WO2016114929A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2016114929A1
WO2016114929A1 PCT/US2015/068040 US2015068040W WO2016114929A1 WO 2016114929 A1 WO2016114929 A1 WO 2016114929A1 US 2015068040 W US2015068040 W US 2015068040W WO 2016114929 A1 WO2016114929 A1 WO 2016114929A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
internal
passageways
supply assembly
Prior art date
Application number
PCT/US2015/068040
Other languages
English (en)
Inventor
Bruce I. NELSON
Original Assignee
Colmac Coil Manufacturing, Inc.
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
Priority claimed from US14/594,803 external-priority patent/US9689621B2/en
Application filed by Colmac Coil Manufacturing, Inc. filed Critical Colmac Coil Manufacturing, Inc.
Publication of WO2016114929A1 publication Critical patent/WO2016114929A1/fr

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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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F28F1/405—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element and being formed of wires
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0042—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for foodstuffs

Definitions

  • the present invention relates to a heat exchanger, and more particularly to a heat exchanger which finds particular utility, and usefulness, in the direct contact cooling of processed food products, BACKGROUND ART
  • Direct contact cooling of processed food products has been widely used in the food processing industry since the 1960s.
  • the direct contact cooling units, or ''plate freezers" as identified within the industry are traditionally constructed of individual planks which are coupled together through welding or other traditional means. Bach of these planks contain internal passageways, through which a volatile refrigerant is introduced. The evaporation of the volatile refrigerant absorbs ambient heat and cools the surface of the planks, which in turn, cools the product which is resting on the surface of the planks.
  • flash gas is usually formed in the common intake manifold at the end of the freezing cyc le if the flow rate of the refrigerant is reduced by throttling or the temperature of the refrigerant is permitted to approach its saturation temperature.
  • the formation of flash gas, and the resulting non-uniform distribution of the liquid refrigerant causes unintended consequences in the freezing process. For example, as the top direct contact plates are ''starved" of liquid refrigerant. the bottom direct contact plates have an abundance of liquid refrigerant. This situation results in an unequal freezing of individual items or products which are placed on the top direct contact plates (under-freezing), versus those placed on the bottom direct contact plates (over-freezing),
  • a first aspect of the present invention relates to a heat exchanger which includes a heat exchanger portion defining a multiplicity of internal passageways, and wherein at least one of the passageways is defined, at least in part, by a wicking structure; and a source of an ammonia refrigerant provided at a flow rate, and which is further supplied to the respective internal passageways of the heat exchanger portion, and wherein the source of refrigerant has a vapor and liquid phase, and wherein the source of the ammonia refrigerant is supplied in predetermined amounts to each of the internal passageways which are defined by the heat exchanger portion regardless of the liquid or vapor phase condition of the ammonia refrigerant or the refrigerant flow rate.
  • a second aspect of the present invention relates to a heat exchanger which includes a plurality of heat exchanger portions each defining a multiplicity of internal passageways, and wherein at least some of the interna; passageways are defined, at least in part, by a icking structure; a refrigerant supply assembly having a weir, and which operabiy cooperates with at least one of the plurality of heat exchanger portions, and wherein the refrigerant supply assembly is coupled in fluid-flowing relation relative to at least one of the multip!ieity of internal passageways: a refrigerant delivery conduit coupling the refrigerant supply assembly in fluid-flowing relation relative to a source of a refrigerant; and a bimetallic coupler which is coupled in fluid-flowing relation relative to the refrigerant supply assembly, and the refrigerant delivery conduit,
  • Still yet another aspect of the present invention relates to a heat exchanger which includes a plurality of heat exchanger portions, and which each has formed therein a multiplicity of internal passageways that are defined by an internal wail, and which individually allow for the movement of a source of a refrigerant, having both liquid and vapor portions, therethrough, and wherein the internal passageways are defined, at least in part, by a wicking structure which is effective, by a capillary force, to draw the liquid refrigerant up onto the internal wall, and which defines the respective internal passageways; a refrigerant supply assembly mounted on each of the heat exchanger portions, and which is further coupled in fluid flowing relation relative to the respective internal passageways which are defined by the individual heat exchanger portions, and wherein each of the refrigerant supply assemblies has a weir which controls the flow of the liquid refrigerant which is supplied to the respective internal passageways that are defined by the individual heat exchanger portions; a plurality of refrigerant delivery conduits each having a first, intake end which
  • Fig. 1 illustrates a typical prior art plate freezer arrangement.
  • Fig. 1 A illustrates a typical fixed orifice arrangement as used in prior art plate freezers as seen in Fig. 1.
  • Fig. 2 illustrates a prior art plate freezer having multiple extruded planks which provide passageways for the flow of refrigerant.
  • Fig. 2A illustrates a transverse vertical sectional view of a prior art plate freezer and which is taken from a position along hne 2A-2A of Fig. 2.
  • Fig. 2B illustrates a second transverse vertical sectional view taken from a position along line 2B-2B of Fig. 2.
  • Fig. 3 is a longitudinal vertical sectional view taken through a prior art, smooth inside diameter, horizontal evaporator tube and which shows the refrigerant flow pattern exhibited by same.
  • Fig. 3A-3E are transverse, vertical, sectional views taken from various positions along lines 3A-3A, 3B-3B, 3C-3C, 3D-3D, and 3E-3E of Fig. 3.
  • Fig. 4 illustrates a fragmentary, environmental, side elevation view of the present invention.
  • Fig, 4A is a longitudinal, transverse, vertical sectional view taken through a refrigerant distributor which forms a feature of the present invention.
  • Fig. 5 shows four exemplary, and non-limiting embodiments of wicking structures which form a feature of the present invention
  • Fig. 5A is a transverse, vertical, sectional view taken through one form of wicking structure which finds usefulness in the present invention.
  • Fig. 5A 1 is a longitudinal, vertical, sectional view taken from a position along line A l -A l of Fig, 5 A.
  • Fig. 5A2 is a longitudinal, vertical, sectional view taken from a position along line A2-A2 of Fig. 5 A.
  • Fig. SB is a transverse, vertical, sectional view taken through another form of the invention
  • Fig. 5 ⁇ ⁇ is a longitudinal, vertical, sectional view taken from a position along line B-B of Fig. 5B.
  • Fig, 5B2 is a greatly exaggerated, functional depiction of a portion of the structure as seen in Fig. 5B 1 , as indicated by tiie arrow.
  • Fig. 5C is a transverse, vertical, sectional view of yet another form of the present invention.
  • Fig, SC I is a longitudinal, vertical, sectional view taken from a position along line C- C of Fig. 5C,
  • Fig. 6 is a great simplified, schematic, top plan view of a portion of a plate freezer portion of the present invention, and with some surfaces removed to show the structure thereunder.
  • Fig. 6A is a top plan view showing an enlarged, fragmentary portion of the internal structure of the novel plate freezer of the present invention.
  • Fig. 68 is an enlarged, transverse, vertical, sectional view taken from a position along line 6B-6B of Fig. 6.
  • Fig. 6C is an enlarged, fragmentary, vertical, sectional view taken from a position along line 6C-6C of Fig, 6,
  • Fig. 61 is again an enlarged, fragmeniary, longitudinal, vertical, sectional view taken from a position along line 6D-6D of Fig. 6.
  • Fig. 7 is a graphical depiction of the refrigeration performance of the present invention with reported L/D performance as compared to a prior art design.
  • Fig. 8 depicts a typical manifold coupling used to connect a source of refrigerant with a prior art plate freezer.
  • Fig. 8A depicts a transverse, vertical, sectional view taken from a location along line SA-SA of Fig. 8.
  • the present invention provides a novel means, as will be discussed in greater detail hereinafter, for mitigating the sometimes disappointing refrigeration performance, and potential health hazards which has been occasionally associated with die prior art direct contact plate cooling units which have been used, heretofore.
  • a well known deficiency of the currently employed direct contact piate cooling units or devices has been the non-uniform distribution of liquid ammonia refrigerant within same, due to the formation of Cash gas, and the further development and/or existence of stratified or wavy flow movement of the liquid ammonia refrigerant within the iniernai passageways of the freezer planks which form a part of the direct contact cooling plates.
  • a prior art piate freezer as employed in a prior art direct contact piate cooling system is generally indicated by the numeral 10.
  • the structure includes a plurality of moveable, direct contact freezing plates 1 1 .
  • the plurality of direct contact freezing plates 1 1 are fluid flowingly connected to a liquid ammonia refrigerant feed manifold 12 by a plurality of flexible hoses or conduits 13.
  • a source of liquid ammonia refrigerant 12A is distributed to each of the flexible hoses 13 by the liquid ammonia, refrigerant manifold 12, Further, the flexible hoses or conduits 13 are connected to both the liquid ammonia refrigerant manifold 12, and the direct contact freezing plates 1 1 by way of individual threaded stainless steel fittings 14a and Mb, respectively.
  • FIG 1A shows an enlarged depiction of an aspect of FIG 1
  • a prior art threaded stainless steel fitting 14a is depicted as fluid flowingly coupling the flexible hose 13, and the liquid ammonia refrigerant manifold 12.
  • a prior art fixed orifice 15 is also shown in FIG 1 A.
  • the fixed orifice 1 5 has been used, heretofore, to control the flow of the liquid ammonia refrigerant 12A, and to create a substantially uniform distribution of the liquid ammonia refrigerant 12A throughout the direct contact freezing plates 1 1.
  • FIG 2 shows a top plan view of a prior art direct contact plate freezer 1 1 and its constituent individual portions, which are typically referred to as "planks" 20.
  • the individual planks 20 contain multiple internal passageways 21 , which cars best be seen in FIG 2A,
  • the multiple internal passageways which are generaiiy rectangularly shaped (FIG 2A) are machined, moided or cast to create a flow or refrigerant pathway 22 for the liquid ammonia refrigerant. 12A.
  • the liquid ammonia refrigerant enters the internal passageways 21 through a fixed liquid intake connection or conduit 23 which is typically located at one corner of the direct contact plate freezer 1 1 .
  • the refrigerant 12A exits the internal passageways 21 through a fixed liquid suction or exhaust connection or conduit 24 that is located at an opposite corner of the direct contact plate freezer 1 1. While the liquid ammonia refrigerant 12A is within the internal passageways 21 of the direct contact plate freezer 1 1, the flo pathway 22 channels the refrigerant in a back and forth or serpentine like path of travel, as can best be seen in FIG 2, In this prior art design 10. the two phase flow pattern of the liquid ammonia refrigerant 12(a) is invariably stratified or wavy (FIG 3). This results in the separation of the liquid phase ammonia 25, and vapor phase ammonia 26, within the internal passageways, as can best be seen in FIG 2B. This flow pattern will be discussed in greater detail, hereinafter.
  • F G 3 a multiplicity of two-phase refngerant flow patterns which may be experienced during evaporation of the liquid ammonia refrigerant 2(a) in smooth inside diameter, substantially horizontally disposed evaporator tubes or substantially circular shaped fluid passageways, (not shown), is illustrated.
  • the flow of the refrigerant includes a single phase liquid region 30; a bubble region 31 ; a plug flow region 32; a slug Dow region 33 ; a wavy flow region 34; an annular flow region 35; and a. dry wall flow region 36.
  • this drawing illustrates a prior art intake manifold coupling 40.
  • this prior art manifold coupling 40 includes an aluminum block 41 which is drilled and tapped 40A (Fig 8 A) to accept a threaded stainless steel refrigerant tube 42.
  • the aluminum block 41 is connected to the direct contact piate freezer manifold extrusion 43 by threaded bolts 44,
  • FiG 8A which shows a transverse, vertical, sectional view taken from a location along line 8A-SA of FIG. 8, the aluminum block 40 manifold extrusion interface is coupled in fluid sealing relation to the intake manifold extrusion 43 by means of an O-ring 45.
  • the prior art method of connecting stainless steel threaded fittings, as seen in FiG 8, to an aluminum conduit, or an aluminum block 41 causes problems because it is typically a source of liquid ammonia refrigerant leaking. This leaking of liquid ammonia refrigerant in prior art structures utilizing stainless steel to aluminum interfaces is due to the differences in the linear coefficient of expansion between stainless steel and aluminum.
  • the present invention 80 includes a liquid ammonia refrigerant distributor which is generally indicated by the numeral 50, and which forms a feature of the present invention.
  • the liquid ammonia refrigerant distributor includes a tank 5 .1 , which is substantially elongated and typically assumes a cylindrical shape.
  • FIG 4A shows a tank 51 having a substantially cylindrical shape, other tank shapes may be employed with equal success in the present invention.
  • the tank 51 as depicted in FIGS 4 and 4A has a main body 52, and is substantially horizontally disposed or oriented.
  • the tank 51 is defined by an outside facing surface 53, and an opposite inside facing surface 54,
  • the inside facing surface 54 defines an internal cavity 55 having a given volume.
  • the tank 51 includes opposite end walls 51 A and 5 IB, respectively.
  • the main body 52 of the tank 51 is defined by a generally longitudinally disposed axis 56, and a transversely disposed axis 57,
  • a first aperture 58 is formed within end wal l 51A of the tank 51 , This first aperture 58 is substantially coaxial! ⁇ ' aligned relative to the longitudinal axis 56 of the main body 52. Still further, and formed in the main body 52 is an enlarged second aperture 59 for receiving, at least in part, a contaminant collection container 60. Additionally, as depicted in F3G 4A, there is formed within the main body 52 a plurality of spaced refrigerant distributor conduit apertures 61 which permit individual refrigerant distributor conduits 62 to extend therethrough. These stnjetures are discussed in greater detail below. Depending upon the form of the invention, the plurality of refrigerant distributor conduit apertures 63 may be oriented at given predetermined distances along the main body 52.
  • the individual refrigerant distributor conduits 62 are operable to provide the source of liquid ammonia refrigerant 32A to the liquid ammonia refrigerant feed manifold 86, as will be discussed in greater detail, below.
  • the plurality of refrigerant distributor conduits 62 each have a first end 63 which is received within the internal cavity 55, As can be recognized by a study of FIG 4A, the first ends 63 of each of the individual refrigerant distributor conduits 62 are located in substantially parallel, spaced relation, one relative to the others, and are substantially verticall oriented within the internal cavity 55 of the tank 51.
  • the respective refrigerant distributor conduits each have a second end 64, which is best seen in FIG 4, and which are further located outside of the tank 53 , and which, additionally, are coupled in refrigerant delivering relation relative to a novel liquid ammonia refrigerant feed manifold 86, and which will be discussed in greater detail in the paragraphs which follow,
  • a multiplicity of apertures 65 are formed within the first end 63 of each of the refrigerant distributor conduits 62.
  • These multiplicity of apertures 65 each have a cross sectional or diametral dimension which diminishes in dimension when that cross sectional or diametral dimension is measured from the first end 63 of the respective refrigerant distributor conduit 62, and in the direction of the second end 64 thereof.
  • These variably sized multiplicity of apertures 65 facilitate the substantial equal flow of liquid ammonia refrigerant 12A out through the refrigerant distributor conduits 62 as the volume of liquid ammonia refrigerant 12A increases within the tank 51 .
  • the multiplicity of apertures 65 which are formed within the first end 63 of the respective refrigerant distributor conduits 62 includes first, second, third and fourth, pairs of substantially eoaxialiy aligned apertures. These respective pairs of apertures are indicated by the numerals 71, 72, 73 and 74, respectively. With regards to these pairs of apertures, they have individual cross sectional or diametral dimensions which lie in the range of about 1.0 mm to about 5.0 mm .
  • each of the pairs of apertures 65 ar ail located within the internal cavity 55 of the tank 51 , and each of the pairs of apertures 65 are located at a given distance from the first end 63 of the respective refrigerant distributor conduits 62, in this regard, the first pair of apertures 71 are located at about 0,25 inches from the first end 63 thereof.
  • the second pair of apertures 72 are located at about 0.625 inches from the first end 63 thereof.
  • the third pair of apertures 73 are located at about 1 ,0 inch from the first end 63 thereof.
  • the fourth pair or apertures 74 are located at about 3 ,3 inches from the first end 63 thereof.
  • a possible fifth, sixth and seventh pair of apertures are possible, but not shown.
  • the first pair of apertures 71 each have a similar diametral dimension of about 0, 187 inches.
  • the second pair of apertures, 72 each have a similar diametral dimension of about 0.125 inches.
  • the third pair of apertures 73 each have a similar diametral dimension of about 0.0625 inches.
  • the fourth pair of apertures 74 each have a similar diametral dimension of about 0,0469 inches.
  • the spacing between the pairs of apertures 71 -74, respectively, and the diametral dimensions of the individual multiplicity of apertures 65 also provides a convenient means whereby the refrigerant distributor SO may be operated over a wider range of cooling loads not possible with refrigerant distributors constructed in accordance with prior art teachings.
  • the refrigerant distributor 50 further includes an inlet conduit 66 which is operable to deliver the source o the refrigerant 12A to the internal cavity 55 of the tank 51 ,
  • the inlet conduit 66 has a first, intake end 67, and an opposite, second, exhaust end 68 which is located within the interna! cavity 55.
  • the second, exhaust end 68 is defined by upper and lower exhaust apertures 68A and 68B respectively.
  • the lower exhaust aperture is located in fluid delivering relation relative to the containment collection container 60.
  • the present invention 80 is illustrated in a typical operational arrangement.
  • the liquid ammonia distributor tank 50 as shown in FIG 4A, and discussed in detail, above, distributes substantially equal amounts of liquid ammonia refrigerant 12A, regardless of the physical state of the refrigerant, to the individual freezer plates or heat exchanger portions 81 of the present invention 80.
  • the present invention 80 has an external appearance similar to that of the prior art, as shown in FIG 1, inasmuch as the present invention 80 includes a plurality of flexible hoses or conduits 1 which are coupled in fluid flowing relation to a novel direct contact freezer plate or heat exchanger portion 81 , Further, the flexible hoses or conduits 13 are connected to the new, and novel liquid ammonia refrigerant manifold 86, and the new, direct contact freezer plates, or heat exchanger portions 81 through the use of stainless steel threaded fittings 14a and 14b, respectively.
  • the plurality of new, direct contact freezer plates 81, utilized in the present invention 80, are connected through conventional means to form a continuous direct, contact freezing surface, such as by welding and other fastening means.
  • a continuous direct, contact freezing surface such as by welding and other fastening means.
  • FIG 6 a greatly simplified, schematic, top plan view of a portion of the freezer plate, or heat exchanger portion 81 of the present invention 80 is illustrated.
  • This structure includes a piuraiity of extruded aluminum pianks 82 which are each defined by a multiplicity of round, internal passageway 83, which are discussed in greater detail, hereinafter.
  • Each of the plurality of extruded aluminum planks 81 has a first end 84 and a second end 85,
  • the structure of the present invention 80 further includes a, novel header, or intake manifold, or refrigerant supply assembly 86.
  • the header plate, intake manifold or refrigerant supply assembly 86 is attached to the first end 84 of each of the extruded aiuminum planks 82 by conventional fastening means, such as by welding (FIG 6C) or the like.
  • the structure, as illustrated, further includes a bimetallic coupling 90, which has a stainless steel portion 91 , and an aiuminum portion 92 which are fused together by employing means such as roll bonding or explosion welding.
  • the bimetallic coupler is coupled as by welding (FIG 6C), to the refrigerant supply assembly or intake manifold 86 and will be discussed in greater detail hereinafter.
  • the ammonia refrigerant I2A once introduced to the extruded aluminum planks 81, flows back and forth through the round internal passageways 83 so as to provide consistent and substantially even heat exchange throughout the entirety of the direct contact freezing surface of the plate 81 which defines a portion of the present invention 80.
  • This movement of the refrigerant is most accurately characterized as straived-wavy, but the wicking structure now mitigates the effects of this type of flow.
  • FIG 6A illustrates a top plan, enlarged view of a portion of the internal structure of the novel freezer plate 81 of the present invention 80
  • the refrigerant supply assembly or intake manifold 86 is defined by an elongated internal passageway 100
  • the internal passageway has a lower portion 101 (Fig 6C) which acts as a reservoir 102, and further defines a weir 103 which collects the liquid ammonia refrigerant 12A which is being distributed or supplied by the bimetallic coupling 84, and which further returns or directs the flow of the refrigerant 12A through the round internal passageways 83 of each of the extruded aluminum planks 82.
  • the reservoir 102 further operates to change the direction of the Dow of liquid ammonia refrigerant 12A about 180 degrees as the liquid ammonia refrigerant 12A exits the round interna! passageways 83 of one of the extruded aluminum planks 82, and enters the round internal passageways 83 of a neighboring extruded aluminum plank 82, by utilizing a plurality of baffles 104 which are located at predetermined, spaced distances along the internal passageway 100 (Fig 6 AO. The respective baffles 104, and the weir 103.
  • wicking structures 200 which constitute a feature of the present invention 80 are shown, As illustrated, one aspect of the present invention 80 relates to a plurality of round passageways 83 which are formed in the new novel, direct contact freezer plate or heat exchanger portions S 3 as earlier described. It should be understood, the round passageways 83 define a cavity 202 which allows a source of the liquid ammonia refrigerant 12A to pass therethrough. Referring now to FIGs 5A and 5A1 , a first form of the present invention is illustrated and which includes two possible wicking structures. The inside facing surface 204 which defines the round passageways 83 are individually coupled in fluid receiving relation relative to a source of a liquid ammonia refrigerant 12A.
  • the first wicking structure which enhances the cooling performance of this structure is indicated by the numeral 206, and is illustrated as helical grooving which is formed in the inside facing surface 204,
  • capillary action facilitated by the wicking structure 206, causes the liquid ammonia refrigerant 12A to be drawn up onto, and alongside, the inside facing surface 204 which defines the round passageways 83 of the direct contact plate freezer 81.
  • This capillary action substantially mitigates the negative effects of the stratified and/or wavy flow patterns 34 of the liquid ammonia refrigerant 12A within the respective round passageway 83.
  • the wicking structure 206 as seen in this form of the invention comprises a multiplicity of helical grooves having a depth of about 0.005 to about 0.05 inches; a spacing of about 0,01 to about 0.1 0 inches; and a lead angle of about 15° to about 90° respectively.
  • FIG 5A2 a second form 207 of the wicking structure 200 is shown.
  • the round passageway 83 in this form of the invention includes a wicking structure which is again formed into the inside feeing surface 204, and which comprises a multiplicity of cross-hatched knurls 207 which are formed into the inside facing surface 204 of the respective round passageways 83.
  • cross-hatched knurls 207 are dimensioned so as to generate the desired capillary action as discussed, above.
  • the respective cross-hatch knurls 207 have a length of about 0,005 to about 0.05 inches; a spacing of about 0.01 to about 0.10 inches; and a lead angle of about 1 5° to about 90° respectively.
  • a third form 208 of the wicking structure 200 comprises a feature of the present invention.
  • the present invention includes a plurality of passageways 83 which are formed in the direct contact plate freezer 81, and which have a wicking structure 208 which comprises a sintered metal coating which is deposited upon the inside facing surface 204 of the respective, round passageways 83.
  • This sintered metal coating 208 is effective in drawing the liquid ammonia refrigerant 12.A, by capillary action, up onto the inside facing surface 204 of the respective round passageways 83.
  • the sintered metal coating is formed from a metal selected from the group comprising stainless steel, nickel, copper and/or aluminum, Still further in this arrangement [FIG 5B2].
  • the sintered metal coating 208 is formed to have a plurality of pores 209 having a pore radius of about 0,001 to about 0.04 cm.
  • the wicking structure 200 comprises a wire mesh which is generally indicated by the numeral 230.
  • the wire mesh has a size ranging from about 60 to about 450 openings per square inch.
  • the wire mesh 210 is formed from metal selected from the group comprising stainless steel; nickel; copper; and/or aluminum, AH forms of the invention as seen in FIG 5 produce an effective capillary action so as to facilitate the advantageous operation of the present invention.
  • a feature of the present invention relates to the advantageous formation of the respective, plurality of round passageways 83 in the direct contact plate freezer plates or heat exchanger portions 81 , in this regard, it should be understood that the direct contact freezer plates or heat exchanger portions 81 comprise metal plates formed of individual metal planks 82 which are fastened together, and wherein the internal passageways 83 formed in the respective individual planks 82 are substantially circular in cross section and have a predetermined diametral dimension as indicated in FIG 6B, in this arrangement the internal passageways 83 are further located at a predetermined distance or pitch from an adjacent internal passageway 83 labeled L in FIG 6B.
  • the ratio of the L/D is greater than about. 1.3, it has been found that this pitch versus diametral relationship provides advantageous cooling for the new and novel invention 80 as depicted.
  • the advantageous performance relative to the prior art assemblies is graphically depicted in FIG 7. OPERATION
  • the present invention comprises a heat exchanger 80 which includes a heat exchanger portion 81 defining a multiplicity of internal passageway 83, and wherein at least one of the passageways 83 is defined, at least in part, by a wicking structure 200.
  • a source of an ammonia refrigerant 12A is supplied to the internal passageways 83 of the heat exchanger portion 81 at a flow rate,
  • the source of refrigerant 12A is has a liquid and a vapor phase condition 25 and 26, respectively.
  • the source of refrigerant is supplied in predetermined amounts to each of the internal passageways 83 of the heat exchanger portion 81 regardless of the liquid or vapor condition 24 or 25 respectively of the ammonia refrigerant 12A, or the refrigerant flow rate which is supplied to the refrigerant distributor 50.
  • a heat exchanger 80 which includes a plurality of heat exchanger portions 81 each defining a multiplicity of internal passageways 83. At least some of the internal passageways 83 are defined, at least in pari, by a wicking structure 200,
  • the invention includes a refrigerant supply assembly 86 having a weir 103 which is mounted on each of the respective heat exchanger portiorss 81. Further, the refrigerant supply assembly 86 is further coupled in fluid flowing relation relative to at least one of the multiplicity of internal passageways 83.
  • the invention 80 further includes a refrigerant delivery conduit 13 which couples the respective refrigerant supply assemblies 86 in fluid flowing relation to a source of a refrigerant 50. Further, the invention includes a bimetallic coupler 90 which is affixed in fluid flowing relation relative to the refrigerant supply assemblies 86, and one of the refrigerant delivery conduits 13,
  • the multiplicity of the internal passageways 83 are defined by an internal wall 204, and wherein the respective internal passageways 83 allow for the movement of the source of the refrigerant 12 A.
  • the wicking structure 200 is made integral with the internal wall 204, In the arrangement as shown in the drawings the wicking structure 200 is selected from the group comprising helical grooves 206, knurling, 207, sintered metal 208, and wire mesh 210, and which are respectively, individually, located on, or in contact with, the internal wall 204, and which defines the respective internal passageways 83.
  • the various wicking structures 200 are effective, by capiilary force, to draw the liquid refrigerant 12A up onto the internal wall 204 which defines the respective internal passageways 83.
  • the respective heat exchanger portions 81, and the refrigerant supply assembly 86 are fabricated from aluminum.
  • the weir 103 extends along at least a portion of a length dimension of the refrigerant supply assembly 86, and wherein the weir 103 controls the flow of the liquid refrigerant 12A which is supplied to the respective internal passageways 83 of each of the heat exchanger portions 81 .
  • a multiplicity of baffles 104 are located in predetermined spaced relation along the length of the refrigerant supply assembly 86, and which are individually effective to change a direction of movement of the liquid refrigerant 12A which is moving along the respective internal passageways 83 which are defined by the heat exchanger portions or direct contact freezer plates 81.
  • Still another aspect of the present invention relates to a heat exchanger 80 which particularly includes a plurality of heat exchanger portions 81 , and which each has formed therein a multiplicity of internal passageways 83 that are defined by an internal wall 204, and which individually allows for the movement of a source of refrigerant 12A having both liquid and vapor portions 25 and 26 respectively, therethrough.
  • the internal passageways 83 are defined, at least in part, by a wicking structure 200 which is effective, by capillary force, to draw the liquid refrigerant 12A up onto the internal wail 204, and which defines the respective internal passageways 83.
  • the plurality of heat exchanger portions 81 further include metal plates which are formed of individual metal planks 82 and which are fastened together.
  • the internal passageways 83 formed in the respective planks are substantially circular in cross section, and have a predetermined diametral dimension D as seen in FIG 6B, and wherein the internal passageways S3 are further located at a predetermined distance or pitch from an adjacent internal passageway [L], and wherein the ratio of the L/ ' D is greater than about 1.3.
  • the present invention 80 includes a refrigerant supply assembly 86 which is mounted on each of the heat exchanger portions 81, and which is further coupled in fluid flowing relation relative to the internal passageways 83 which are defined by the individual heat, exchanger portions 81.
  • Each of the refrigerant supply assemblies 86 has a weir 103 which controls the flow of the liquid refrigerant 12A which is supplied to the respective internal passageways 83 that are defined by the individual heat exchanger portions 81 .
  • the refrigerant supply assembly 86 further has a main body 87 with opposite first and second ends 88 and 89, respectively, and which defines an internal cavity or passageway 100 that extends between the opposite first and second ends.
  • the internal cavity or passageway 100 defines a reservoir 102 for receiving the liquid refrigerant 12 A which is delivered to the liquid supply assembly 86 by a refrigerant distributor 50.
  • the weir 103 is made integral with a refrigerant supply assembly 86, and is operable to control the flow of the liquid refrigerant 12A which is supplied to the reservoir 102 and to the respective internal passageways 83.
  • a plurality of baffles 1 04 are mounted within the internal cavity 100 of the refrigerant supply assembly 86, and which are located in predetermined spaced relation between the first and second ends 88 and 89 thereof.
  • the respective baffles 104 are individually operable to redirect the flow of the source of the refrigerant 12A and which is flowing along the respective internal passageways 83.
  • the present invention 80 further includes a refrigerant distributor 50 which supplies substantially equal amounts of the source of the refrigerant 12 A to each of the respective refrigerant supply assemblies 86.
  • the refrigerant distributor includes a tank 50 which defines an interna! cavity 55 for receiving the source of the refrigerant 12A which has both a liquid and a vapor portion 25 and 26, respectively.
  • the refrigerant distributor 50 further has an inlet conduit 66 for delivering the source of the refrigerant 12A to the internal cavity 55 of the tank 51 ,
  • the inlet conduit has a first intake end 67, and a second exhaust end 68, which is located within the internal cavity 55 of the tank 51.
  • the second exhaust end 68 is defined by an upper and lower exhaust aperture 68A and 68B respectively,
  • the refrigerant distributor 50 includes a contaminant collection container 60 which is coupled in fluid receiving relation relative to the internal cavity 55 of the tank 51.
  • the second exhaust aperture 68B of the inlet conduit 66 is disposed in fluid delivering relation relative thereto,
  • the present invention also includes a plurality of refrigerant distributor conduits 61 which are coupled in fluid receiving relation relative to the internal cavity 55 of the tank 51.
  • Each of the refrigerant distributor conduits has a first intake end 63, and a second exhaust end 64.
  • the first intake end 63 of the respective refrigerant distributor conduits 61 are substantially vertically oriented within the internal cavity 55 of the tank 51.
  • a multiplicity of apertures 65 are formed in each of the first end 63 of the respective refrigerant distributor conduits 61.
  • the multiplicity of apertures 65 each have a cross-sectional dimension which diminishes when the cross-sectional dimension is measured from the first intake end of the respective refrigerant distributor conduit 61, and in the direction of the second exhaust end 64, thereof.
  • the second exhaust end 64 is coupled in fluid flowing relation relative to the respective refrigerant supply assemblies 86.
  • the present invention 80 includes a bimetallic coupler 90 which is affixed to each of the respective refrigerant supply assemblies 86, and to the respective second exhaust end 64 of each of the individual refrigerant distributor conduit 61 .
  • the present invention provides a convenient means whereby high value food products may be chilled and otherwise refrigerated to a convenient amount in a manner not possible heretofore, Still further, the present invention avoids many of the shortcomings associated with the prior art teachings, and additionally provides a convenient means for refrigerating objects of interest by utilizing highly volatile refrigerants in a more effective manner and at lower refrigerant volumes thereby preventing or eliminating dangers associated with using such refrigerants,

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Dispersion Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur, qui comprend une partie d'échange de chaleur délimitant une pluralité de voies de passage internes, au moins l'une des voies de passage étant délimitée en partie par une structure à effet de mèche ; et une source de fluide frigorigène à l'ammoniac qui est apportée aux voies de passage internes de la partie d'échange de chaleur, des quantités pratiquement égales de fluide frigorigène liquide étant apportées à chacune des voies de passage, délimitées par la partie d'échange de chaleur.
PCT/US2015/068040 2015-01-12 2015-12-30 Échangeur de chaleur WO2016114929A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US14/594,803 US9689621B2 (en) 2012-06-20 2015-01-12 Heat exchanger
US14/594,803 2015-01-12

Publications (1)

Publication Number Publication Date
WO2016114929A1 true WO2016114929A1 (fr) 2016-07-21

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7597137B2 (en) * 2007-02-28 2009-10-06 Colmac Coil Manufacturing, Inc. Heat exchanger system
US7958738B2 (en) * 2008-06-06 2011-06-14 Colmac Coil Mfg., Inc. Direct expansion ammonia refrigeration system and a method of direct expansion ammonia refrigeration
US20130340979A1 (en) * 2012-06-20 2013-12-26 Bruce I. Nelson Heat Exchanger
US8783057B2 (en) * 2011-02-22 2014-07-22 Colmac Coil Manufacturing, Inc. Refrigerant distributor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7597137B2 (en) * 2007-02-28 2009-10-06 Colmac Coil Manufacturing, Inc. Heat exchanger system
US7958738B2 (en) * 2008-06-06 2011-06-14 Colmac Coil Mfg., Inc. Direct expansion ammonia refrigeration system and a method of direct expansion ammonia refrigeration
US8783057B2 (en) * 2011-02-22 2014-07-22 Colmac Coil Manufacturing, Inc. Refrigerant distributor
US20130340979A1 (en) * 2012-06-20 2013-12-26 Bruce I. Nelson Heat Exchanger

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