficiency by recovering unused refrigeration affect from the unevaporated refrigerant leaving the evaporator (recuperation).
  • the refrigerant vapor in the accumulator 62 is then conveyed by line 66 to the suction end 24 of the compressor 22 where the pressure and temperature of the gaseous refrigerant is raised.
  • the refrigerant is dischargedfrom the discharge end 26 of the compressor to the reversing valve 58 and then passes through a line 72 and then through a condenser 74.
  • seawater is carried through a strainer 76 by means of the coolant pump 42 and passes from the coolant pump through a line 78 through the condenser 74.
  • the cooling water is emitted from the condenser through a line 80 and is then discharged overboard.
  • the strainer 76 and check valve 82 are similar to the strainer 44 and check valve 45 and functions with the coolant pump 42 in a manner identical to that described with respect to the brine pump 36.
  • the functions of the brine pump and the coolant pump can be combined with appropriate valving so as to provide sufficient seawater for both cooling the condenser and providing input seawater to the evaporator.
  • the output liquid refrigerant from the condenser is conveyed through a strainer-dryer 84 and is then conveyed through the capillary tube 64.
  • the refrigerant in the capillary tube 64 is then conveyed to a second strainer-dryer 86 which provides the same function as the strainer-dryer 84 during reverse operation as will be explainer hereinafter.
  • the output of the strainer-dryer 86 is then connected to the refrigerant line 54 at the input of the evaporator 48.
  • the refrigerant cycle is completed and the desired chilled seawater is produced at line 52.
  • the refrigerant then passes through the capillary expansion tube 64, the strainer-dryer 84, condenser 74, line 72, line 90 of valve 58, line 60, the suction accumulator 62 and then enters the suction end 24 of the compressor 22.
  • the system can be used to produce hot water rather than chilled water, when such is desired.
  • An ice/brine slurry can be provided by recycling the chilled water at the output 52. This can be accomplished by reconveying the chilled seawater through the brine pump 36 as shown by dashed line 92. This provides the capability of adjusting the output temperature while preserving the monotube positive displacement character of the system. Thus, the resultant recycling can reduce the temperature of the slurry at the output of the hose 52 to 15F. Thus, the capability of continuously freezing seawater is provided.
  • any ice crystals formed in the single line 46 or in the monotube section of the evaporator connected to the line 46 are pushed therethrough by the increasing pressure applied by the pump as the seawater becomes more viscous or as the tube becomes restricted.
  • the monotube evaporator design coupled with the positive displacement brine pump creates an increasing shearing action at any spot where local build-up of ice scale would occur, thereby keeping the tube free-flowing, the ice/- brine slurrywell mixed and the ice crystals extremely fine in texture.
  • the evaporator 48 is shown a preferred embodiment of the evaporator 48.utilized in the construction of the refrigeration system of FIG. 1.
  • the evaporator 48 comprises an inner coiled tube 102, one end of which is connected to the output line 52. Surrounding the coiled line 102 in an outer coiled line 104,
  • the line 102 is formed of a it; inch outer diameter tube of about 50 feet in length, and the tube 104 surrounding the tube 102 is fonned with a 5 1 inch outer diameter.
  • Such a coiled tube-within-a-tube construction efficiently produces chilled seawater having a temperature in the range of 29-39F, and an ice/slurry when recycled as above.
  • the condenser 74 may be constructed in a manner similar to the evaporator 48 wherein an inner tube containing the seawater is surrounded by an outer tube containing the refrigerant which is cooled and condensed as it passes in annular countercurrent flow arrangement with the seawater in the inner tube. Coiling of the tubes as illustrated results in an advantageous economy of space and portability.
  • the evaporator and condenser coils can be nested one within the other, permitting compact enclosure which facilitates sliding, skidding and other handling and installation of the unit.
  • the enclosure can be made as a Water-proof hull for flotation on the surf and between boats at sea.
  • a hold tank 55 which may be in the form of a container, pressure vessel, flexible feed bag, drum or the like, and which is connected into the I brine pump strainer 44 through a valve 59 as shown or ity system for converting seawater into refrigerated seawater, comprising:
  • an evaporator for lowering the temperature of seawater said evaporator comprising an outer coiled evaporator tube and an inner coiled evaporator tube within and coextensive with said outer evaporator tube and having a discharge end extending therefrom;
  • a refrigerant condenser comprising an outer coiled condenser tube and an inner coiled condenser tube within and coextensive with said outer condenser tube and having a discharge end extending therefrom;
  • refrigerant tube means for. connecting said outer evaporater and condensure tubes constituting with said outer tubes a refrigerant line;
  • compressor means connected to said refrigerant line for circulating refrigerant therethrough and driven by said single drive means;
  • means for pumping seawater through said inner evaporator and condenser tubes comprising at least one positive displacement-pump, and strainer means therefor, connected to said inner evaporator and condenser tubes and driven by said single drive means, whereby to provide cooled seawater discharge from said inner evaporator tube discharge end and heated seawater discharge from said inner condenser tube discharge end;
  • valve means for reversing the flow of refrigerant through said refrigerant line whereby to produce hot water at the discharge encl of said inner evaporator tube.

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  • Engineering & Computer Science (AREA)
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  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
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  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

A portable utility system particularly useful for drastically cooling seawater and/or forming an ice/brine slurry for application to fish. A tube-in-tube evaporator is provided for cooling the seawater while it is drawn into the evaporator by means of a positive displacement brine pump. Seawater is drawn into a tube-in-tube condenser by a coolant pump to remove heat from the system refrigerant and is continuously discharged after it is passed through the condenser coils. A compressor is provided to raise the pressure and temperature of the gaseous refrigerant. A reversible valve enables the flow of refrigerant through the system to be reversed, producing hot water at the output of the evaporator, when desired. The evaporator is formed of a first tube for conveying refrigerant and a second tube positioned in heat exchange relation within the first tube, the second tube conveying seawater to be refrigerated. The condenser may also be formed of a tube within a tube wherein the refrigerant is conveyed in the inner tube and the cooling seawater is conveyed in the outer tube. An in-line dispenser for bacteriostatic agents, or the like, can be provided. The system can supply electrical as well as hydraulic needs and can be used onshore with air cooling in place of water cooling.

Description

United States Patent [191 Lowi, Jr.
'61] 3,822,566 [451 July 9,1974
[ PORTABLE UTILITY SYSTEM [76] Inventor: I
San Pedro, Calif. 90732 [22] Filed: July 13, 1972 [21] Appl. No.: 271,457
[52] US. or. ..62/435,62/325,62/324, 62/240, 62/64, 62/78, 62/98, 62/99, 62/439 51 Int. Cl F25d 17/02 [58] Field of Search 62/324, 240, 435, 98, 99, 62/64, 185, 201, 325
[56] References Cited UNITED STATES PATENTS 1,712,568 5/1929 Kritzer 62/185 2,136,813 11/1938 Dobson 62/98 2,299,188 10/1942 Stork 62/99 2,511,582 6/1950 Grindrod 62/98 2,513,373 7/1950 Sporn 62/324 2,596,195 5/1952 Arbuckle 62/435 2,620,635 12/1952 lnautner 62/185 2,746,272 5/1956 Carpenter 62/240 2,966,779 1/1961 Lintern 62/240 3,540,229 1 H1970 Bunten 62/240 SOCT/ON PUMP Alvin Lowi, Jr., 2146 Toscanini Dr,
[57 ABSTRACT A portable utility system particularly useful for drastically cooling seawater and/or forming an ice/brine slurry for application to fish. A tube-in-tube evaporator is provided for cooling the seawater while it is drawn into the evaporator by means of a positive displacement brine pump. Seawater is drawn into a tubein-tube condenser by a coolant pump to remove heat from the system refrigerant and is continuously discharged after it is passed through the condenser coils. A compressor is provided to raise the pressure and temperature of the gaseous refrigerant. A reversible valve enables the flow of refrigerant through the system to be reversed, producing hot water at the output of the evaporator, when desired. The evaporator is formed of a first tube for conveying refrigerant and a second tube positioned in heat exchange relation within the first tube, the second tube conveying seawater to be refrigerated. The condenser may also be formed of a tube within a tube wherein the refrigerant is conveyed in the inner tube and the cooling seawater is conveyed in the outer tube. An in-1ine dispenser for bacteriostatic agents, or the like, can be provided. The system can supply electrical as well as hydraulic needs and can be used onshore with air cooling in place of water cooling. 1
4 Claims, 2 Drawing Figures 1 PORTABLE UTILITY SYSTEM FIELD OF THE INVENTION BACKGROUND AND SUMMARY OF THE INVENTION The principal sources of commercial marketable sea food in the world today are remote in time and distance from their ultimate consumers. Unlike meat products, such as beef, which are actually improved with aging, seafood is highly perishable. Fish begin to deteriorate as soon as caught and immediate refrigeration is the only known way to preserve the original quality of the fish. Much of the worlds high quality seafood is taken in warm tropical waters by small craft which typically have no refrigeration system at all or, at best, utilize ice. Therefore, a significant percentage of the fish catch spoils before it can reach processing facilities. It is not uncommon for such spoilage to amount to more than half the value of the catch. Thus preservation and quality control are the fundamental obstacles confronting the advancement of commercialfishing in much of the world today. 1
The changing technology of fishing actually favor the use of small boats in many areas where new commercial fisheries are being developed. Moreover,there is a growing tendency for largeseafood companies to establish canning and processing plants in underdeveloped areas of the'world and to buy fish from native fisherman.
Typical fishing boats without refrigeration can keep their catch on the boat for up to a maximum of 24 hours. Thus, fish caught early in the trip may spoil be fore a full load has been caught. Custom refrigeration systems for such fishing boats have been relatively expensive, often costing more than the market value of the'boat itself. The use of the customrefrigeration systerns has been limited to shrimp boats of greater than .60 feet in length and this guideline has only been found acceptable in recent years, as the price of shrimp has greatly increased. Thus, inexpensive refrigeration systemscould substantially boost the yield for a fishing boat by increasing the amount of marketable fish and, by preserving quality, assuring a higher price per pound of fish at the time of sale.
Prior art'devices which utilize chilled seawater are relatively complex and expensive. In addition, these refrigeration systems are not readily repaired by a fishing crew while the boat is at sea. Typical systems which involved the spraying of fish for refrigeration purposes include US. Pat. Nos. 2,746,272, 2,982,109 and, 3,162,020. Also of interest with respect to the cooling and heating functions of a refrigeration system are US. Pat. Nos. 2,887,853, 3,308,877 and 3,453,840. Additional patents which are of background and environmental interest include US. Pat. Nos. 1,322,312, 1,192,896, 2,863,037, 2,909,040 and 3,309,891.
In order to overcome the disadvantages of priorart refrigeration systems, the present invention provides an economical, portable source of refrigeration suitable for use in commercial fishing operations by small craft. a
In addition, the refrigeration system can also be used on large boats andshore facilities and requires only seawater and ordinary motor fuel for its operation. Refrigeration occurs by the direct contact of the seafood with a stream of refrigerated seawater or an ice/brine slurry. An advantage of the system is that immediate chilling of the fish occurs, which is superior to ice or other conventional refrigeration methods. When utilized with fish caught from warm ocean water, the refrigerated seawater is lowered to about 31-39F, thereby reducing spoilage from enzymatic attack and suppressing the activity of mesophillic bacteria of these waters which are substantially dormant at temperatures below 50F. In addition, cold water fish may spoil from psychrophillic bacterial attack at temperatures as low as 19F Thus, for application with cold water fishing vessels the system is designed to produce ice/brine slurrys, without additional salt requirement, from recycled refrigerated seawater at temperatures as low as 15F. The system thus has the capability of freezing aswell as chillingthe fish. a
The refrigeration system is designed to produce an ice/ brine slurry by taking advantage of the fact that seawater has no definite freezing point. Due to its dissolved minerals, the seawater does not solidify at once, but forms ice (fresh water) crystals suspended in the residual brine as its temperature is reduced, the first crystals being formed at about 29F. With further reduction of temperature, more and more crystals form, taking water out of the solution and leaving a brine of higher and higher salt content as the matrix. The slurry of ice crystals and brine becomes more and more vis- 4 The pump is of a positive displacement configuration so that ice crystals are pushed through a tube by increasing pressure as the ice/brine slurry becomes more viscous. The evaporator of the systemis formed of a first tube for conveying a refrigerant and a second tube member positionedwithin the first tube member through which the seawater is pumped. In addition, a pump is provided forcontinuouslly dischargingwater through a condenser so as, to remove heat from the compressed refrigerant. The condenser is also constructed tube-in-tube. Cooling seawater passes-through the inner tube, Heat is removed from the condenser by seawater in the outer tube.
In a further embodiment, a reversible valve is provided for reversing the flow of refrigerant through the system, thereby producing hot water at the output of the evaporator.
As a result of providing the novel portable refrigeration capability, as outlined above, small boats will be able to remain in the fishery for much longer periods of time. As a consequence, greater need will exist for supportive utilities suchas electrical power, hot cleaning water, drinking water, bilge pumping and other water transport capability. The system described herein.
also provides these utilities. Thus, the engine constituting the pump motor can be used to provide electrical power withappropriate takeofis. The ice slurry capability can be used to provide drinking water by the freezing method of desalination. Hot water can be provided as noted above. Accordingly, a complete utility ered in connection with the accompanying drawing in whichlike referenced numerals designate like parts throughout the figures.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic illustration of a refrigeration system made in accordance with the present invention; and
FIG. 2 is a detailed view, partly in section, of the evaporator utilized in the refrigeration system of FIG.
DETAILED DESCRIPTION Referring to FIG. 1, there is shown an exemplary embodiment of the refrigeration system made in accordance with principles of the invention. The refrigeration system comprises a motor 12 which normally may be air-cooled and can be conveniently mounted on a deck of a, small boat. The motor 12 can be a fossil, and fuel internal combustion engine, such as spark ignition or diesel can be electrically or hydraulically driven or driven by a belt driving mechanism. The motor 12 is used to drive a shaft 14 having a pulley l6 thereon. The shaft 14 in addition is connected through a clutch member 18 to a compressor 22 and is used to drive the compressor 22. The compressor 22 comprises a suction input section 24 and discharge output section 26. The pulley 16 has a belt 28 thereon which is used to drive a second pulley 32. The pulley 32 is mounted on a shaft 34 which is used to drive a brine pump 36 and also is connected through a coupling 38 to a coolant pump 42. Alternatively the brine and coolant pumps 36 and 42 can be tandemly disposed on the same shaft and/or driven off the same belt as the compressor. The refrigeration system is normally utilized to chill seawater or if desired, to recycle the chilled seawater, reducing the temperature of the seawater sufficiently that a slurry is produced.
Seawater is positively drawn into the refrigeration system by means of the brine pump 36 through a strainer 44. Normally, the suction prime of the seawater to the pumps is maintained by a check valve 45 once operation is established in order to avoid dry sucking by the pumps. The strainer 44 prevents gross entrained solids in the seawater from entering the system. The seawater is pumped through a tube 46 by the brine pump 36 into the evaporator 48 of the refrigeration system. The chilled seawater emerges from the evaporator 48 through a hose outlet 52 where it can be used as desired. Thus, (not shown) the outlet 52 can be connected, to a treating tank which, in turn, is connected through a valve to the inlet of the brine pump strainer. Other means of distributing the flow can be used such as high velocity spray, fog, and the like.
Liquid refrigerant, which may be any conventional refrigerant such as any common halogenated hydrocarbon refrigerant, e.g., Freon, leaves a capillary expansion tube 64 and enters the evaporator 48 through a line 54 where it boils at a low temperature to produce cooling and emerges therefrom into an output refrigerant line 56. The refrigerant is then conveyed through a reversing valve 58 into a line 60 and then to an accumulator vessel 62 as shownby the arrows. At the accumulator 62, heat from the liquid refrigerant flowing in the capillary tube 64 contacts the accumulator 62 at a point upstream from the line 54, flows through the vessel wall and into the refrigerant vapor leaving the evaporator 48. Such heat transfer causes the vaporization of any remaining refrigerant liquid trapped in the accumulator providing protection to the compressor 22 from liquid entrainment. The heat transfer also provides a high degree of thermal efficiency by recovering unused refrigeration affect from the unevaporated refrigerant leaving the evaporator (recuperation).
The refrigerant vapor in the accumulator 62 is then conveyed by line 66 to the suction end 24 of the compressor 22 where the pressure and temperature of the gaseous refrigerant is raised. The refrigerant is dischargedfrom the discharge end 26 of the compressor to the reversing valve 58 and then passes through a line 72 and then through a condenser 74. To expediteremoval of heat fromthe refrigerant at the condenser stage, seawater is carried through a strainer 76 by means of the coolant pump 42 and passes from the coolant pump through a line 78 through the condenser 74. The cooling water is emitted from the condenser through a line 80 and is then discharged overboard.
The strainer 76 and check valve 82 are similar to the strainer 44 and check valve 45 and functions with the coolant pump 42 in a manner identical to that described with respect to the brine pump 36. The functions of the brine pump and the coolant pump can be combined with appropriate valving so as to provide sufficient seawater for both cooling the condenser and providing input seawater to the evaporator.
The output liquid refrigerant from the condenser is conveyed through a strainer-dryer 84 and is then conveyed through the capillary tube 64. The refrigerant in the capillary tube 64 is then conveyed to a second strainer-dryer 86 which provides the same function as the strainer-dryer 84 during reverse operation as will be explainer hereinafter. The output of the strainer-dryer 86 is then connected to the refrigerant line 54 at the input of the evaporator 48. Thus, the refrigerant cycle is completed and the desired chilled seawater is produced at line 52.
Should it be desired to produce hot water at the output line 52, it is merely necessary to reverse the connections of the valve 58 so as to reverse the flow of the referigerant through the system as shown by the dotted lines 88 and 90 in the valve 58. In the hot water mode of operation, refrigerant from the discharge end 26 of the compressor 22 is conducted through the line 88 and the line 56 and into the evaporator '48 whereupon the resultant heat exchange therein produces hot water at the output of the line 52. The refrigerant passing through the evaporator in the line 56 exits through the line 54 where it enters the strainer-dryer 86 which, as previously mentioned for reverse operation, will produce the same function as the strainer-dryer 84. The refrigerant then passes through the capillary expansion tube 64, the strainer-dryer 84, condenser 74, line 72, line 90 of valve 58, line 60, the suction accumulator 62 and then enters the suction end 24 of the compressor 22. Thus, the system can be used to produce hot water rather than chilled water, when such is desired.
v the refrigerated chilled water at the output of the evaporator 48. An ice/brine slurry can be provided by recycling the chilled water at the output 52. This can be accomplished by reconveying the chilled seawater through the brine pump 36 as shown by dashed line 92. This provides the capability of adjusting the output temperature while preserving the monotube positive displacement character of the system. Thus, the resultant recycling can reduce the temperature of the slurry at the output of the hose 52 to 15F. Thus, the capability of continuously freezing seawater is provided. Since the brine pump 36 is a positive displacement pump, any ice crystals formed in the single line 46 or in the monotube section of the evaporator connected to the line 46 are pushed therethrough by the increasing pressure applied by the pump as the seawater becomes more viscous or as the tube becomes restricted. The monotube evaporator design coupled with the positive displacement brine pump creates an increasing shearing action at any spot where local build-up of ice scale would occur, thereby keeping the tube free-flowing, the ice/- brine slurrywell mixed and the ice crystals extremely fine in texture.
Referring now to FIG. 2, there is shown a preferred embodiment of the evaporator 48.utilized in the construction of the refrigeration system of FIG. 1. The evaporator 48 comprises an inner coiled tube 102, one end of which is connected to the output line 52. Surrounding the coiled line 102 in an outer coiled line 104,
one end of which is connected to the refrigerant line 54 and the other end of which is connected to the refrigerant line 56. In a typical construction, the line 102 is formed of a it; inch outer diameter tube of about 50 feet in length, and the tube 104 surrounding the tube 102 is fonned with a 5 1 inch outer diameter. Such a coiled tube-within-a-tube construction efficiently produces chilled seawater having a temperature in the range of 29-39F, and an ice/slurry when recycled as above.
The condenser 74 may be constructed in a manner similar to the evaporator 48 wherein an inner tube containing the seawater is surrounded by an outer tube containing the refrigerant which is cooled and condensed as it passes in annular countercurrent flow arrangement with the seawater in the inner tube. Coiling of the tubes as illustrated results in an advantageous economy of space and portability. The evaporator and condenser coils can be nested one within the other, permitting compact enclosure which facilitates sliding, skidding and other handling and installation of the unit. The enclosure can be made as a Water-proof hull for flotation on the surf and between boats at sea.
Referring back to FIG. 1, there is illustrated, in shadow, a further embodiment wherein means are provided to chemically treat the brine applied to the fish.
said pump upstream of 6 Specifically, a hold tank 55 is provided which may be in the form of a container, pressure vessel, flexible feed bag, drum or the like, and which is connected into the I brine pump strainer 44 through a valve 59 as shown or ity system for converting seawater into refrigerated seawater, comprising:
single drive means; an evaporator for lowering the temperature of seawater, said evaporator comprising an outer coiled evaporator tube and an inner coiled evaporator tube within and coextensive with said outer evaporator tube and having a discharge end extending therefrom; a refrigerant condenser comprising an outer coiled condenser tube and an inner coiled condenser tube within and coextensive with said outer condenser tube and having a discharge end extending therefrom;
refrigerant tube means for. connecting said outer evaporater and condensure tubes constituting with said outer tubes a refrigerant line;
strainer means in said refrigerant line;
compressor means connected to said refrigerant line for circulating refrigerant therethrough and driven by said single drive means;
means for pumping seawater through said inner evaporator and condenser tubes comprising at least one positive displacement-pump, and strainer means therefor, connected to said inner evaporator and condenser tubes and driven by said single drive means, whereby to provide cooled seawater discharge from said inner evaporator tube discharge end and heated seawater discharge from said inner condenser tube discharge end;
valve means for reversing the flow of refrigerant through said refrigerant line whereby to produce hot water at the discharge encl of said inner evaporator tube.
2. A system in accordance with claim 1 wherein said condenser and evaporator coils are nested.
3. A system in accordance with claim 1 and further comprising means for recirculating said refrigerated seawater at the output of said refrigerator through said pump means to form the output of said inner evaporator tube as an ice/brine slurry.
4. A system in accordance with claim 1 and further comprising means for applying fish treating agents to said evaporator.

Claims (4)

1. A portable single drive, positive displacement utility system for converting seawater into refrigerated seawater, comprising: single drive means; an evaporator for lowering the temperature of seawater, said evaporator comprising an outer coiled evaporator tube and an inner coiled evaporator tube within and coextensive with said outer evaporator tube and having a discharge end extending therefrom; a refrigerant condenser comprising an outer coiled condenser tube and an inner coiled condenser tube within and coextensive with said outer condenser tube and having a discharge end extending therefrom; refrigerant tUbe means for connecting said outer evaporater and condensure tubes constituting with said outer tubes a refrigerant line; strainer means in said refrigerant line; compressor means connected to said refrigerant line for circulating refrigerant therethrough and driven by said single drive means; means for pumping seawater through said inner evaporator and condenser tubes comprising at least one positive displacement pump, and strainer means therefor, connected to said inner evaporator and condenser tubes and driven by said single drive means, whereby to provide cooled seawater discharge from said inner evaporator tube discharge end and heated seawater discharge from said inner condenser tube discharge end; valve means for reversing the flow of refrigerant through said refrigerant line whereby to produce hot water at the discharge end of said inner evaporator tube.
2. A system in accordance with claim 1 wherein said condenser and evaporator coils are nested.
3. A system in accordance with claim 1 and further comprising means for recirculating said refrigerated seawater at the output of said refrigerator through said pump means to form the output of said inner evaporator tube as an ice/brine slurry.
4. A system in accordance with claim 1 and further comprising means for applying fish treating agents to said pump upstream of said evaporator.
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992896A (en) * 1973-08-22 1976-11-23 August Janson Air conditioning system
FR2487056A1 (en) * 1980-07-18 1982-01-22 Froid Ste Toulousaine Cooling or reheating of liq. in mobile tank - where liq. is circulated through external heat exchanger, and tank is mounted on lorry or wagon used to transport the liq.
US4335580A (en) * 1979-11-08 1982-06-22 Carrier Corporation Refrigeration unit with water cooled condenser
US4769998A (en) * 1986-04-25 1988-09-13 Advantage Electronics, Incorporated Precision-controlled water chiller
US4850201A (en) * 1986-04-25 1989-07-25 Advantage Engineering Incorporated Precision-controlled water chiller
US4922724A (en) * 1989-03-13 1990-05-08 William Grayson Marine ice making and delivery system
US4936102A (en) * 1987-07-20 1990-06-26 Sunwell Engineering Company Ltd. Method and apparatus for cooling fish on board a ship
US5584185A (en) * 1992-05-14 1996-12-17 Mishport Pty Ltd Engine powered energy providing assemblies
US5848536A (en) * 1997-02-26 1998-12-15 Dodge; David Self contained marine air conditioner
US6263689B1 (en) 1998-10-29 2001-07-24 Taylor Made Environmental, Inc. Chilled water marine air conditioning
FR2835454A1 (en) * 2002-02-01 2003-08-08 Collard Trolart Thermique Coaxial tube heat exchanger has movable inner tube fitted with spacers to maintain its distance from outer tube when bent
US6658889B2 (en) 2001-06-20 2003-12-09 3L Filters Ltd. Apparatus for producing potable water and slush from sea water or brine
US20070068188A1 (en) * 2005-09-29 2007-03-29 Tecumseh Products Company Ice maker circuit
US10913526B2 (en) * 2019-06-18 2021-02-09 Kevin J. Clark Fresh water boat chiller system

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1712568A (en) * 1926-12-10 1929-05-14 Peerless Ice Machine Company Refrigerating system
US2136813A (en) * 1935-09-12 1938-11-15 Dewey H Dolison Liquid cooler control
US2299188A (en) * 1940-03-13 1942-10-20 Ralph E Stork Refrigeration system
US2511582A (en) * 1945-09-12 1950-06-13 Grindrod George Process and apparatus for cooling milk and other liquids
US2513373A (en) * 1947-09-20 1950-07-04 American Gas And Electric Comp Heat pump system
US2596195A (en) * 1947-04-24 1952-05-13 Bell & Gossett Co Heat exchanger for refrigerating systems
US2620635A (en) * 1950-09-09 1952-12-09 Erwin W Mautner Cooling system and control
US2746272A (en) * 1952-07-24 1956-05-22 Walter H Carpenter Method for holding shrimp
US2966779A (en) * 1957-05-27 1961-01-03 Larco Inc Heating and cooling system for motor yachts
US3540229A (en) * 1969-01-24 1970-11-17 Repco Products Corp Air cooling apparatus

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1712568A (en) * 1926-12-10 1929-05-14 Peerless Ice Machine Company Refrigerating system
US2136813A (en) * 1935-09-12 1938-11-15 Dewey H Dolison Liquid cooler control
US2299188A (en) * 1940-03-13 1942-10-20 Ralph E Stork Refrigeration system
US2511582A (en) * 1945-09-12 1950-06-13 Grindrod George Process and apparatus for cooling milk and other liquids
US2596195A (en) * 1947-04-24 1952-05-13 Bell & Gossett Co Heat exchanger for refrigerating systems
US2513373A (en) * 1947-09-20 1950-07-04 American Gas And Electric Comp Heat pump system
US2620635A (en) * 1950-09-09 1952-12-09 Erwin W Mautner Cooling system and control
US2746272A (en) * 1952-07-24 1956-05-22 Walter H Carpenter Method for holding shrimp
US2966779A (en) * 1957-05-27 1961-01-03 Larco Inc Heating and cooling system for motor yachts
US3540229A (en) * 1969-01-24 1970-11-17 Repco Products Corp Air cooling apparatus

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992896A (en) * 1973-08-22 1976-11-23 August Janson Air conditioning system
US4335580A (en) * 1979-11-08 1982-06-22 Carrier Corporation Refrigeration unit with water cooled condenser
FR2487056A1 (en) * 1980-07-18 1982-01-22 Froid Ste Toulousaine Cooling or reheating of liq. in mobile tank - where liq. is circulated through external heat exchanger, and tank is mounted on lorry or wagon used to transport the liq.
US4769998A (en) * 1986-04-25 1988-09-13 Advantage Electronics, Incorporated Precision-controlled water chiller
US4850201A (en) * 1986-04-25 1989-07-25 Advantage Engineering Incorporated Precision-controlled water chiller
US4936102A (en) * 1987-07-20 1990-06-26 Sunwell Engineering Company Ltd. Method and apparatus for cooling fish on board a ship
US4922724A (en) * 1989-03-13 1990-05-08 William Grayson Marine ice making and delivery system
US5584185A (en) * 1992-05-14 1996-12-17 Mishport Pty Ltd Engine powered energy providing assemblies
US5848536A (en) * 1997-02-26 1998-12-15 Dodge; David Self contained marine air conditioner
US6263689B1 (en) 1998-10-29 2001-07-24 Taylor Made Environmental, Inc. Chilled water marine air conditioning
US6449973B2 (en) 1998-10-29 2002-09-17 Taylor Made Environmental Systems, Inc. Chilled water marine air conditioning
US6658889B2 (en) 2001-06-20 2003-12-09 3L Filters Ltd. Apparatus for producing potable water and slush from sea water or brine
FR2835454A1 (en) * 2002-02-01 2003-08-08 Collard Trolart Thermique Coaxial tube heat exchanger has movable inner tube fitted with spacers to maintain its distance from outer tube when bent
US20070068188A1 (en) * 2005-09-29 2007-03-29 Tecumseh Products Company Ice maker circuit
US10913526B2 (en) * 2019-06-18 2021-02-09 Kevin J. Clark Fresh water boat chiller system

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