CN110081742A - Distributor for plate-fin heat exchanger - Google Patents

Distributor for plate-fin heat exchanger Download PDF

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Publication number
CN110081742A
CN110081742A CN201910067514.1A CN201910067514A CN110081742A CN 110081742 A CN110081742 A CN 110081742A CN 201910067514 A CN201910067514 A CN 201910067514A CN 110081742 A CN110081742 A CN 110081742A
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CN
China
Prior art keywords
channel
group
finless parts
type
heat exchanger
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Granted
Application number
CN201910067514.1A
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Chinese (zh)
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CN110081742B (en
Inventor
徐方
D.M.赫伦
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Air Products and Chemicals Inc
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Air Products and Chemicals Inc
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • 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
    • F28D9/0068—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 with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04151—Purification and (pre-)cooling of the feed air; recuperative heat-exchange with product streams
    • F25J3/04187—Cooling of the purified feed air by recuperative heat-exchange; Heat-exchange with product streams
    • F25J3/04218—Parallel arrangement of the main heat exchange line in cores having different functions, e.g. in low pressure and high pressure cores
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/0446—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using the heat generated by mixing two different phases
    • F25J3/04466—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using the heat generated by mixing two different phases for producing oxygen as a mixing column overhead gas by mixing gaseous air feed and liquid oxygen
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04636—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a hybrid air separation unit, e.g. combined process by cryogenic separation and non-cryogenic separation techniques
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04763—Start-up or control of the process; Details of the apparatus used
    • F25J3/04866—Construction and layout of air fractionation equipments, e.g. valves, machines
    • F25J3/04896—Details of columns, e.g. internals, inlet/outlet devices
    • F25J3/04903—Plates or trays
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04763—Start-up or control of the process; Details of the apparatus used
    • F25J3/04866—Construction and layout of air fractionation equipments, e.g. valves, machines
    • F25J3/04896—Details of columns, e.g. internals, inlet/outlet devices
    • F25J3/04927—Liquid or gas distribution devices
    • 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
    • F25J5/005—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 in a reboiler-condenser, e.g. within a column
    • 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
    • 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
    • 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
    • F28F3/027—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 with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Plate-fin heat exchanger has the dispenser designs of beveling, for improving the fluid flow distribution for passing through plate-fin heat exchanger, to improve efficiency of heat exchanger.The part of distributor has different fin types, provides improved fluid by heat exchanger and distributes.The fin type of the different piece of distributor is than the j- factor parameter with different fin types based on coefficient of friction parameter than carrying out selection.

Description

Distributor for plate-fin heat exchanger
Background technique
Plate-fin heat exchanger is well-known in chemical process industry (CPI), including air-separating technology.
The even velocity of flow distribution that the technique stream of heat is exchanged in plate-fin heat exchanger is important heat exchanger efficiency.
The difference of flow path length of the plate-fin heat exchanger with mitered distributor due to supplying main heat exchanger core in distributor It is different and flow resistance is caused to change, therefore it is easy to velocity flow profile unevenness.Other than the flow resistance variation in distributor, distribution The variation of process fluid density in device can also further deteriorate velocity flow profile unevenness.Due to the temperature of the process fluid in distributor The difference of variation is spent, the density of process fluid can change in distributor, this also depends on the flow path in distributor.
Industrially wish that plate-fin heat exchanger has improved heat exchanger efficiency, i.e., lesser heat exchanger offer is changed with larger The identical thermic load of hot device.
Industry needs distributor for plate-fin heat exchanger, to improve the distribution of the process fluid flow in heat exchanger core.
Summary of the invention
The present invention relates to plate-fin heat exchangers.The present invention more particularly relates to changing for the distributor of plate-fin heat exchanger Into.
As described below, plate-fin heat exchanger has several aspects.Hereinafter, specific aspect of the invention is outlined.Bracket The appended drawing reference of middle setting and expression refer to the example embodiment being below with reference to the accompanying drawings explained further.However, appended drawing reference and Expression is merely illustrative, and this aspect is not limited to any specific components or feature of example embodiment.These aspects can To be expressed as claim, wherein the appended drawing reference and expression that are arranged in bracket are omitted or in due course by other tables Show.
1. plate-fin heat exchanger of aspect, comprising:
Main heat exchanger core segment (10) includes first group of heat transfer path (54) and second group of heat transfer path (56), first group of biography Each heat transfer path of the passage of heat (54) includes corresponding finless parts, and each heat transfer of second group of heat transfer path (56) is logical Road includes corresponding finless parts；
The dispenser portion (20) of main heat exchanger core segment (10) is abutted along the face (11) of main heat exchanger core segment (10), Dispenser portion (20) includes:
Multiple demarcation plate parts (22), relationship is arranged multiple demarcation plate parts (22) at regular intervals, wherein described more A demarcation plate part (22) limits first group of channel (24) and second group of channel (26)；
First head (30), the face (31) along the first head (30) is adjacent and is in fluid communication with first group of channel (24), In first group of channel (24) each channel the first head (30) opposite side by be closed accordingly bar part (32) be closed；
Second head (40), adjoining are simultaneously in fluid communication with second group of channel (26) of dispenser portion (20)；
Wherein first group of channel (24) is along the adjacent main heat exchange in the face (11) of the main heat exchanger core segment (10) Device core segment (10), wherein first group of each channel of first group of channel (24) and the main heat exchanger core segment (10) The corresponding heat transfer path of heat transfer path (54) is in fluid communication, and wherein each channel of first group of channel (24) described The side on main heat exchanger core segment (10) opposite is closed by corresponding closed rod (12)；
Wherein each channel of first group of channel (24) is limited by the first cuboid and combining for the second cuboid First group of channel (24) each channel divider plate portions point between there is long flow path region (15), described the One cuboid extends to such position perpendicular to corresponding closed rod (12) from the fin side of corresponding closed rod (12), should Position is the face (31) along first head (30) from corresponding closed rod (12) towards the main heat exchanger core segment (10) the 50% of the distance in face (11), and second cuboid extends to this perpendicular to corresponding closure bar part (32) The position of sample, the position are to be closed bar part (32) direction from corresponding along the face (11) of the main heat exchanger core segment (10) The 50% of the distance in the face (31) of first head (30)；
Wherein each channel of first group of channel (24) is by long flow path region (15), first head (30) a part in the face (11) of a part and main heat exchanger core segment (10) in face (31) define described first There is short flow path region (25) between the divider plate portions point in each channel of group channel (24)；
Wherein the stream by the length is contained in the flow path region of the length in each channel of first group of channel (24) At least part for two or more finless parts that dynamic passage zone extends, including first kind finless parts (1) and the Two type finless parts (2), at least part of the first kind finless parts (1) and the Second Type finless parts (2) at least part abuts against at boundary (9), and the first kind finless parts (1) are included in the first kind fin Multiple fins in multiple channels are partially limited in (1), and the Second Type finless parts (2) are included in the Second Type Multiple fins in multiple channels are limited in finless parts (2)；
Wherein the first kind finless parts (1) in each channel of the first kind channel (24) are along each corresponding The face (31) of adjacent first head (30) in the boundary (33) of one type finless parts (1)；
Wherein the Second Type finless parts (2) in each channel of first group of channel (24) are along each corresponding The face (11) of the adjacent main heat exchanger core segment (10) in the boundary (13) of two type finless parts (2), wherein described first group The Second Type finless parts (2) in each channel in channel (24) and connect with the respective channel fluid of first group of channel (24) Continuity between the corresponding finless parts of the respective heat transfer path of first group of logical heat transfer path (54) is interrupted；
The wherein first kind finless parts (1) and Second Type fin part in each channel of first group of channel (24) Divide (2) that there is corresponding coefficient of friction parameter ratioWhereinWherein
The wherein first kind finless parts (1) and Second Type fin part in each channel of the first kind channel (24) Divide (2) that there is corresponding j- factor parameter ratioWhereinOrWherein
Wherein
f1It is the first kind fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (1) fin corresponding coefficient of friction,
f2It is the Second Type fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (2) fin corresponding coefficient of friction,
j1It is the first kind fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (1) fin the corresponding j- factor,
j2It is the Second Type fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (2) fin the corresponding j- factor,
Dh,1It is the corresponding hydraulic diameter of the first kind finless parts (1) in each channel of first group of channel (24),
Dh,2It is the corresponding hydraulic diameter of the Second Type finless parts (2) in each channel of first group of channel (24),
Af,1It is the every of each channel of the first kind finless parts (1) in each channel of first group of channel (24) The corresponding free-flowing area of a unit width,
Af,2It is the every of each channel of the Second Type finless parts (2) in each channel of first group of channel (24) The corresponding free-flowing area of a unit width,
As,1It is the every of each channel of the first kind finless parts (1) in each channel of first group of channel (24) The corresponding heat transfer area of each unit width of a unit length,
As,2It is the every of each channel of the Second Type finless parts (2) in each channel of first group of channel (24) The corresponding heat transfer area of each unit width of a unit length,
Wherein consistent unit is used for Dh,1、Dh,2、Af,1、Af,2、As,1And As,2Each of.
The plate-fin heat exchanger according to aspect 1 of aspect 2., wherein each channel of first group of channel (24) One or more finless parts features of Second Type finless parts (2) are different from the with the main heat exchanger core segment (10) First group of each channel for first group of channel (24) that the corresponding heat transfer path of one group of heat transfer path (54) is in fluid communication The corresponding finless parts feature of the corresponding finless parts of each heat transfer path of heat transfer path (54).
The plate-fin heat exchanger according to aspect 2 of aspect 3., wherein one or more finless parts features are selected from fin Formula flows freely area, fin density, fin thickness and hydraulic diameter.
The plate-fin heat exchanger according to any one of aspect 1 to 3 of aspect 4., wherein plate-fin heat exchanger is configured as Made with the counter-current flow relationship for passing through second group of heat transfer path (56) with second first-class across first group of heat transfer Channel (54).
Plate-fin heat exchanger described in 5. aspect 1 of aspect, wherein the second of each corresponding first kind finless parts (1) Boundary (7) is parallel with respective closed bar (12) of each respective channel of first group of channel (24).
The plate-fin heat exchanger according to any one of aspect 1 to 5 of aspect 6., wherein each of first group of channel (24) The first kind finless parts (1) in channel have it is longitudinal, wherein the longitudinal direction of each corresponding first kind finless parts (1) and the Respective closed bar (12) parallel alignment of each respective channel of one group of channel (24).
The plate-fin heat exchanger according to any one of aspect 1 to 6 of aspect 7., wherein each described first group corresponding The second boundary (8) of the Second Type finless parts (2) in each channel in channel (24) usually with first group of channel (24) Each respective channel respective closed bar (32) parallel alignment.
The plate-fin heat exchanger according to any one of aspect 1 to 7 of aspect 8., wherein first group of channel (24) The Second Type finless parts (2) in each channel have longitudinal direction, wherein the longitudinal direction of each corresponding Second Type finless parts (2) Usually with respective closed bar part (32) parallel alignment of each respective channel of first group of channel (24).
The plate-fin heat exchanger according to any one of aspect 1 to 8 of aspect 9., wherein first group of channel (24) The short flow path region (25) of each respective channel includes a part of corresponding first kind finless parts (1).
The plate-fin heat exchanger according to any one of aspect 1 to 9 of aspect 10., wherein first group of channel (24) is every The short flow path region (25) of a respective channel includes a part of corresponding Second Type finless parts (2).
The plate-fin heat exchanger according to any one of aspect 1 to 10 of aspect 11., wherein first group of channel (24) The short flow path region (25) in each channel contain two or more corresponding finless parts, including corresponding third class Type finless parts (3) are included in multiple fins that multiple channels are limited in corresponding third type finless parts (3), wherein institute The corresponding third type finless parts (3) in each channel in first kind channel (24) are stated along each corresponding third type fin The partially face (31) of adjacent first head (30) in the boundary (34) of (3)；
The wherein first kind finless parts (1) and third type fin part in each channel of first group of channel (24) Divide (3) that there is corresponding coefficient of friction parameter ratioWhereinOrOrWherein
Wherein
f3It is the third type fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (3) fin corresponding coefficient of friction,
Dh,3It is the corresponding hydraulic diameter of the third type finless parts (3) in each channel of first group of channel (24),
Af,3It is the every of each channel of the third type finless parts (3) in each channel of first group of channel (24) The corresponding free-flowing area of a unit width,
Wherein consistent unit is used for Dh,1、Dh,3、Af,1And Af,3Each of.
The plate-fin heat exchanger according to any one of aspect 1 to 11 of aspect 12., wherein first group of channel (24) The short flow path region (25) of each respective channel contain two or more corresponding finless parts, including corresponding the Four type finless parts (4) are included in multiple wings that multiple channels are limited in each corresponding 4th type finless parts (4) Piece, wherein the corresponding 4th type finless parts (4) in each channel in the first kind channel (24) are along each corresponding The face (11) on the boundary (14) of four type finless parts (4) adjacent main heat exchanger part (10), wherein first group of channel (24) the 4th type finless parts (4) in each channel and it is in fluid communication with the respective channel of first group of channel (24) Continuity between the corresponding finless parts of the respective heat transfer path of first group of heat transfer path (54) is interrupted；
Wherein the 4th type finless parts (4) and Second Type fin part in each channel of first group of channel (24) Divide (2) that there is corresponding j- factor parameter ratioWhereinOrOrWherein
Wherein
j4It is the 4th type fin in each channel for the first group of channel (24) assessed when Reynolds number is 3000 Partially in (4) fin the corresponding j- factor,
Af,4It is the every of each channel of the 4th type finless parts (4) in each channel of first group of channel (24) The corresponding free-flowing area of a unit width,
As,4It is the every of each channel of the 4th type finless parts (4) in each channel of first group of channel (24) The corresponding heat transfer area of each unit width of a unit length,
Wherein consistent unit is used for Af,2、Af,4、As,2And As,4Each of.
The plate-fin heat exchanger according to any one of preceding aspects of aspect 13., wherein first group of channel (24) Each channel first kind finless parts (1) one or more finless parts features be different from first group of channel (24) the correspondence finless parts feature of the Second Type finless parts (2) in each channel, and wherein one or more fins Partial Feature is selected from finned, free-flowing area, fin density, fin thickness and hydraulic diameter.
The plate-fin heat exchanger according to any one of preceding aspects of aspect 14., wherein dispenser portion (20) and main Heat exchanger core part (10) is separately manufactured, and is connected to main heat exchanger core segment at the face of main heat exchanger core segment (10) (11) (10)。
The plate-fin heat exchanger according to any one of preceding aspects of aspect 15., wherein dispenser portion (20) is oblique The distributor cut, at least part of first kind finless parts (1) adjoining Second Type finless parts (2) at boundary (9), The boundary (9) along closed rod (12) and be closed bar part (32) crosspoint diagonal line to the first head (30) face (31) and The crosspoint in the face (11) of main heat exchanger core segment (10).
Aspect 16. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 11, wherein first group Each third type finless parts (3) in each channel (24) in channel (24) extend through the short flowing of respective channel (24) At least 20% volume or at least 40% volume of passage zone (25).
Aspect 17. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 11, wherein described Each third type finless parts (3) in each channel of one group of channel (24) are from each corresponding third type finless parts (3) boundary (34) towards have a common boundary (9) extend, and abut against from boundary (9) towards the main heat exchanger core segment (10) The finless parts (2 that face (11) extends；2,4) at least part of boundary (9).
Aspect 18. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 11, wherein first group Each third type finless parts (3) in each channel in channel (24) are from each corresponding third type finless parts (3) Boundary (34) towards have a common boundary (9) extend, and abut against type and third type finless parts it is different types of at least one Finless parts (2；2,4) at least part of boundary (9).
Aspect 19. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 12, wherein first group The 4th type finless parts (4) of each of each channel in channel (24) extend through the short flow path of respective channel (24) At least 20% volume or at least 40% volume in region (25).
Aspect 20. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 12, wherein first group The 4th type finless parts (4) of each of each channel in channel (24) are from each corresponding 4th type finless parts (4) Boundary (14) is towards (9) extension of having a common boundary, and the face (31) abutted against from boundary (9) towards the dispenser portion (20) extends Finless parts at least part of boundary (9).
Aspect 21. is according to any one of preceding aspects and the plate-fin heat exchanger in conjunction with described in aspect 12, wherein first group The 4th type finless parts (4) of each of each channel in channel (24) are from each corresponding 4th type finless parts (4) Boundary abuts against at least one different types of fin of type Yu the 4th type finless parts towards (14) extension of having a common boundary The partially at least part of boundary (9) of (1,3).
A kind of method for carrying out heat exchange between second first-class of aspect 22., this method comprises:
The plate-fin heat exchanger according to any one of aspect 1 to 21 is provided；
To pass through the counter-current flow relationship of second group of heat transfer path (56) of the plate-fin heat exchanger with the second Make first-class first group of heat transfer path (54) across the plate-fin heat exchanger.
Method described in the aspect of aspect 23. 22, wherein it is described it is first-class be oxygen concentration range be 20 volume % oxygen extremely 22 volume % oxygen and nitrogen gas concn range are the first fluid of 78 volume % nitrogen to 80 volume % nitrogen, and wherein the Second-rate is the rich nitrogen waste gas stream from destilling tower.
Brief description
Fig. 1 shows the cross section of plate-fin heat exchanger.
Fig. 2 shows the fin of different-style.
Fig. 3 shows the cross section of the dispenser portion of plate-fin heat exchanger.
Fig. 4 shows the part A-A of the dispenser portion of Fig. 3 and Fig. 6.
Fig. 5 shows the part B-B of the dispenser portion of Fig. 3 and Fig. 6.
Fig. 6 shows tool, and there are two the cross sections of the dispenser portion of finless parts.
Fig. 7 shows tool, and there are three the cross sections of the dispenser portion of finless parts.
Fig. 8 shows tool, and there are three the cross sections of the dispenser portion of finless parts.
Fig. 9 shows tool, and there are four the cross sections of the dispenser portion of finless parts.
Figure 10 shows tool, and there are five the cross sections of the dispenser portion of finless parts.
Figure 11 shows the cross section of the dispenser portion with finless parts, which has and main heat exchanger core The longitudinal direction in the identical direction in the longitudinal direction of the fin in part.
Figure 12 shows tool, and there are two the cross sections of the dispenser portion of finless parts.
Figure 13 shows the cross section of the dispenser portion of plate-fin heat exchanger.
Figure 14 shows the part C-C of the dispenser portion of Figure 13.
Figure 15 shows the part D-D of the dispenser portion of Figure 13.
Figure 16 shows heat exchanger and distributor is separated into the grid and fluid flow path of the first (warm) stream.
Figure 17 shows grids and fluid flow path that heat exchanger and distributor are separated into the second (cold) stream.
Detailed description of the invention
Subsequent detailed description only provides preferred exemplary embodiment, and is not intended to be limited to the scope of the present invention, fits With property or configuration.Reality is used on the contrary, will then provide for those skilled in the art the detailed description of preferred illustrative embodiment The enabled description of existing preferred illustrative embodiment of the invention, it should be appreciated that can without departing from the case where to the function of element Various changes are carried out with arrangement, without departing from the scope of the present invention defined by claim.
When any feature being applied in the embodiment of the present invention described in description and claims, used here as The article " one " and "one" indicate one or more.This limitation unless stated otherwise, otherwise " one " and the use of "one" The meaning of single feature is not limited.Article "the" before singular or plural noun or noun phrase indicates specific special characteristic Or specific special characteristic, and depend on can have singular or plural meaning using its context.
Adjective " any " mean any number of one, some or all indiscriminately.
The term "and/or" placed between first instance and second instance includes (1) only first instance, (2) only second Entity, and any meaning of (3) first instance and second instance.In most latter two reality of the list of 3 or more entities The term "and/or" placed between body means that at least one entity in list includes any specific of the entity in the list Combination.For example, " A, B and/or C " have with " A and/or B and/or C " identical meaning, and including A, B and C with the following group Close: (1) only A, (2) only B, (3) only C, (4) A and B rather than C, (5) A and C rather than B, (6) B and C rather than A, and (7) A and B and C.
One or more features in the phrase "at least one" presentation-entity list before feature or list of entities or Entity, but include not necessarily at least one of each entity being expressly recited in list of entities, and be not excluded for list of entities Any combination of middle entity.For example, " at least one of A, B or C " (or it is equally " at least one of A, B and C " or equivalent Ground " at least one of A, B and/or C ") and " A and/or B and/or C " has the same meaning and the group including following A, B and C Close: (1) only A, (2) only B, (3) only C, (4) A and B rather than C, (5) A and C rather than B, (6) B and C rather than A, and (7) A and B and C.
Term " multiple " expression " two or more ".
As used herein, " indirect heat transfer " is that the heat transmitting of another stream is flowed to from one, is not blended in one wherein flowing It rises.Indirect heat transfer includes that heat is transmitted to second fluid from first fluid for example in heat exchanger, and wherein fluid is by plate or pipe It separates.
As it is used herein, " first ", " second ", " third " etc. are used to distinguish multiple steps and/or feature, and not Indicate the relative position in sum or time and/or space, unless expressly stated so.
In order to help to describe the present invention, can in the specification and in the claims use direction term it is of the invention to describe Partially (for example, top, top, lower part, bottom, left side, right side etc.).These direction terms are only used for helping to describe and require to protect The shield present invention, it is no intended to limit the invention in any way.In addition, in the description can in conjunction with the appended drawing reference that attached drawing introduces To be repeated in one or more subsequent drawings, without the additional description in specification, to be provided up and down for other features Text.
In the claims, letter can be used to identify claimed step (such as (a), (b) and (c)).These letters It is used to help quoting method step, it is no intended to indicate to execute the sequence of claimed step, unless and only wanting in right It asks in the range of specifically stating this sequence.
The present invention relates to plate-fin heat exchangers.The plate-fin heat exchanger of the disclosure will be described with reference to the drawings.
Fig. 1 is typicallying represent for plate-fin heat exchanger.As shown in Figure 1, the first (warm) stream is transmitted to distributor from head 30 Part 20, from dispenser portion 20 to main heat exchanger core segment 10 to dispenser portion 50, from dispenser portion 50 to head 60. Second (cold) stream enters dispenser portion 50 from head 70, passes through main heat exchanger core segment 10 to distributor from dispenser portion 50 Part 20, from dispenser portion 20 to head 40.First (warm) stream is shown to be worn along the flow direction with the second (cold) stream adverse current Cross plate-fin heat exchanger.
Plate-fin heat exchanger includes main heat exchanger core segment 10.Main heat exchanger core segment 10 includes demarcation plate part and wing Piece.Demarcation plate part separates first group of heat transfer path 54 and second group of heat transfer path 56 shown in fig. 5.First group of heat transfer path 54 each heat transfer path includes corresponding finless parts.The corresponding fin part of each heat transfer path of first group of heat transfer path 54 Dividing includes multiple wings that multiple channels are defined in the corresponding finless parts of each heat transfer path 54 of first group of heat transfer path 54 Piece.Each heat transfer path 56 of second group of heat transfer path 56 includes corresponding finless parts.Each of second group of heat transfer path 56 The corresponding finless parts of heat transfer path include fixed in the corresponding finless parts of each heat transfer path of second group of heat transfer path 56 Multiple fins in the multiple channels of justice.In the first group of heat transfer path 54 and second group of heat transfer path 56 of main heat exchanger core segment 10 Each may include any of fin pattern, for example, straight fins, the fin of perforation, zigzag fin fin and wing ring wing Piece.Various fin patterns are as shown in Figure 2.
First group of heat transfer path 54, which can be configured as, is transferred to distributor portion from dispenser portion 20 for the first (warm) stream Divide 50 and rejects heat to the second (cold) stream.Second group of heat transfer path 56 can be configured as the second (cold) stream from distribution Device part 50 is transferred to dispenser portion 20 and receives heat from the first (warm) stream.Plate-fin heat exchanger can be configured as with First (warm) stream is passed through into first group of heat transfer path 54 by the second (cold) stream counter-current relationship of second group of heat transfer path 56.
The case where for air separation, first (warm) stream can be air, and second (cold) stream can be from destilling tower Rich nitrogen exhaust gas.First group of heat transfer path 54 and second group of heat transfer path 56 are configured between the first (warm) stream and the second (cold) stream Indirect heat transfer is provided.Each heat transfer path in first group of heat transfer path 54 can in second group of heat transfer path 56 at least One heat transfer path is adjacent.Each heat transfer path in second group of heat transfer path 56 can in first group of heat transfer path 54 extremely A few heat transfer path is adjacent.
Plate-fin heat exchanger includes dispenser portion 20, along the adjacent main heat exchanger in the face 11 of main heat exchanger core segment 10 Core segment 10.With reference to Fig. 3-6, several views of dispenser portion 20 are shown, dispenser portion 20 includes multiple divider plate portions Divide 22.With what is be fixed to one another, substantially parallel spaced relationship is arranged for the multiple demarcation plate part 22.The multiple divider plate portions 22 are divided to define first group of channel 24 and second group of channel 26.Each channel 24 in first group of channel 24 can be with second group of channel 26 at least one channel 26 is adjacent.Each channel in second group of channel 26 can lead to at least one of first group of channel 24 Road is adjacent.
Each channel in first group of channel 24 of dispenser portion 20 and first group of heat transfer path 54 of main heat exchanger core 10 Corresponding heat transfer path be in fluid communication.The of each channel in second group of channel 26 of dispenser portion 20 and main heat exchanger core 10 The corresponding heat transfer path of two groups of heat transfer paths 56 is in fluid communication.
Referring to Fig. 3-10, plate-fin heat exchanger includes the first head 30, it is adjacent along the face 31 on the first head 30 and with First group of channel 24 of dispenser portion 20 is in fluid communication.Each channel in first group of channel 24 by being closed bar part accordingly 32 opposite with the first head 30 one side closed.Each corresponding closure bar part 32 has the surface towards fin (in i.e. Side), with length LH。
First group of channel 24 abuts main heat exchanger core segment 10 along the face 11 of main heat exchanger core segment 10.First group of channel 24 each channel is in fluid communication to the corresponding heat transfer path of first group of heat transfer path 54 of main heat exchanger core segment 10.First group Each channel in channel 24 is by corresponding closed rod 12 opposite with main heat exchanger core segment 10 one side closed.It is each corresponding Closed rod 12 have the surface towards fin, with length LW。
As shown in Fig. 3,4 and 7-10, point of each channel in first group of channel 24 in each channel in first group of channel 24 There is long flow path region 15 between partition part 22, first group of channel 24 each channel demarcation plate part 22 it Between there is short flow path region 25, it is so-called because of process fluid in the dispenser portion in long flow path region 15 The distance advanced is greater than the distance advanced in short flow path region 25.Process fluid need in dispenser portion 20 from The distance that head 30 advances to main heat exchanger core 10 influences the velocity flow profile of the process fluid in main heat exchanger core 10.
The flow path region 15 of the length in each channel in first group of channel 24 is by the first cuboid and the second cuboid Joint definition." cuboid " is 3D shape, and there are six rectangular surfaces substantially at right angle each other for tool.First cuboid is from corresponding The surface towards fin of closed rod 12 extends vertically up to the face 31 along the first head 30 from phase towards corresponding closed rod 12 The closed rod 12 answered towards the face of main heat exchanger core segment 10 11 distance 50% position.Second long body body is perpendicular to corresponding Closure bar part 32 extend to the face 11 along main heat exchanger core segment 10 from corresponding closure bar part 32 towards first 50% position of the distance in the face 31 in portion 30.
The flow path region 15 of length in Fig. 3 is similar to " L " for rotating clockwise 90 °.
The short flow path region 25 in each channel for first group of channel 24 is by long flow path region 15, A part of the face 11 of a part and main heat exchanger core segment 10 of the face 31 on one head 30 defines.
Long flow path region 15 is included in entirely long flow path region 15, and (it includes first kind finless parts 1 and Second Type finless parts 2) in extend two or more finless parts at least part.As used herein, term " type " for distinguishing the finless parts being made of the fin with one or more different characteristics, such as fin pattern and/or Flow freely area and/or fin density and/or hydraulic diameter etc..For example, first kind finless parts 1 can have herringbone Fin, has the first fin density, and first kind finless parts 1 are different from Second Type finless parts 2, Second Type fin Part 2 has herringbone wavy fin, has the second fin density different from the first fin density.
Part of the flow path region 15 of the length in each channel in first group of channel 24 in addition to first kind finless parts Or except some or all of whole and Second Type finless parts, additional finless parts may not included, such as Fig. 6,7 and Shown in 9.
The flow path region 15 of the length in each channel in first group of channel 24 is in addition to including first kind finless parts 1 Part or all of part or all and Second Type finless parts 2 also may include other one or more finless parts Part or all, for example, third type finless parts, as shown in figures 8 and 10.For each channel in first group of channel 24 In addition to a part of part or all and corresponding Second Type finless parts 2 of corresponding first kind finless parts 1 Or some or all of situation except whole also comprising other one or more finless parts, combine the corresponding first kind Finless parts 1 and corresponding Second Type finless parts 2 may extend through the flow path region 15 of the length of respective channel 24 Volume at least 50% or at least 75% or at least 90%.Fig. 8 shows first kind finless parts 1 and Second Type wing 90% or more of the volume for extending to long flow path region 15 is combined in piece part 2, and wherein third type finless parts 3 extend By the volume in long flow path region 15 less than 10%.
Different types of finless parts are designated as first kind finless parts, Second Type finless parts, third type Finless parts etc..The finless parts of a certain type, for example, first kind finless parts 1, by having at least one to influence fluid stream The fin of dynamic and/or heat transfer structure feature rearranges, and is different from another type of finless parts (such as the second class Type finless parts 2) and another type of optional finless parts identical structure feature.At least one structure feature, wherein one The finless parts of seed type, for example, first kind finless parts 1, different from another type of finless parts, for example, second Type finless parts 2 or optional third type finless parts, can be finned, and example is as shown in Fig. 2, the face of free-flowing Product, fin density, hydraulic diameter etc..Different types of respective finless parts can be only one or two or three or more It is different from each other in a feature.
As shown in Fig. 6,7,9,10, the short flow path region 25 in each channel in first group of channel 24 may include A part of one type finless parts 1.
Such as Fig. 6,7,8, shown in 9,10, the short flow path region 25 in each channel in first group of channel 24 be may include A part of Second Type finless parts 2.
At least part of first kind finless parts 1 abuts at least one of Second Type finless parts 2 at boundary 9 Point.As shown in Fig. 6,7,8,9,10, having a common boundary 9 can follow the along the diagonal line in the crosspoint of closed rod 12 and closure bar part 32 The crosspoint in the face 11 in the face 31 and main heat exchanger core segment 10 on one head 30.Dispenser portion 20 is a so-called beveling Distributor.
First kind finless parts 1 include multiple fins that multiple channels are defined in first kind finless parts 1.It is described The first kind finless parts 1 in each channel in first group of channel along each corresponding first kind finless parts 1 boundary The face 31 on 33 adjacent first heads 30.Each first kind finless parts have the second boundary 7.Each corresponding first kind wing The second boundary 7 of piece part can be parallel with the respective closed bar 12 in each channel in first group of channel 24.It is " flat with closed rod 12 The second boundary 7 of the first kind finless parts 1 of row " means between closed rod 12 and the boundary 7 of first kind finless parts 1 Spacing closed rod 12 length LWUpper variation is less than LW5%.
The first kind finless parts 1 in each channel in first group of channel 24 have longitudinal.
The longitudinal direction of finless parts corresponds to the length direction of fin.Finless parts it is longitudinally perpendicular in fin density direction. Finless parts form channel, and wherein the smallest path of the resistance of process fluid is in longitudinal direction.Longitudinal such as Fig. 2 of each fin pattern It is shown.
It the longitudinal direction of first kind finless parts 1 can be parallel with the respective closed bar 12 in each channel in first group of channel 24 Alignment.The planar section and closed rod 12 of demarcation plate in meaning to be transversely to the machine direction with " parallel " that closed rod 12 " longitudinal direction " is aligned The distance between closed rod 12 length LWUpper variation is less than LW5%.
Each Second Type finless parts 2, which are included in each corresponding Second Type finless parts 2, defines multiple channels Multiple fins.The Second Type finless parts 2 in each channel in first group of channel 24 are along each corresponding Second Type wing The face 11 of the adjacent main heat exchanger core segment 10 in the boundary 13 of piece part 2.The Second Type wing in each channel in first group of channel 24 The corresponding finless parts of the corresponding heat transfer path of piece part 2 and first group of heat transfer path 54, it is corresponding to first group of channel 24 Passage is independent finless parts.Therefore, the Second Type finless parts 2 in each channel in first group of channel 24 To corresponding finless parts (the respective channel fluid of itself and first group of channel 24 of the corresponding heat transfer path of first group of heat transfer path 54 Connection) between there are continuity interruption, between the finless parts corresponding to main heat exchanger core segment 10 of Second Type finless parts 2 The gap of 0.5mm to 5mm may be present.Have at face 11 between main heat exchanger core segment 10 and dispenser portion 20 individual The benefit of finless parts first is that for the ease of manufacture.
One or more finless parts features of the Second Type finless parts 2 in each channel in first group of channel 24 can be with Finless parts feature corresponding to the boundary finless parts of the heat transfer path of main heat exchanger core is different.One or more finless parts Feature can be selected from the group being made of fin pattern, free-flowing area, fin density, fin thickness and hydraulic diameter.Pass through Using the fin feature of the dispenser portion different from the fin feature of main heat exchanger core, the whole of plate-fin heat exchanger can be improved Body efficiency.The selection criteria of the fin feature of dispenser portion can be tended to improve flow distribution and improve heat transfer, and be used for The selection criteria of the fin feature of main heat exchanger core segment can be tended to improve heat transfer.The result is that improving plate-fin heat exchanger Whole heat transfer property.
Each Second Type finless parts 2 have the second boundary 8.Second side of each corresponding Second Type finless parts It boundary 8 can be parallel with the corresponding closure bar part 32 in each channel in first group of channel 24.With the second of closure bar part 32 The second boundary 8 of type finless parts 2 " parallel " mean to be closed bar part 32 and Second Type finless parts 2 boundary 8 it Between interval variation closure bar part 32 length LHIt is upper to be less than LH5%.
The Second Type finless parts 2 in each channel in first group of channel 24 have longitudinal.Second Type finless parts 2 Longitudinal direction can be with 32 parallel alignment of respective closed bar part in each channel in first group of channel 24.It is " vertical with closure bar part 32 To " " parallel " of alignment mean to be transversely to the machine direction in the planar section of demarcation plate exist with the distance between bar part 32 is closed It is closed the length L of bar part 32HIt is upper to be less than LH5%.
According to the disclosure, the Second Type finless parts 2 in each channel 24 and the first kind finless parts 1 in each channel It is different, it means that Second Type finless parts 2 have at least one feature different from first kind finless parts 1, such as Fin, the hydraulic diameter of different-style, each of the free-flowing area of each unit width in each channel or each channel The heat transfer area of each unit width of unit length.
The feature of the Second Type finless parts 2 in each channel in first kind finless parts 1 and first group of channel 24 exists In corresponding coefficient of friction parameter ratio,WhereinOrThe j- factor Parameter ratio,WhereinOr
Coefficient of friction parameter ratioIt isWherein
f1It is the coefficient of friction of fin in the first kind finless parts 1 assessed when Reynolds number is 3000,
f2It is the coefficient of friction of fin in the Second Type finless parts 2 assessed when Reynolds number is 3000,
Dh,1It is the hydraulic diameter of first kind finless parts 1,
Dh,2It is the hydraulic diameter of Second Type finless parts 2,
Af,1It is the free-flowing area of each unit width in each channel of first kind finless parts 1, and
Af,2It is the free-flowing area of each unit width in each channel of Second Type finless parts 2,
J- factor parameter ratioIt isWherein
j1It is the j- factor of fin in the first kind finless parts 1 assessed when Reynolds number is 3000,
j2It is the j- factor of fin in the Second Type finless parts 2 assessed when Reynolds number is 3000,
As,1It is the heat-transfer area of each unit width of each unit length in each channel of first kind finless parts 1 Product,
As,2It is the heat-transfer area of each unit width of each unit length in each channel of Second Type finless parts 2 Product,
Af,1It is the free-flowing area of each unit width in each channel of first kind finless parts 1, and
Af,2It is the free-flowing area of each unit width in each channel of Second Type finless parts 2.
Each parameter f1、f2、j1、j2、Dh、1、Dh、2、Af、1、Af、2As、1And As,1Value can commercially obtainable fin The supplier/manufacturer of type obtains, these values are preferred for designing the device.If supplier/manufacturer can not obtain It must be worth, then can determine numerical value from standard method of test, such as 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.1075-1085, 1950,and London,A.L.,and Ferguson,C.K.,Test Results of High Performance Heat Exchanger Surfaces Used in Aircraft Intercoolers and Their Significance for Gas Turbine Regenerator Design,Trans.ASME,Vol.71,P.17,1949。
If from Kays and London, value and the value obtained from London and Ferguson in 1949 that nineteen fifty obtains it Between there are any difference, then implementation of the value of nineteen fifty Kays and London prior to the present apparatus.
Coefficient of friction f and the j- factor is dimensionless number, and value is the function of Reynolds number.Reynolds number Re is also dimensionless number, And byDefinition, wherein ρ is the density of fluid, and v is the speed of fluid in fin channels, DhIt is the water in finless parts channel Power diameter, and μ is the viscosity of fluid.
Dispenser portion is usually 2000 to 30,000 operations with Reynolds number.It has been found that being 3000 news commentaries in Reynolds number Estimate coefficient of friction and the j- factor for characterize according to the disclosure provide benefit coefficient of friction parameter than with j- factor parameter ratio Range is useful.
Consistent unit is used for each parameter, so that coefficient of friction parameter ratio and j- factor parameter ratio are nondimensional.Such as Fruit Dh,1Unit with m, then Dh,2Unit with m.If Af,1With m2The unit of/m, then Af,2With m2The unit of/m.Such as Fruit As,1Unit be m2/ m/m, then As,2Unit be m2/m/m。
From following analysis it is understood that as described using first kind finless parts and Second Type finless parts It needs.
Flow distribution between fin channels is determined by the pressure drop in flow resistance or each fin channels.Per unit length Pressure drop be given by
Wherein G is mass flux, and M is by the mass flow in a channel, A 'fIt is the free-flowing face in each channel Product, other parameters are as described above.When negligible density variation, the unit of first kind finless parts and Second Type finless parts Length pressure drop ratio can be written as
WhereinThe function of its at least fin feature.
First (warm) stream enters heat exchanger from head (30) and leaves heat exchanger from head (60).By distributor (20) and The overall flow rate path of distributor (50) is identical in different fin channels.However, the fluid density in distributor (20) It is more much lower than distributor (50).Therefore, the flow resistance in the fin channels in distributor (20) with long flow path is higher than distribution With the fin channels of short flow path in device (20).In order to reduce the variation of this flow resistance in fin channels, needs to reduce and divide Flow resistance in orchestration (20) in long flow path.
The fluid temperature (F.T.) of first kind finless parts is higher than Second Type finless parts.As a result, first kind finless parts Fluid density be lower than Second Type finless parts.The flow resistance of first kind finless parts is more than Second Type finless parts Obviously.Therefore, Low-resistance fin should be used in first kind finless parts.It is adopted in the first kind and Second Type finless parts With the standard of F alternatively fin.Fin feature and Second Type fin part when F is equal to 1, in first kind finless parts Fin feature in point is identical.When F is less than 1, the flow resistance that the fin feature in first kind finless parts provides is lower than Fin feature in Second Type finless parts.In addition to being caused due to the difference of flow path length and fin feature in fin channels Flow resistance variation except, the fluid density that also results in different piece of heat transmitting in dispenser portion is uneven, this Change the flow resistance in fin channels.
The product UA of the overall heat-transfer coefficient U and heat transfer area A of every channel per unit length per unit width are given by:
Wherein h is heat transfer coefficient, AwIt is each unit width of each unit length in each channel of the first (warm) stream Heat transfer area, AcIt is the heat transfer area of each unit width of each unit length in each channel of the second (cold) stream.
The hA of the per unit length per unit width of one stream is given by
WhereinCpIt is thermal capacity, k is thermal conductivity, and other parameters are as described above.
When ignoring the difference of physical property of fluid, the per unit length of one in first kind finless parts stream it is every The hA of unit width and the ratio of Second Type finless parts can be written as
WhereinIt is the function of fin feature.
Second (cold) stream enters heat exchanger from head (70) and there are heat exchangers from head (40).In distributor (20) portion In point, the second (cold) stream exchanges heat with the first (warm) stream.However, first (temperature) the stream temperature in first kind finless parts is high First (temperature) in Second Type finless parts flows temperature.Therefore, (warm) stream and the first in first kind finless parts The driving force that heat exchange is carried out between two (cold) streams is greater than the drive that heat exchange is carried out between the first (warm) stream and second (the second) Power (cold) stream is in the second fin type portions.This non-uniform driving force causes in the fin channels of the second (cold) stream Temperature and fluid density are uneven, and cause flow distribution uneven.In order to reduce due to driving force it is uneven caused by this stream It is dynamic to be unevenly distributed, lower hA can be used in first kind finless parts.Therefore, it is used as using J in the first kind and the Another standard of fin is selected in two type finless parts.Fin feature when J is equal to 1, in first kind finless parts It is identical as the fin feature in Second Type finless parts.When J is less than 1, the hA of the fin in first kind finless parts is low In Second Type finless parts.
As shown in Fig. 7, Fig. 8, Fig. 9 and Figure 10, the short flow path region 25 in each channel in first group of channel 24 can With at least part comprising third type finless parts 3.Each third type finless parts 3 are included in each corresponding third Multiple fins in multiple channels are defined in type finless parts 3.Each third type wing in each channel in first group of channel 24 Piece part 3 abuts the face 31 on the first head 30 along the boundary 34 of each corresponding third type finless parts 3.First group of channel The third type finless parts 3 in 24 each channel extend to boundary 9 from boundary 34, and abut at least at boundary 9 A part of finless parts extend from boundary 9 towards the face of main heat exchanger core segment 10 11.Each channel in first group of channel 24 Each third type finless parts 3 can abut at least one and the different types of finless parts of third type at boundary 9 At least partially, the 4th type fin in a part and Fig. 9 and 10 of the Second Type finless parts 2 such as in Fig. 7 and Fig. 8 A part of part 4.
Short flow path region 25 for each channel in first group of channel 24 includes third type finless parts 3 Some or all of situation, corresponding third type finless parts 3 can extend to the short flow path of respective channel 24 At least the 20% of the volume in region 25 or at least 40%.Fig. 7,9 and 10 show the body for extending to short flow path region 25 The third type finless parts 3 of long-pending about 23%.Fig. 8 shows third type finless parts 3, extends through short flowing road 50% volume in diameter region 25.
When each channel in first group of channel 24 includes third type finless parts 3, relative in each paragraph each The preferred feature of each third type finless parts 3 of the feature of one type finless parts 1 can compare table with coefficient of friction parameter Show, whereinOrOrCoefficient of friction parameter ratioIt isWherein
f1It is the coefficient of friction of fin in the first kind finless parts 1 assessed when Reynolds number is 3000,
f3It is the coefficient of friction of fin in the third type finless parts 3 assessed when Reynolds number is 3000,
Dh,1The hydraulic diameter of first kind finless parts 1,
Dh,3It is the hydraulic diameter of third type finless parts 3,
Af,1It is the free-flowing area of each unit width in each channel of first kind finless parts 1, and
Af,3It is the free-flowing area of each unit width in each channel of third type finless parts 3,
Wherein consistent unit is used for Dh,1、Dh,3、Af,1And Af,3Each of.
Consistent unit is used for each parameter, so that coefficient of friction parameter compares dimensionless.If Dh,1Unit with m, then Dh,3Unit with m.If Af,1With m2The unit of/m, then Af,3With m2The unit of/m.
The needs using described third type finless parts are understood that from following discussion.
Flow path in first kind finless parts is longer than the flow path in third type finless parts.The first kind The flow resistance of finless parts is more important than the flow resistance of third type finless parts.Therefore, in first kind finless parts In should use the fin than the lower drag in third type finless parts.Coefficient of friction parameter ratioIt can be used as first The standard of fin is selected in type finless parts and third type finless parts.When coefficient of friction parameter ratioEqual to 1 When, the fin feature in first kind finless parts is identical as the fin feature in third type finless parts.Work as coefficient of friction Parameter ratioWhen less than 1, the flow resistance that the fin feature in first kind finless parts provides is lower than third type wing Fin feature in piece part.
As shown in Figures 9 and 10, the short flow path region 25 in each channel in first group of channel 24 may include the 4th At least part of type finless parts 4.Each 4th type finless parts 4 are included in each 4th type finless parts 4 Define multiple fins in multiple channels.The 4th type finless parts 4 of each of each channel in first group of channel 24 are along each The face 11 of the adjacent main heat exchanger core segment 10 in the boundary 14 of corresponding 4th type finless parts 4.Each of first group of channel 24 The 4th type finless parts 4 in channel extend to boundary 9 from boundary 14, and have a common boundary at 9 adjacent at least part from Have a common boundary 9 finless parts extended towards the face of dispenser portion 20 31.The 4th class of each of each channel in first group of channel 24 Type finless parts 4 can abut at least part of at least one and the 4th different types of finless parts of type at boundary 9, Such as a part of all third type finless parts 3 in first kind finless parts 1 and Fig. 9 and Figure 10.
Short flow path region 25 for each channel in first group of channel 24 includes the 4th type finless parts 4 Some or all of situation, corresponding 4th type finless parts 4 can extend to the short flow path of respective channel 24 At least the 20% of the volume in region 25 or at least 40%.Fig. 9, which is shown, extends through about the 26% of short flow path region 25 4th type finless parts 4 of volume.Figure 10 shows the of the 50% of the volume for extending through short flow path region 25 Four type finless parts 4.
Since " first ", " second ", " third ", " the 4th " etc. are for distinguishing multiple features, and the total of feature is not indicated Number, therefore there may be the 4th type finless parts for being with or without above-mentioned third type finless parts.
The corresponding heat transfer of the 4th type finless parts 4 and first group of channel 54 of preaching in each channel in first group of channel 24 The corresponding finless parts in channel, what is be in fluid communication with the respective channel in first group of channel 24 is independent finless parts.Therefore, The 4th type finless parts 4 in each channel in first group of channel 24 and the phase of the corresponding heat transfer path of first group of heat transfer path 54 The continuity between finless parts (respective channel in itself and first group of channel 24 is in fluid communication) is answered to be interrupted.4th type wing The gap of 0.5mm to 5mm may be present between the finless parts corresponding to main heat exchanger core segment 10 of piece part 4.With individual The benefit of finless parts is for the ease of manufacture.The benefit in gap is to limit the flowing limitation of intersection, this is because fin is horizontal Section it is Chong Die with the open area in channel and generate.
One or more finless parts features of the 4th type finless parts 4 in each channel in first group of channel 24 can be with Finless parts feature corresponding to the adjacent fins part of the heat transfer path of main heat exchanger core is different.One or more finless parts Feature can be selected from the group being made of fin pattern, free-flowing area, fin density, fin thickness and hydraulic diameter.Pass through Using the fin feature of the dispenser portion different from the fin feature of main heat exchanger core, the whole of plate-fin heat exchanger can be improved Body efficiency.
When each channel in first group of channel 24 includes the 4th type finless parts 4, each Second Type in each paragraph The preferred feature of the 4th type finless parts 4 of each of feature of finless parts 2 can use j- factor parameter ratioTable Show, whereinOrOrJ- factor parameter ratio It isWherein
j2It is the j- factor of fin in the Second Type finless parts 2 assessed when Reynolds number is 3000,
j4It is the j- factor of fin in the 4th type finless parts 4 assessed when Reynolds number is 3000,
Af,2It is the free-flowing area of each unit width in each channel of Second Type finless parts 2, and
Af,4It is the free-flowing area of each unit width in each channel of the 4th type finless parts 4,
As,2It is the heat-transfer area of each unit width of each unit length in each channel of Second Type finless parts 2 Product, and
As,4It is the heat-transfer area of each unit width of each unit length in each channel of the 4th type finless parts 4 Product,
Wherein consistent unit is used for Af,2、Af,4、As,2And As,4Each of.
Consistent unit is used for each parameter, so that j- factor parameter ratio is nondimensional.If Af,2Unit be m2/ M, then Af,4Unit be m2/m.If As,2With m2The unit of/m/m, then As,4With m2The unit of/m/m.
The needs using described 4th type finless parts are understood that from following discussion.
Second (cold) stream enters heat exchanger from head 70 and leaves heat exchanger from head 40.In 20 part of distributor, the Two (cold) streams exchange heat with the first (warm) stream.However, first (temperature) the stream temperature in the 4th type finless parts is higher than second First (temperature) in type finless parts flows temperature.Therefore, the first (warm) stream and the second (cold) stream in the 4th type finless parts Between heat exchange driving force be higher than Second Type finless parts in first it is (warm) stream and second it is (cold) flow between heat exchange drive Power.This non-uniform driving force causes temperature in the fin channels of the second (cold) stream and fluid density uneven, and leads Cause flow distribution uneven.In order to reduce due to driving force it is uneven caused by this flow distribution unevenness, can be in the 4th type Lower hA is used in finless parts.J- factor parameter ratioSecond Type finless parts and the 4th class of electing can be used The standard of fin in type finless parts.When j- factor parameter ratioWing when equal to 1, in Second Type finless parts Piece feature is identical as the fin feature in the 4th type finless parts.When j- factor parameter ratioWhen less than 1, the 4th class The hA of fin in type finless parts is lower than the fin in Second Type finless parts.
Plate-fin heat exchanger further includes the second head 40, and fluid adjacent with second group of channel 26 of dispenser portion 20 Connection.
In the design shown in Figure 11, second group of channel 26 of dispenser portion 20 is adjacent along the face 41 on the second head 40. Each channel in second group of channel 26 is along the adjacent main heat exchanger core segment 10 in the face of main heat exchanger core segment 10 11.Second group of channel Respective closed bar part 38 of the 26 each channel on side of the side by adjacent first head 30 and with the first head 30 Respective closed bar part 36 on opposite side is closed.
The specific design of finless parts in the channel in second group of channel 26 of dispenser portion 20 has been confirmed as being not so good as The design of finless parts in the paragraph in first group of channel 24 is important.
As shown in figure 11, the longitudinal direction of the finless parts in second group of channel 26 can be substantially parallel to corresponding closed rod Part 36 and have it is identical with the finless parts in heat transfer path 56 (Fig. 5) corresponding in main heat exchanger core segment 10 indulge To.
Fin in second group of channel 26 of dispenser portion 20 can be the fin of same type, have and main heat exchanger The identical fin feature of fin in the corresponding heat transfer path of core 10.Alternatively, in second group of channel 26 of dispenser portion 20 Fin can have the fin feature different from the fin in the heat transfer path of main heat exchanger core 10.
The design for needing to chamfer in the alternate design in second group of channel 26 of dispenser portion 20, can be used side head 40b, as shown in figure 12.
Finless parts 42 in the plate-fin heat exchanger design with side head 40b, in the channel in second group of channel 26 The fin that can have same type with 43, feature having the same, so that coefficient of friction parameter ratio is equal to 1 and j- factor parameter Than being equal to 1.If the finless parts 42 and 43 in second group of channel 26 have different fin features, for first group of channel 24 First kind finless parts and Second Type finless parts, it may be necessary to implement corresponding coefficient of friction parameter ratio and the j- factor The similar standard of parameter ratio.The description of first kind finless parts and Second Type finless parts is respectively suitable for finless parts 43 With finless parts 42.
Plate-fin heat exchanger includes the distributor along the adjacent main heat exchanger core segment 10 in the face of main heat exchanger core segment 10 51 Part 50.With reference to Figure 13-15, it illustrates several views of dispenser portion 50, dispenser portion 50 includes multiple demarcation plates Part 72.With what is be fixed to one another, substantially parallel spaced relationship is arranged for the multiple demarcation plate part 72.The multiple demarcation plate Part 72 defines first group of channel 74 of dispenser portion 50 and second group of channel 76 of dispenser portion 50.First group of channel 74 In each channel 74 can be adjacent at least one channel in second group of channel 76.Each channel 76 in second group of channel 76 It can be adjacent at least one channel in first group of channel 74.
First group of heat transfer path in each channel 74 and main heat exchanger core 10 in first group of channel of dispenser portion 50 Corresponding heat transfer path is in fluid communication.Each channel in second group of channel 76 of dispenser portion 50 and the second of main heat exchanger core 10 The corresponding heat transfer path of group heat transfer path is in fluid communication.
Referring to Figure 13-15, plate-fin heat exchanger includes head 60, and head 60 is along the face 81 on head 60 and dispenser portion 50 first group of channel 74 is adjacent and is in fluid communication.Each channel 74 in first group of channel by being closed bar part accordingly 82 opposite with head 60 one side closed.
First group of channel 74 of dispenser portion 50 abuts main heat exchanger core along the face 51 of main heat exchanger core segment 10 Divide 10.Each channel 74 in first group of channel is by corresponding closed rod 62 opposite with main heat exchanger core segment 10 one Side seal closes.
Second group of channel 76 of dispenser portion 50 is adjacent along the face 61 on head 70.Second group of channel of dispenser portion 50 76 each channel is along the adjacent main heat exchanger core segment 10 in the face of main heat exchanger core segment 10 51.Each of second group of channel 76 is logical Road is closed by the respective closed bar part on the side close to head 60 and in side corresponding on the opposite side in head 60 Bar part 86 is closed to close.
Dispenser portion 50 can be according to known traditional design method or according to dispenser portion 20 as described herein Design method is configured with finless parts.
Embodiment
A two-dimensional mathematical model is developed to calculate the Coupled Heat Transfer and stream in the double passage heat exchanger with distributor Body flow distribution.The outlet temperature of two stream is solved with the regulation inlet temperature of each in two stream.Heat exchanger and distributor It is separated into the grid comprising multiple units, as shown schematically in Figure 16 and 17.Selection cell number make cell quantity into One step increase causes acquired solution not have significant variation.Figure 16 shows the regulation fluid flow path of first (temperature) stream.Figure 17 Show the regulation fluid flow path of the second (cold) stream.Unit in grid can usually include more than one fin channels.
The thermal balance of each unit is calculated from the following terms:
With
Calculate the pressure drop of each cell.Pressure drop includes the pressure drop in the pressure drop and fin channels of fin intersection.Flow path i's The pressure drop of fin intersection is given by:
Wherein viIt is the upstream speed of fin boundary q in the i of path, ρqIt is the corresponding close of fluid in the q upstream, cell of fin boundary Degree, AqIt is the corresponding free-flowing area in the upstream, cell of fin boundary q.
It is given by along the flow path i in unit j by the pressure drop of finless parts:
Wherein LI, jIt is in unit j along the flow-path-length of flow path i.
It is given by along the overall presure drop of flow path i:
Wherein N1 is the sum that fin has a common boundary, and N2 is the unit sum in flow path.
At steady state, the pressure drop along each flow path is identical.In other words, Δ PiIt is a constant.So Afterwards, the flow mass M in flow path iiIt is proportional to following formula:
Therefore
Wherein N3 is flow path number used in model.
Specify the total mass flow rate of each stream and the temperature and pressure of distributor inlet, and input value in a model. The physical property of fluid is the function of the temperature and pressure calculated in each unit in each unit.Iteratively calculate solution party Case solves the temperature of first (warm) stream and the second (cold) stream in the exit of the relative distribution device of each respective streams.Based on above-mentioned Equation updates the mass flowrate of each flow path, the pressure of temperature and each unit for each iteration.
Table 1 summarizes three kinds of situations, and illustrates the effect of this plate-fin heat exchanger design.Tb1It is that first main body goes out Mouth temperature, Tb2It is the bulk outlet temperature of second.LHXThe main body for being to provide first bulk outlet temperature and second goes out The length of heat exchanger needed for mouth temperature.
The total mass flow rate of first (temperature) stream and the total mass flow rate of the second (cold) stream are set as 0.3kg/s.Into head The temperature of first (temperature) stream in portion 30 is set in 24.14 DEG C.Temperature into second (cold) stream on head 70 is -179.11 DEG C. The pressure that first (temperature) into head 30 flows is 5.3 bars, and the pressure into second (cold) stream on head 70 is 5.01 bars.Air Physical property for the first (warm) stream, the physical property of nitrogen is for the second (cold) stream for these model results.
The fin feature in fin feature and Second Type finless parts in situation 1, in first kind finless parts It is identical, represent prior art design.In this case, coefficient of friction parameter ratioJ- factor parameter ratioHeat exchanger length is set as 3.3 meters.The bulk temperature for being discharged to first (temperature) stream on head 60 is 174.59 ℃.The final body temperature for being discharged to second (cold) stream on head 40 is 20.62 DEG C.Entirety is calculated in a usual manner using mass velocity Temperature is to provide quality average external volume value.
In situation 2, the fin feature in first kind finless parts is identical as case 1, and Second Type fin part Fin feature in point is changed to provide coefficient of friction parameter ratioWith j- factor parameter ratioEvery other condition keeps identical as situation 1.Heat exchanger length is adjusted, the until being discharged to head 60 One (temperature) stream obtains identical bulk temperature, and second (cold) stream is discharged to head 40 and obtains identical bulk temperature.The mould Type the result shows that, heat exchanger length needed for the first and second streams obtain identical outlet temperature is 3.25m, is less than situation 1 In heat exchanger length.This means that the design of heat exchanger in situation 2 provides improved biography than the design of heat exchanger in situation 1 The thermal efficiency.
In situation 3, the fin feature in first kind finless parts is identical as case 1, and Second Type fin part Fin feature in point is changed to provide coefficient of friction parameter ratioWith j- factor parameter ratioEvery other condition keeps identical as situation 1.Heat exchanger length is conditioned, until being discharged to head 60 First (temperature) stream identical bulk temperature, and second (the second) obtains identical bulk temperature (cold) stream and is discharged to head 40.Model the result shows that, obtain first and second stream same volume outlet temperature needed for heat exchanger length be 3.15 meters, Less than the heat exchanger length in situation 1.This means that design of heat exchanger is provided to be set than the heat exchanger in situation 1 in situation 3 Count better heat transfer efficiency.
In situation 4, fin feature and the phase in situation 3 of first kind finless parts and Second Type finless parts Together.Third type finless parts add as shown in Figure 7.The fin feature of third type finless parts is selected to provide coefficient of friction Parameter ratio,Every other condition keeps identical as situation 3.Third type finless parts are from heat exchanger core The face 11 of part 10 extends L towards closed rod 12HThe 20% of length.Adjust heat exchanger length LHX, until being discharged to head 60 The identical bulk temperature of first (temperature) stream, and for being discharged into head 40 second (cold) stream obtains identical whole temperature Degree.Model shows that heat exchanger length needed for obtaining the same volume outlet temperature of the first and second streams is 3.13 meters, is less than every Heat exchanger length in a situation 1,2 and 3.Design of heat exchanger in situation 4 means that the heat exchanger in situation 1,2 and 3 is set Improved heat exchanger efficiency is provided in meter.
Table 1.

Claims (20)

1. plate-fin heat exchanger, comprising:
Main heat exchanger core segment, including first group of heat transfer path and second group of heat transfer path, first group of heat transfer path it is every A heat transfer path includes corresponding finless parts, and each heat transfer path of second group of heat transfer path includes corresponding wing Piece part；
Along the dispenser portion of the adjacent main heat exchanger core segment in the face of the main heat exchanger core segment, the distributor portion Divide and includes:
Multiple demarcation plate parts, relationship is arranged at regular intervals for the multiple demarcation plate part, wherein the multiple demarcation plate Part limits first group of channel and second group of channel；
First head, the face along first head it is adjacent and with first group of passage, wherein described first group Each channel in channel is closed in the side on first head opposite by being closed bar part accordingly；
Second head, adjacent and second group of passage with the dispenser portion；
Wherein first group of channel is along the adjacent main heat exchanger core segment in the face of the main heat exchanger core segment, wherein described Each channel in first group of channel connects to the corresponding heat transfer path fluid of first group of heat transfer path of the main heat exchanger core segment It is logical, and wherein each channel in first group of channel in the side on main heat exchanger core segment opposite by being closed accordingly Bar closure；
Wherein each channel in first group of channel is combining limit described by the first cuboid and the second cuboid There is long flow path region, first cuboid is from corresponding point between the divider plate portions in each channel in one group of channel The fin side of closed rod extends to such position perpendicular to corresponding closed rod, which is along first head Face from corresponding closed rod towards the face of the main heat exchanger core segment distance 50%, and second cuboid is vertical Such position is extended in corresponding closed rod, which is to be closed along the face of the main heat exchanger core segment from corresponding Bar towards first head face distance 50%；
Wherein each channel in first group of channel is by one of long flow path region, the face on first head Point and the main heat exchanger core segment face the divider plate portions in each channel in first group of channel that define of a part / have short flow path region；
Wherein the flow path area by the length is contained in the flow path region of the length in each channel in first group of channel At least part for two or more finless parts that domain extends, including first kind finless parts and Second Type fin part Point, at least part of at least part of the first kind finless parts and the Second Type finless parts abuts against friendship At boundary, the first kind finless parts include multiple fins that multiple channels are limited in the first kind finless parts, And the Second Type finless parts include multiple fins that multiple channels are limited in the Second Type finless parts；
Wherein the first kind finless parts in each channel in the first kind channel are along each corresponding first kind fin The face on adjacent first head of portion boundary；
Wherein the Second Type finless parts in each channel in first group of channel are along each corresponding Second Type fin The face of the adjacent main heat exchanger core segment of portion boundary, wherein the Second Type wing in each channel in first group of channel The respective heat transfer path of piece part and first group of heat transfer path being in fluid communication with the respective channel in first group of channel Continuity between corresponding finless parts is interrupted；
Wherein the first kind finless parts and Second Type finless parts in each channel in first group of channel have corresponding Coefficient of friction parameter ratioWhereinWherein
Wherein the first kind finless parts and Second Type finless parts in each channel in the first kind channel have corresponding J- factor parameter ratioWhereinWherein
Wherein
f1It is fin in the first kind finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 Corresponding coefficient of friction,
f2It is fin in the Second Type finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 Corresponding coefficient of friction,
j1It is fin in the first kind finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 The corresponding j- factor,
j2It is fin in the Second Type finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 The corresponding j- factor,
Dh,1It is the corresponding hydraulic diameter of the first kind finless parts in each channel in first group of channel,
Dh,2It is the corresponding hydraulic diameter of the Second Type finless parts in each channel in first group of channel,
Af,1It is each unit width in each channel of the first kind finless parts in each channel in first group of channel It is corresponding to flow freely area,
Af,2It is each unit width in each channel of the Second Type finless parts in each channel in first group of channel It is corresponding to flow freely area,
As,1It is each unit length in each channel of the first kind finless parts in each channel in first group of channel The corresponding heat transfer area of each unit width,
As,2It is each unit length in each channel of the Second Type finless parts in each channel in first group of channel The corresponding heat transfer area of each unit width,
Wherein consistent unit is used for Dh,1、Dh,2、Af,1、Af,2、As,1And As,2Each of.
2. plate-fin heat exchanger according to claim 1, wherein the Second Type in each channel in first group of channel One or more finless parts features of finless parts are different from and first group of heat transfer path of the main heat exchanger core segment Each heat transfer path of first group of heat transfer path in each channel in first group of channel that corresponding heat transfer path is in fluid communication Corresponding finless parts corresponding finless parts feature.
3. plate-fin heat exchanger according to claim 2, wherein one or more of finless parts features are selected from fin Formula flows freely area, fin density, fin thickness and hydraulic diameter.
4. plate-fin heat exchanger according to claim 1, wherein the plate-fin heat exchanger be configured as with second Make across the counter-current flow relationship of second group of heat transfer path first-class across first group of heat transfer path.
5. plate-fin heat exchanger according to claim 1, wherein the second side of each corresponding first kind finless parts Boundary is parallel with the respective closed bar of each respective channel in first group of channel.
6. plate-fin heat exchanger according to claim 1, wherein the first kind in each channel in first group of channel Finless parts have longitudinal direction, wherein each phase of the longitudinal direction and first group of channel of each corresponding first kind finless parts Answer the respective closed bar parallel alignment in channel.
7. plate-fin heat exchanger according to claim 1, wherein each channel in each corresponding first group of channel Second Type finless parts the second boundary it is usually flat with the respective closed bar of each respective channel in first group of channel Row alignment.
8. plate-fin heat exchanger according to claim 1, wherein the Second Type in each channel in first group of channel Finless parts have longitudinal direction, wherein the longitudinal direction of each corresponding Second Type finless parts is usually every with first group of channel The respective closed bar part parallel alignment of a respective channel.
9. plate-fin heat exchanger according to claim 1, wherein each respective channel in first group of channel is short Flow path region includes a part of corresponding first kind finless parts.
10. plate-fin heat exchanger according to claim 1, wherein each respective channel in first group of channel is short Flow path region includes a part of corresponding Second Type finless parts.
11. plate-fin heat exchanger according to claim 1, wherein the short flowing in each channel in first group of channel Passage zone contains two or more corresponding finless parts, including corresponding third type finless parts, is included in corresponding Multiple fins in multiple channels are limited in third type finless parts, wherein corresponding the of each channel in the first kind channel Three type finless parts abut the face on first head along the boundary (34) of each corresponding third type finless parts；
Wherein the first kind finless parts and third type finless parts in each channel in first group of channel have corresponding Coefficient of friction parameter ratioWhereinWherein
Wherein
f3It is fin in the third type finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 Corresponding coefficient of friction,
Dh,3It is the corresponding hydraulic diameter of the third type finless parts in each channel in first group of channel,
Af,3It is each unit width in each channel of the third type finless parts in each channel in first group of channel It is corresponding to flow freely area,
Wherein consistent unit is used for Dh,1、Dh,3、Af,1And Af,3Each of.
12. plate-fin heat exchanger according to claim 11, wherein each of each channel in first group of channel Three type finless parts extend through at least 20% volume in the short flow path region of respective channel.
13. plate-fin heat exchanger according to claim 11, wherein each of each channel in first group of channel Three type finless parts extend from the boundary of each corresponding third type finless parts towards having a common boundary, and abut against from boundary At least part of boundary of the finless parts extended towards the face of the main heat exchanger core segment.
14. plate-fin heat exchanger according to claim 11, wherein each of each channel in first group of channel Three type finless parts extend from the boundaries of each corresponding third type finless parts towards having a common boundary, and abut against type with At least part of boundary of at least one different types of finless parts of third type finless parts.
15. plate-fin heat exchanger according to claim 1, wherein each respective channel in first group of channel is short Two or more finless parts, including corresponding 4th type finless parts are contained in flow path region, are included in each corresponding The 4th type finless parts in limit multiple fins in multiple channels, wherein each channel in the first kind channel is corresponding 4th type finless parts abut the face of main heat exchanger part along the boundary of each corresponding 4th type finless parts, wherein The 4th type finless parts in each channel in first group of channel and connect with the respective channel fluid in first group of channel Continuity between the corresponding finless parts of the respective heat transfer path of first group of logical heat transfer path is interrupted；
Wherein the 4th type finless parts and Second Type finless parts in each channel in first group of channel have corresponding J- factor parameter ratioWhereinWherein
Wherein
j4It is fin in the 4th type finless parts in each channel in the first group of channel assessed when Reynolds number is 3000 The corresponding j- factor,
Af,4It is each unit width in each channel of the 4th type finless parts in each channel in first group of channel It is corresponding to flow freely area,
As,4It is each unit length in each channel of the 4th type finless parts in each channel in first group of channel The corresponding heat transfer area of each unit width,
Wherein consistent unit is used for Af,2、Af,4、As,2And As,4Each of.
16. plate-fin heat exchanger according to claim 15, wherein each of each channel in first group of channel Four type finless parts extend through at least 20% volume in the short flow path region of respective channel.
17. plate-fin heat exchanger according to claim 15, wherein each of each channel in first group of channel Four type finless parts extend from the boundary of each corresponding 4th type finless parts towards having a common boundary, and abut against from boundary At least part of boundary of the finless parts extended towards the face of the dispenser portion.
18. plate-fin heat exchanger according to claim 15, wherein each of each channel in first group of channel Four type finless parts extend from the boundaries of each corresponding 4th type finless parts towards having a common boundary, and abut against type with At least part of boundary of at least one different types of finless parts of 4th type finless parts.
19. a kind of method for carrying out heat exchange between second first-class, this method comprises:
Plate-fin heat exchanger according to claim 1 is provided；
Make described the to pass through the counter-current flow relationship of second group of heat transfer path of the plate-fin heat exchanger with the second One stream passes through first group of heat transfer path of the plate-fin heat exchanger.
20. according to the method for claim 19, wherein it is described it is first-class be oxygen concentration range be 20 volume % oxygen extremely 22 volume % oxygen and nitrogen gas concn range are the first fluid of 78 volume % nitrogen to 80 volume % nitrogen, and wherein the Second-rate is the rich nitrogen waste gas stream from destilling tower.
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