EP3517878B1 - Distributor for plate-fin heat exchanger - Google Patents

Distributor for plate-fin heat exchanger Download PDF

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Publication number
EP3517878B1
EP3517878B1 EP18153523.8A EP18153523A EP3517878B1 EP 3517878 B1 EP3517878 B1 EP 3517878B1 EP 18153523 A EP18153523 A EP 18153523A EP 3517878 B1 EP3517878 B1 EP 3517878B1
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EP
European Patent Office
Prior art keywords
passages
group
passage
section
type fin
Prior art date
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Application number
EP18153523.8A
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German (de)
English (en)
French (fr)
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EP3517878A1 (en
Inventor
Fang Xu
Donn Michael Herron
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Air Products and Chemicals Inc
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Air Products and Chemicals Inc
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Priority to PL18153523T priority Critical patent/PL3517878T3/pl
Priority to EP18153523.8A priority patent/EP3517878B1/en
Priority to ES18153523T priority patent/ES2837323T3/es
Publication of EP3517878A1 publication Critical patent/EP3517878A1/en
Application granted granted Critical
Publication of EP3517878B1 publication Critical patent/EP3517878B1/en
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    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • 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
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate heat exchangers
    • 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
    • F28D2021/0022—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for chemical reactors
    • 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
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • Plate-fin heat exchangers are well-known in the chemical process industry including processes for air separation.
  • Uniform flow rate distribution of the process streams exchanging heat in plate-fin heat exchangers is important for heat exchanger efficiency.
  • Plate-fin heat exchangers with mitered distributors are prone to flow rate maldistribution because of flow resistance variations due to differences in the length of the flow paths in the distributor feeding the main heat exchanger core.
  • changes in the density of the process fluid in the distributor can further worsen flow rate maldistribution.
  • the density of the process fluid can vary in the distributor due to differences in the change in temperature of the process fluid in the distributor, which also depends on the flow path in the distributor.
  • Plate-fin heat exchangers to which the invention relates are disclosed in EP 0 952 419 A1 , EP 0 740 119 A2 , FR 2 085 924 A1 , and US 3 860 065 A .
  • FR 2 085 924 A1 and US 3 860 065 A describe plate-fin heat exchangers with distributor sections comprising passages containing fin sections of different type including a uniquely shaped and oriented wedge section which is shaped and orientated so that fluid passing closest to the port side of the respective passage travels further in the wedge section than the fluid passing farthest from the port side.
  • the fin material of which the wedge section is constructed is selected to have a comparatively higher resistance to fluid flow therethrough per unit length than the other section(s) of the distributor. The higher flow resistance and unique shape and orientation of the wedge section counterbalances unequal pressure drops accross the distributor.
  • the present disclosure relates to plate-fin heat exchangers.
  • the present disclosure more specifically relates to an improvement in the distributor for plate-fin heat exchangers.
  • Plate-fin heat exchangers according to the invention are described in claim 1 and claim 2.
  • FR 2 085 924 discloses a heat exchanger having the features of the preamble of claims 1 and 2.
  • Claim 14 describes a process employing such a plate-fin heat exchanger.
  • the sub-claims describe advantageous further developments.
  • the distributor section may be manufactured separately from the main heat exchanger core section and jointed to the main heat exchanger core section at the face of the main heat exchanger core section.
  • the distributor section may be a mitered distributor, the first-type fin section abutting at least a portion of the second-type fin section at a junction which follows a diagonal from an intersection of the closing bar and closing bar segment to an intersection of the face of the first header and the face of the main heat exchanger core section.
  • Each third-type fin section of each passage of the first group of passages may extend through at least 20%, or at least 40% of the volume of the short flow path region (25) of the respective passage (24) in each of the claimed embodiments comprising a third-type fin section (3).
  • each third-type fin section of each passage of the first group of passages may extend from the border of each respective third-type fin section towards a junction and abut at the junction at least a portion of a fin section extending from the junction towards the face of the main heat exchanger core section.
  • each fourth-type fin section of each passage of the first group of passages may extend through at least 20%, or at least 40% of the volume of the short flow path region of the respective passage.
  • each fourth-type fin section of each passage of the first group of passages may extend from the border of each respective fourth-type fin section towards a junction and abut at the junction at least a portion of a fin section extending from the junction towards the face of the distributor section.
  • each fourth-type fin section of each passage of the first group of passages may extend from the border of each respective fourth-type fin section towards a junction and abut at the junction at least a portion of at least one fin section of a type different from the fourth type.
  • Fig. 6 shows a distributor of an embodiment that is not claimed but serves for understanding the claimed invention.
  • the term "and/or" placed between a first entity and a second entity includes any of the meanings of (1) only the first entity, (2) only the second entity, and (3) the first entity and the second entity.
  • the term "and/or” placed between the last two entities of a list of 3 or more entities means at least one of the entities in the list including any specific combination of entities in this list.
  • “A, B and/or C” has the same meaning as “A and/or B and/or C” and comprises the following combinations of A, B and C: (1) only A, (2) only B, (3) only C, (4) A and B and not C, (5) A and C and not B, (6) B and C and not A, and (7) A and B and C.
  • phrases "at least one of" preceding a list of features or entities means one or more of the features or entities in the list of entities, but not necessarily including at least one of each and every entity specifically listed within the list of entities and not excluding any combinations of entities in the list of entities.
  • “at least one of A, B, or C” (or equivalently “at least one of A, B, and C” or equivalently “at least one of A, B, and/or C") has the same meaning as “A and/or B and/or C" and comprises the following combinations of A, B and C: (1) only A, (2) only B, (3) only C, (4) A and B and not C, (5) A and C and not B, (6) B and C and not A, and (7) A and B and C.
  • indirect heat transfer is heat transfer from one stream to another stream where the streams are not mixed together. Indirect heat transfer includes, for example, transfer of heat from a first fluid to a second fluid in a heat exchanger where the fluids are separated by plates or tubes.
  • directional terms may be used in the specification and claims to describe portions of the present invention (e.g., upper, top, lower, bottom, left, right, etc.). These directional terms are merely intended to assist in describing and claiming the invention and are not intended to limit the invention in any way.
  • reference numerals that are introduced in the specification in association with a drawing figure may be repeated in one or more subsequent figures without additional description in the specification in order to provide context for other features.
  • FIG. 1 is a general representation of a plate-fin heat exchanger.
  • a first (warm) stream is passed from header 30 into distributor section 20, from distributor section 20 through main heat exchanger core section 10 to distributor section 50, and from distributor section 50 to header 60.
  • a second (cold) stream is passed from header 70 into distributor section 50, from distributor section 50 through the main heat exchanger core section 10 to distributor section 20, from distributor section 20 to header 40.
  • the first (warm) stream is shown to pass through the plate-fin heat exchanger in a flow direction countercurrent to the second (cold) stream.
  • the respective fin section of each heat transfer passage of the second group of heat transfer passages 56 comprises a plurality of fins defining a plurality of channels in the respective fin section of each heat transfer passage of the second group of heat transfer passages 56.
  • Each of the first group of heat transfer passages 54 and the second group of heat transfer passages 56 of the main heat exchanger core section 10 may comprise any known fin style, for example, straight fins, perforated fins, serrated fins, and herringbone fins. The various fin styles are illustrated in FIG. 2 .
  • the first group of heat transfer passages 54 may be configured to transport a first (warm) stream from distributor section 20 to distributor section 50 and give up heat to the second (cold) stream.
  • the second group of heat transfer passages 56 may be configured to transport a second (cold) stream from distributor section 50 to distributor section 20 and receive heat from the first (warm) stream.
  • the plate-fin heat exchanger may be configured to pass the first (warm) stream through the first group of heat transfer passages 54 in countercurrent flow relationship to the second (cold) stream passed through the second group of heat transfer passages 56.
  • the first (warm) stream may be air and the second (cold) stream may be a nitrogen-rich waste gas from a distillation column.
  • the first group of heat transfer passages 54 and the second group of heat transfer passages 56 are configured to provide indirect heat transfer between the first (warm) stream and the second (cold) stream.
  • Each heat transfer passage in the first group of heat transfer passages 54 may be adjacent to at least one heat transfer passage in the second group of heat transfer passages 56.
  • Each heat transfer passage in the second group of heat transfer passages 56 may be adjacent to at least one heat transfer passage in the first group of heat transfer passages 54.
  • the plate-fin heat exchanger comprises a distributor section 20 abutting the main heat exchanger core section 10 along a face 11 of the main heat exchanger core section 10.
  • the distributor section 20 comprises a plurality of parting sheet segments 22.
  • the plurality of parting sheet segments 22 are disposed in fixed, substantially parallel, spaced relation with each other.
  • the plurality of parting sheet segments 22 define a first group of passages 24 and a second group of passages 26.
  • Each passage 24 in the first group of passages 24 may be adjacent to at least one passage 26 of the second group of passages 26.
  • Each passage in the second group of passages 26 may be adjacent to at least one passage of the first group of passages 24.
  • Each passage of the first group of passages 24 of the distributor section 20 is in fluid communication with a respective heat transfer passage of the first group of heat transfer passages 54 of the main heat exchanger core 10.
  • Each passage of the second group of passages 26 of the distributor section 20 is in fluid communication with a respective heat transfer passage of the second group of heat transfer passages 56 of the main heat exchanger core 10.
  • the first group of passages 24 abuts the main heat exchanger core section 10 along a face 11 of the main heat exchanger core section 10.
  • Each passage of the first group of passages 24 is in fluid communication with a respective heat transfer passage of the first group of heat transfer passages 54 of the main heat exchanger core section 10.
  • Each passage of the first group of passages 24 is closed on a side opposite the main heat exchanger core section 10 by a respective closing bar 12.
  • Each respective closing bar 12 has a fin-side facing surface having a length, L W .
  • each passage of the first group of passages 24 has a long flow path region 15 between the parting sheet segments 22 of each passage of the first group of passages 24 and a short flow path region 25 between the parting sheet segments 22 of each passage of the first group of passages 24, so-called because the distance traveled by the process fluid in the distributor section for the long flow path region 15 is greater than the distance traveled in the short flow path region 25.
  • the distance that the process fluid needs to travel in the distributor section 20 from the header 30 to the main heat exchanger core 10 impacts the flow rate distribution of the process fluid in the main heat exchanger core 10.
  • the long flow path region 15 for each passage of the first group of passages 24 is defined by the union of a first cuboid and a second cuboid.
  • a "cuboid” is a 3-dimensional shape that has six rectangular faces at substantially right angles to each other.
  • the first cuboid extends normal to the respective closing bar 12 from the fin-side facing surface of the respective closing bar 12 to a position 50% of the distance along the face 31 of the first header 30 from the respective closing bar 12 towards the face 11 of the main heat exchanger core section 10.
  • the second cuboid extends normal to the respective closing bar segment 32 to a position 50% of the distance along the face 11 of the main heat exchanger core section 10 from the respective closing bar segment 32 towards the face 31 of the first header 30.
  • the long flow path region 15 in FIG. 3 resembles an "L" rotated 90° clockwise.
  • the short flow path region 25 for each passage of the first group of passages 24 is bounded by the long flow path region 15, a portion of the face 31 of the first header 30, and a portion of the face 11 of the main heat exchanger core section 10.
  • the long flow path region 15 contains at least a portion of two or more fin sections extending throughout the long flow path region 15 including a first-type fin section 1 and a second-type fin section 2.
  • the term "type" is used to distinguish between fin sections composed of fins having one or more different characteristics, such as fin style and/or free flow area and/or fin density and/or hydraulic diameter, etc.
  • the first-type fin section 1 may have herringbone fins with a first fin density that is different from the second-type fin section 2 having herringbone fins with a second fin density that is different than the first fin density.
  • the long flow path region 15 of each passage of the first group of passages 24 may contain a portion or all of one or more other fin sections, for example, a third-type fin section, in addition to a portion or all of the first-type fin section 1 and a portion or all of the second-type fin section 2 as shown in FIGS. 8 and 10 .
  • each passage of the first group of passages 24 contains a portion or all of one or more other fin sections in addition to a portion or all of the respective first-type fin section 1 and a portion or all of the respective second-type fin section 2
  • the respective first-type fin section 1 and the respective second-type fin section 2 in combination may extend through at least 50%, or at least 75%, or at least 90% of the volume of the long flow path region 15 of the respective passage 24.
  • FIG. 8 shows the first-type fin section 1 and the second-type fin section 2 in combination extending through greater than 90% of the volume of the long flow path region 15, with third-type fin section 3 extending through less than 10% of the volume of the long flow path region 15.
  • Fin sections of different types are designated as first-type fin section, second-type fin section, third-type fin section, etc.
  • a fin section of a certain type, for example, the first-type fin section 1 is composed of an arrangement of fins having at least one structural characteristic effecting fluid flow and/or heat transfer which differs from the same structural characteristic of a fin section of another type, for example, the second-type fin section 2, and an optional fin section of another type.
  • the at least one structural characteristic in which a fin section of one type, e.g. the first-type fin section 1, differs from a fin section of another type, e.g. the second-type fin section 2 or an optional third-type fin section may be fin style, examples of which are illustrated in FIG. 2 , free flow area, fin density, hydraulic diameter, etc.
  • the respective fin sections of different types may differ one from the other in only one or in two or three or more characteristics.
  • the short flow path region 25 of each passage of the first group of passages 24 may contain a portion of the first-type fin section 1.
  • each passage of the first group of passages 24 may contain a portion of the second-type fin section 2.
  • the junction 9 may follow a diagonal from the intersection of the closing bar 12 and closing bar segment 32 to the intersection of the face 31 of the first header 30 and the face 11 of the main heat exchanger core section 10.
  • the distributor section 20 is a so-called mitered distributor.
  • the first-type fin section 1 comprises a plurality of fins defining a plurality of channels in the first-type fin section 1.
  • the first-type fin section 1 of each passage of the first group of passages abuts the face 31 of the first header 30 along a border 33 of each respective first-type fin section 1.
  • Each first-type fin section has a second border 7.
  • the second border 7 of each respective first-type fin section may be parallel with the respective closing bar 12 of each passage of the first group of passages 24.
  • a second border 7 of the first-type fin section 1 "parallel" with the closing bar 12 means that the spacing between the closing bar 12 and the border 7 of the first-type fin section 1 varies by less than 5% of L W over the length, L W , of the closing bar 12.
  • the first-type fin section 1 of each passage of the first group of passages 24 has a longitudinal direction.
  • the longitudinal direction of a fin section corresponds to the lengthwise direction of the fins.
  • the longitudinal direction of a fin section is perpendicular to the fin density direction.
  • the fin section forms channels where the path of least resistance for the process fluid is in the longitudinal direction.
  • the longitudinal direction for each fin style is shown in FIG. 2 .
  • the longitudinal direction of the first-type fin section 1 may be aligned parallel with the respective closing bar 12 of each passage of the first group of passages 24.
  • a longitudinal direction aligned "parallel" with the closing bar 12 means that the distance between a planar segment perpendicular to the parting sheets in the longitudinal direction and the closing bar 12 varies by less than 5% of L W over the length, L W , of the closing bar 12.
  • Each second-type fin section 2 comprises a plurality of fins defining a plurality of channels in each respective second-type fin section 2.
  • the second-type fin section 2 of each passage of the first group of passages 24 abuts the face 11 of the main heat exchanger core section 10 along a border 13 of each respective second-type fin section 2.
  • the second-type fin section 2 of each passage of the first group of passages 24 and the respective fin section of the respective heat transfer passage of the first group of heat transfer passages 54 that are in fluid communication with the respective passage of the first group of passages 24 are separate pieces of fin section.
  • One or more fin section characteristics of the second-type fin section 2 of each passage of the first group of passages 24 may be different than a corresponding fin section characteristic of the bordering fin section of heat transfer passage of the main heat exchanger core.
  • the one or more fin section characteristics may be selected from the group consisting of fin style, free flow area, fin density, fin thickness, and hydraulic diameter.
  • the overall efficiency of the plate-fin heat exchanger can be improved by using fin characteristics for the distributor section that are different than the fin characteristics of the main heat exchanger core.
  • the criteria for selection of the fin characteristics of the distributor section may be tilted towards improved flow distribution and improved heat transfer while the criteria for selection of the fin characteristics for the main heat exchanger core section may be tilted towards improved heat transfer. The result is improved overall heat transfer performace of the plate-fin heat exchanger.
  • Each second-type fin section 2 has a second border 8.
  • the second border 8 of each respective second-type fin section may be parallel with the respective closing bar segment 32 of each passage of the first group of passages 24.
  • a second border 8 of the second-type fin section 2 "parallel" with the closing bar segment 32 means that the spacing between the closing bar segment 32 and the border 8 of the second-type fin section 2 varies by less than 5% of L H over the length, L H , of the closing bar segment 32.
  • the second-type fin section 2 of each passage of the first group of passages 24 has a longitudinal direction.
  • the longitudinal direction of the second-type fin section 2 may be aligned parallel with the respective closing bar segment 32 of each passage of the first group of passages 24.
  • a longitudinal direction aligned "parallel" with the closing bar segment 32 means that the distance between a planar segment perpendicular to the parting sheets in the longitudinal direction and the closing bar segment 32 varies by less than 5% of L H over the length, L H , of the closing bar segment 32.
  • the second-type fin section 2 of each passage 24 is different than the first-type fin section 1 of each passage, meaning that the second-type fin section 2 has at least one different characteristic than the first-type fin section 1, such as fins of a different style, hydraulic diameter, free flow area per unit width per passage, or heat transfer area per unit width per unit length per passage.
  • Values for each of the parameters, f 1 , f 2 , j 1 , j 2 , D h,1 , D h,2 , A f,1 , A f,2 A s,1 , and A s,1 are available from vendors/manufacturers of commercially available fin types with these values preferred for designing the apparatus. In case values are not available from vendors/manufacturers, values may be determined from standard testing methods, such as described for example, in Kays, W.M., and London, A.L., Heat Transfer and Flow Friction Characteristics of Some Compact Heat Exchanger Surfaces - Part I: Test System and Procedure, Trans. ASME, Vol. 72, pp.
  • the friction factor, f , and j -factor are dimensionless numbers having values that are a function of Reynolds number.
  • the Reynolds number, Re is also a dimensionless number and is defined, ⁇ vD h ⁇ , where ⁇ is the density of the fluid, v is the velocity of the fluid in the fin channels, D h is the hydraulic diameter of the fin section channels, and ⁇ is the viscosity of the fluid.
  • Consistent units are used for each of the parameters so that the friction factor parameter ratio and the j-factor parameter ratio are dimensionless. If D h,1 has units of m, then D h,2 , has units of m. If A f,1 has units of m 2 /m, then A f,2 has units of m 2 /m. If A s,1 has units of m 2 /m/m, then A s,2 has units of m 2 /m/m.
  • first-type fin section and second-type fin section as described can be understood from the following analysis.
  • the flow distribution among the fin channels is determined by the flow resistance, or the pressure drop in each fin channel.
  • G mass flux
  • M mass flow rate through one passage
  • a f ′ is the free flow area per passage
  • the first (warm) stream enters the heat exchanger from the header (30) and exits the heat exchanger from the header (60).
  • Total flow path through the distributor (20) and distributor (50) is the same in different fin channels.
  • the fluid density is much lower in the distributor (20) than the distributor (50). Therefore, the flow resistance in the fin channels which have long flow path in the distributor (20) is higher than the fin channels which have short flow path in the distributor (20). To reduce such flow resistance variation in the fin channels, the flow resistance in long flow path in the distributor (20) needs to be reduced.
  • the temperature of the fluid is higher in the first-type fin section than the second-type fin section.
  • the density of the fluid is lower in the first-type fin section than the second-type fin section.
  • the flow resistance is more pronounced in the first-type fin section than the second-type fin section. Therefore, low resistance fins should be used in the first-type fin section.
  • F is adopted as a criterion for selecting fins in the first-type and second-type fin sections.
  • F is adopted as a criterion for selecting fins in the first-type and second-type fin sections.
  • fin characteristics in the first-type fin section are the same as the fin characteristics in the second-type fin section.
  • fin characteristics in the first-type fin section provide a lower flow resistance than the fin characteristics in the second-type fin section.
  • heat transfer in the distributor section can also cause uneven fluid density in the different sections, which compounds the flow resistance variation in the fin channels.
  • the second (cold) stream enters the heat exchanger from the header (70) and exists the heat exchanger from the header (40).
  • the second (cold) stream exchanges heat with the first (warm) stream.
  • the first (warm) stream temperature in the first-type fin section is higher than the first (warm) stream temperature in the second-type fin section. Therefore, the driving force for exchanging heat between the first (warm) stream and the second (cold) stream in the first-type fin section is greater than the driving force for exchanging heat between the first (warm) stream and the second (cold) stream in the second fin-type section.
  • Such uneven driving force results in uneven temperature and fluid density in fin channels of the second (cold) stream, and leads to flow maldistribution.
  • J is adopted as another criterion for selecting fins in the first-type and second-type fin sections.
  • J is equal to 1
  • fin characteristics in the first-type fin section are the same as the fin characteristics in the second-type fin section.
  • J is less than 1
  • fins in the first-type fin section have a lower hA than in the second-type fin section.
  • the short flow path region 25 of each passage of the first group of passages 24 may contain at least a portion of a third-type fin section 3.
  • Each third-type fin section 3 comprises a plurality of fins defining a plurality of channels in each respective third-type fin section 3.
  • Each third-type fin section 3 of each passage of the first group of passages 24 abuts the face 31 of the first header 30 along a border 34 of each respective third-type fin section 3.
  • Each third-type fin section 3 of each passage of the first group of passages 24 extends from the border 34 up to the junction 9 and abuts at the junction 9 at least a portion of a fin section extending from the junction 9 towards the face 11 of the main heat exchanger core section 10.
  • Each third-type fin section 3 of each passage of the first group of passages 24 may abut at junction 9 at least a portion of at least one fin section of a type different from the third type such as, for example, a portion of the second-type fin section 2 in FIGS. 7 and 8 and a portion of a fourth-type fin section 4 in FIGS. 9 and 10 .
  • the respective third-type fin section 3 may extend through at least 20%, or at least 40% of the volume of the short flow path region 25 of the respective passage 24.
  • FIGS. 7 , 9 and 10 show the third-type fin section 3 extending through about 23% of the volume of the short flow path region 25.
  • FIG. 8 shows the third-type fin section 3 extending through 50% of the volume of the short flow path region 25.
  • Consistent units are used for each of the parameters so that the friction factor parameter ratio is dimensionless. If D h,1 has units of m, then D h,3 , has units of m. If A f,1 has units of m 2 /m, then A f,3 has units of m 2 /m.
  • the flow path in the first-type fin section is longer than the flow path in the third-type fin section.
  • the flow resistance in the first-type fin section is more significant than the flow resistance in the third-type fin section. Therefore, lower resistance fins should be used in the first-type fin section than in the third-type fin section.
  • the fin characteristics in the first-type fin section are the same as the fin characteristics in the third-type fin section.
  • the short flow path region 25 of each passage of the first group of passages 24 may contain at least a portion of a fourth-type fin section 4.
  • Each fourth-type fin section 4 comprises a plurality of fins defining a plurality of channels in each respective fourth-type fin section 4.
  • Each fourth-type fin section 4 of each passage of the first group of passages 24 abuts the face 11 of the main heat exchanger core section 10 along a border 14 of each respective fourth-type fin section 4.
  • Each fourth-type fin section 4 of each passage of the first group of passages 24 extends from the border 14 up to the junction 9 and abuts at the junction 9 at least a portion of a fin section extending from the junction 9 towards the face 31 of the distributor section 20.
  • Each fourth-type fin section 4 of each passage of the first group of passages 24 may abut at junction 9 at least a portion of at least one fin section of a type different from the fourth type such as, for example, a portion of the first-type fin section 1 and all of the third-type fin section 3 in FIGS. 9 and 10 .
  • the respective fourth-type fin section 4 may extend through at least 20%, or at least 40% of the volume of the short flow path region 25 of the respective passage 24.
  • FIG. 9 shows the fourth-type fin section 4 extending through about 26% of the volume of the short flow path region 25.
  • FIG. 10 shows the fourth-type fin section 4 extending through 50% of the volume of the short flow path region 25.
  • a fourth-type fin section may be present with or without the above-described third-type fin section.
  • the fourth-type fin section 4 of each passage of the first group of passages 24 and the respective fin section of the respective heat transfer passage of the first group of heat transfer passages 54 that are in fluid communication with the respective passage of the first group of passages 24 are separate pieces of fin section. Therefore, there is a break in continuity between the fourth-type fin section 4 of each passage of the first group of passages 24 and the respective fin section of the respective heat transfer passage of the first group of heat transfer passages 54 that are in fluid communication with the respective passage of the first group of passages 24.
  • the benefit of the having separate pieces of fin section is for ease of manufacturing. The benefit of the gap is to limit the flow restriction at the junction resulting from fin cross-sections overlapping the open area of the channels.
  • One or more fin section characteristics of the fourth-type fin section 4 of each passage of the first group of passages 24 may be different than a corresponding fin section characteristic of the bordering fin section of heat transfer passage of the main heat exchanger core.
  • the one or more fin section characteristics may be selected from the group consisting of fin style, free flow area, fin density, fin thickness, and hydraulic diameter.
  • the overall efficiency of the plate-fin heat exchanger can be improved by using fin characteristics for the distributor section that are different than the fin characteristics of the main heat exchanger core.
  • Consistent units are used for each of the parameters so that the j-factor parameter ratio is dimensionless. If A f,2 has units of m 2 /m, then A f,4 has units of m 2 /m. If A s,2 has units of m 2 /m/m, then A s,4 has units of m 2 /m/m.
  • the second (cold) stream enters the heat exchanger from header 70 and exits the heat exchanger from header 40.
  • the second (cold) stream exchanges heat with the first (warm) stream.
  • the first (warm) stream temperature in the fourth-type fin section is higher than the first (warm) stream temperature in the second-type fin section. Therefore, the driving force for exchanging heat between the first (warm) stream and the second (cold) stream in the fourth-type fin section is higher than the driving force for exchanging heat between the first (warm) stream and the second (cold) stream in the second-type fin section.
  • Such uneven driving force results in uneven temperature and fluid density in the fin channels of the second (cold) stream, and leads to flow maldistribution.
  • fin characteristics in the second-type fin section are the same as the fin characteristics in the fourth-type fin section.
  • the plate-fin heat exchanger also comprises a second header 40 abutting and in fluid communication with the second group of passages 26 of the distributor section 20.
  • the second group of passages 26 of the distributor section 20 abut along face 41 of the second header 40.
  • Each passage of the second group of passages 26 abuts the main heat exchanger core section 10 along face 11 of the main heat exchanger core section 10.
  • Each passage of the second group of passages 26 is closed on one side by a respective closing bar segment 38 on the side adjacent the first header 30 and a respective closing bar segment 36 on the side opposite the first header 30.
  • the specific design of the fin sections in the passages of the second group of passages 26 of the distributor section 20 has been determined to be less important than the design of the fin sections in the passages for the first group of passages 24.
  • the fins in the second group of passages 26 of the distributor section 20 may be the same type of fins, having the same fin characteristics as the fins in the corresponding heat transfer passages of the main heat exchanger core 10.
  • the fins in the second group of passages 26 of the distributor section 20 may have different fin characteristics than the fins in the heat transfer passages of the main heat exchanger core 10.
  • a side header 40b may be used as shown in FIG. 12 , requiring a mitered design.
  • the fin sections 42 and 43 in the passages of the second group of passages 26 can have the same type of fins, having the same characteristics such that the friction factor parameter ratio is equal to 1 and the j-factor parameter ratio is equal to 1.
  • the description provided for the first-type fin section and the second-type fin section applies mutatis mutandis to fin section 43 and fin section 42, respectively.
  • the plate-fin heat exchanger comprises a distributor section 50 abutting the main heat exchanger core section 10 along a face 51 of the main heat exchanger core section 10.
  • the distributor section 50 comprises a plurality of parting sheet segments 72.
  • the plurality of parting sheet segments 72 are disposed in fixed, substantially parallel, spaced relation with each other.
  • the plurality of parting sheet segments 72 define a first group of passages 74 of the distributor section 50 and a second group of passages 76 of the distributor section 50.
  • Each passage 74 in the first group of passages 74 may be adjacent to at least one passage of the second group of passages 76.
  • Each passage 76 in the second group of passages 76 may be adjacent to at least one passage of the first group of passages 74.
  • the plate-fin heat exchanger comprises a header 60 abutting and in fluid communication with the first group of passages 74 of the distributor section 50 along a face 81 of the header 60.
  • Each passage of the first group of passages 74 is closed on a side opposite the header 60 by a respective closing bar segment 82.
  • the first group of passages 74 of distributor section 50 abuts the main heat exchanger core section 10 along a face 51 of the main heat exchanger core section 10.
  • Each passage of the first group of passages 74 is closed on a side opposite the main heat exchanger core section 10 by a respective closing bar 62.
  • the second group of passages 76 of distributor section 50 abut along face 61 of header 70.
  • Each passage of the second group of passages 76 of distributor section 50 abuts the main heat exchanger core section 10 along face 51 of the main heat exchanger core section 10.
  • Each passage of the second group of passages 76 is closed on one side by a respective closing bar segment on the side adjacent the header 60 and a respective closing bar segment 86 on the side opposite the header 60.
  • the distributor section 50 may be constructed with fin sections according to known conventional design methods or according to the design method described herein for the distributor section 20.
  • a two-dimensional numerical model was developed to calculate coupled heat transfer and fluid flow distribution in a two-passage heat exchanger with distributors.
  • the outlet temperature of the two streams are solved with a prescribed inlet temperature for each of the two streams.
  • the heat exchanger and distributors are discretized into a mesh comprising a number of cells as shown schematically in FIGS. 16 and 17 .
  • the number of cells is chosen such that a further increase in the number of cells results in no significant change in the resulting solution.
  • FIG. 16 shows the prescribed fluid flow path for the first (warm) stream.
  • FIG. 17 shows the prescribed fluid flow path for the second (cold) stream.
  • a cell within the mesh may normally contain more than one fin channel.
  • the total mass flow rate of each stream, and the temperature and pressure at the inlet to the distributor are specified and input values in the model.
  • the physical properties of the fluid in each cell are a function of the calculated temperature and pressure in each cell.
  • a solution is calculated iteratively, solving for the temperature of the first (warm) stream and the second (cold) stream at the outlet of the opposite distributor for each respective stream.
  • the mass flow rate of each flow path, the temperature, and the pressure of each cell are updated for each iteration based on the equations described above.
  • the fin characteristics in the first-type fin section are the same as the fin characteristics in the second-type fin section, representative of prior art designs.
  • the heat exchanger length is set at 3.3 m.
  • the resulting bulk temperature for the first (warm) stream discharged to header 60 is -174.59°C.
  • the resulting bulk temperature for the second (cold) stream discharged to the header 40 is 20.62°C.
  • the bulk temperature is calculated in the normal way using the mass flow rate to provide the mass averaged bulk value.
  • the heat exchanger length is adjusted until the same bulk temperature is obtained for the first (warm) stream discharged to header 60 and the same bulk temperature is obtained for the second (cold) stream discharge to header 40.
  • the heat exchanger length is adjusted until the same bulk temperature is obtained for the first (warm) stream discharged to header 60 and the same bulk temperature is obtained for the second (cold) stream discharge to header 40.
  • the fin characteristics of the first-type fin section and the second-type fin section are the same as in case 3.
  • a third-type fin section is added like shown in FIG. 7 .
  • the third-type fin section extends for a length of 20% of L H from the face 11 of the heat exchanger core section 10 towards the closing bar 12.
  • the heat exchanger length, L HX is adjusted until the same bulk temperature is obtained for the first (warm) stream discharged to header 60 and the same bulk temperature is obtained for the second (cold) stream discharged to header 40.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP18153523.8A 2018-01-25 2018-01-25 Distributor for plate-fin heat exchanger Active EP3517878B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL18153523T PL3517878T3 (pl) 2018-01-25 2018-01-25 Dystrybutor dla płytowo-żebrowego wymiennika ciepła
EP18153523.8A EP3517878B1 (en) 2018-01-25 2018-01-25 Distributor for plate-fin heat exchanger
ES18153523T ES2837323T3 (es) 2018-01-25 2018-01-25 Distribuidor para intercambiador de calor de placas y aletas

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18153523.8A EP3517878B1 (en) 2018-01-25 2018-01-25 Distributor for plate-fin heat exchanger

Publications (2)

Publication Number Publication Date
EP3517878A1 EP3517878A1 (en) 2019-07-31
EP3517878B1 true EP3517878B1 (en) 2020-11-04

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EP18153523.8A Active EP3517878B1 (en) 2018-01-25 2018-01-25 Distributor for plate-fin heat exchanger

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EP (1) EP3517878B1 (es)
ES (1) ES2837323T3 (es)
PL (1) PL3517878T3 (es)

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Publication number Priority date Publication date Assignee Title
WO2024017504A1 (en) * 2022-07-21 2024-01-25 Nuovo Pignone Tecnologie - S.R.L. A heat exchanger with a vapor-liquid distributor
CN116680838B (zh) * 2023-07-27 2024-04-26 东莞市鹏锦机械科技有限公司 一种板翅式换热器的传热计算方法
CN117723327B (zh) * 2023-12-07 2024-06-18 中国科学院近代物理研究所 一种2k负压可视化换热器测试平台、系统及使用方法

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Publication number Priority date Publication date Assignee Title
CA902601A (en) * 1972-06-13 Trane Company Of Canada Limited Distributor for plate type heat exchangers having end headers
CA929929A (en) * 1970-04-08 1973-07-10 Trane Company Of Canada Limited Distributor for plate type heat exchangers having side headers
US3860065A (en) * 1970-04-08 1975-01-14 Trane Co Distributor for plate type heat exchanger having side headers
US5730209A (en) * 1995-04-28 1998-03-24 Air Products And Chemicals, Inc. Defrost and liquid distribution for plate-fin heat exchangers
CA2268999C (en) * 1998-04-20 2002-11-19 Air Products And Chemicals, Inc. Optimum fin designs for downflow reboilers
CN102792116B (zh) * 2010-03-08 2015-04-08 乔治洛德方法研究和开发液化空气有限公司 热交换器
JP2014161777A (ja) * 2013-02-22 2014-09-08 Sumitomo Precision Prod Co Ltd 触媒反応器及び触媒反応器の製造方法

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Title
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PL3517878T3 (pl) 2021-05-04
ES2837323T3 (es) 2021-06-30

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