EP3781887A1 - Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur - Google Patents

Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur

Info

Publication number
EP3781887A1
EP3781887A1 EP19727493.9A EP19727493A EP3781887A1 EP 3781887 A1 EP3781887 A1 EP 3781887A1 EP 19727493 A EP19727493 A EP 19727493A EP 3781887 A1 EP3781887 A1 EP 3781887A1
Authority
EP
European Patent Office
Prior art keywords
tubes
tube
twisted
sections
along
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP19727493.9A
Other languages
German (de)
English (en)
Inventor
Byron BLACK
Prashant Jadhav
Marco FAZZINI
Donald Woods
Nathan BARNETT
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koch Heat Transfer Co LP
Original Assignee
Koch Heat Transfer Co LP
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Koch Heat Transfer Co LP filed Critical Koch Heat Transfer Co LP
Publication of EP3781887A1 publication Critical patent/EP3781887A1/fr
Pending legal-status Critical Current

Links

Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1669—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • Embodiments of the present invention relate generally to a heat exchanging apparatus, heat exchanger, methad of use and method of manufacturing, and more particularly to embodiments providing a plurality of bundled round heat exchange tubes comprising individually segmented sections generally having a twisted configuration capable of operably self-supporting the respective tubes within the heat exchanger.
  • Tubular heat exchangers including shell-and-tube and hairpin (multitube) type heat exchangers, are used in a wide variety of applications to create heat exchange between streams of various fluids.
  • Such heat exchangers generally include a combination, or bundle, of tubes housed within a cylindrically shaped shell.
  • a first fluid commonly referred to as the“tube-side fluid”
  • a second fluid commonly referred to as the“shell-side fluid”
  • the“shell-side fluid” is directed within the shell and into any void around the tubes comprising the tube bundle, wherein the tube wall of each tube can permit heat exchange between the tube-side fluid stream flowing within the tubes and the shell-side fluid stream flowing around the tubes.
  • the tube bundle of a tubular heat exchanger includes a plurality of separate, self-contained individual tubes that extend in parallel to each other, wherein one or both of the ends of each respective tube is fixed to a header plate or a plurality of header plates, which are known as tube sheets.
  • a header plate or a plurality of header plates which are known as tube sheets.
  • tubular heat exchangers including shell-and-tube or hairpin (multitube) type heat exchangers, are subject to sagging and vibrations, both of which can negatively affect the heat exchanger and its components.
  • baffles e.g., segmented baffles
  • Such intermediate support structures or members can include spaced-apart baffles (e.g., segmented baffles), which generally consist of plates having holes or openings to receive and support the tubes and may further include spaces or voids for permitting the flow of shell-side fluid.
  • baffles may generally redirect the flow of the shell-side fluid, such that it flows across, rather than along, the tubes. In this way, such baffles generally inhibit the flow of the shell-side fluid along the length of the tubes.
  • Other types of supports can consist of grids or rods.
  • baffles designs can vary and have any number of configurations and features to suit a particular application, baffle positioning and spacing can pose a difficult design challenge and create an impediment to efficient and optimal heat exchanger operation.
  • the limited space between the baffles can adversely affect the heat exchanger by reducing the flow area for the shell-side fluid, which results in excessive shell-side pressure drop.
  • FIGURE 1 is a perspective view of an exemplary heat exchanger in accordance with embodiments presented herein;
  • FIGURE 2 is a partial side elevation schematic representation of an exemplary heat exchanger in accordance with embodiments presented herein;
  • FIGURE 3 is a partial detail side representation of tube sections of a heat exchanger in accordance with embodiments presented herein;
  • FIGURE 4 is a cross-sectional representation taken generally along line 4-4 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 5 is a cross-sectional representation taken generally along line 5-5 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 6 is a cross-sectional representation taken generally along line 6-6 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 7 is a cross-sectional representation taken generally along line 7-7 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 8 is a cross-sectional representation taken generally along line 8-8 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 9 is a cross-sectional representation taken generally along line 9-9 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3;
  • FIGURE 10 is a cross-sectional representation taken generally along line 10-10 of FIG. 3 in the direction of the arrows and showing a tube bundle in accordance with the embodiment shown in FIG. 3.
  • Embodiments presented herein are generally directed to a heat exchanging apparatus, a heat exchanger, a method of manufacture and method of carrying out heat exchange providing segmented twisted sections of bundled heat exchange tubes.
  • Embodiments disclosed herein can be provided or practiced with any number of exemplary heat exchanger designs, including for example a shell-and-tube or hairpin (multitube) type heat exchanger or multi-pass arrangements, and/or designs implementing parallel (co-current) or counter-flow arrangements.
  • FIG. 1 schematically depicts a perspective illustration of a heat exchanger 100 according to an exemplary embodiment of the present invention.
  • a tubular heat exchanger 100 can be generally elongated and comprise an inlet 102, an outlet 104, and tubes 120 or a tube bundle 140.
  • the tubular heat exchanger 100 of FIG. 1 is depicted without a shell or other common heat exchanger components (e.g., a shroud, and so on). Flowever, it will be understood that heat exchanger 100 may comprise such components without limitation.
  • FIG. 2 representatively illustrates a partial side schematic representation view of a heat exchanger 100 according to an exemplary embodiment provided herein, and more particularly to an exemplary bundle 140 of individual tubes 120 having a generally U-shaped arrangement.
  • the U-shaped bundle 140 of tubes 120 can comprise a plurality of generally elongated tubes 120 having at least a first leg portion 142 and a second leg portion 144 extending substantially parallel to each other along their lengths. According to the embodiment illustrated in FIG.
  • portions 142, 144 of tubes 120 within the tube bundle 140 are in fluid communication with each other so that tube-side fluid within an interior passageway of the tubes can be permitted to flow in a first direction along the first leg portion 142 of a U-shaped tube 120 from an inlet 102 and into the U-shaped portion 146, where the tube-side fluid can reverse direction and flow back in a second direction, opposite to the first direction, along the second leg portion 144 of a U-shaped tube 120 to an outlet 104.
  • FIG. 2 depicts the tube bundle 140 generally comprising a linear first leg portion 142 and a linear second leg portion 144 that are joined by a generally U-shaped portion 146
  • the tube bundle 140 can comprise any of a number of shapes, whether presently known or later developed, including, without limitation, generally triangular shapes, generally rectangular shapes, and any similar symmetrical and non-symmetrical shapes or series of shapes that are joined by any number of rounded portions that have varying arc lengths and radius sizes.
  • a preferred embodiment of the present invention can be used with alternate tube bundle arrangements including, for example, straight tube or shell arrangements, single or multi-pass arrangements, and/or designs implementing parallel (co-current) or counter-flow arrangements.
  • the fluid tubes 120 of the tube bundle 140 can generally comprise an alternating series of individually segmented sections 150, in fluid communication with each other, comprising generally tubular straight sections 152 and sections further generally comprising a twisted configuration 154, which are twisted or rotated along their lengths about the respective central longitudinal axes 160 defined thereby.
  • FIG. 2 shows schematically in FIG. 2, according to exemplary embodiments the fluid tubes 120 of the tube bundle 140 can generally comprise an alternating series of individually segmented sections 150, in fluid communication with each other, comprising generally tubular straight sections 152 and sections further generally comprising a twisted configuration 154, which are twisted or rotated along their lengths about the respective central longitudinal axes 160 defined thereby.
  • each tube 120 of the tube bundle 140 is shown as providing a series 150 of intermittent twisted sections 154 spaced apart by straight or untwisted tube sections 152.
  • a preferred embodiment of the present invention can comprise a first straight section 152, generally corresponding with the entire length of the first leg portion 142, and a first twisted section 154, generally corresponding with the entire length of the second leg portion 144, or any variation thereof.
  • FIG. 2 depicts the alternating series of individually segmented sections 150 as being generally equal or consistent in length, it will be understood that the length of any straight section 152 or any twisted section 154 can vary relative to any other straight section 152 or twisted section 154.
  • the twisted tube sections 154 of the plurality of tubes can be generally positioned in alignment with one another and the straight tube sections 152 can be generally positioned in alignment with one another.
  • the intermittent twisted sections 154 of the first leg portion 142 and the intermittent twisted sections 154 of the second leg portion 144 of each tube 120 within the tube bundle 140 can be aligned so that the twisted sections 154 of each leg portion are generally laterally adjacent to the twisted sections 154 of the other leg portion.
  • FIG. 2 illustrates a specific number and location of alternating twisted sections 154 and straight sections 152, it will be understood that embodiments are not limited to such and that such alternating sections 150 can be provided in alternative numbers or locations, without limitation.
  • the twisted sections 154 are advantageous because they can generally result in a more efficient conversion of pressure drop across the shell-side of the tubes 120 and the tube bundle 140.
  • the twisted sections 154, and the arrangement thereof can mitigate the negative effects of tube sagging and vibration of the tubes 120, because the twisted sections 154, and the arrangement thereof, increases the mechanical resonant frequency of the tube 120, which can make the tubes 120 and any bundle 140 of such tubes 120 more resistant to lateral deflection from forces generated by shell-side fluid flow through the heat exchanger 100.
  • the twisted sections 154 and the arrangement thereof with straight sections 152, eliminate the need for closely-spaced intermediate support structures or members at various points along the length thereof and, in some instances, the need for intermediate support structures or members at all.
  • the improvement being advantageous over tubes, arrangements of tubes, and tube bundles that comprise either entirely straight tubes or tubes that are twisted over their entire lengths, without the alternating series of individually segmented straight sections and twisted sections 150.
  • the twisted sections 154 can promote the efficiency of heat transfer between tube-side fluid and shell-side fluid when compared to known tube arrangements.
  • FIGS. 4-10 further depict representations of the various cross-sections at specific rotational intervals along the length of a segment S of the respective tubes 120 in FIG. 3.
  • each tube 120 is twisted or rotated about a central longitudinal axis 160 at least 360 s , or one complete revolution, with each cross-section view along segment S showing rotation on the order of approximately 60 s from any immediately adjacent cross-section.
  • the segment S can be approximately between three (3) inches and sixteen (16) inches, or approximately between five (5) inches and ten (10) inches, depending on the diameter of the respective tube 120, which can vary between approximately 0.625 inches in diameter and one (1 ) inch in diameter.
  • each tube 120 can complete two 360 s turns between any two consecutive straight sections 152. As shown schematically in FIG. 3, the exterior surfaces of tubes 120 avoid contact along the straight sections 152.
  • FIGS. 4-10 schematically illustrate rotation of tubes 120 within a tube bundle 140 through a 360° portion of rotation along the twisted section 154.
  • the tubes 120 according to exemplary embodiments presented herein are generally provided as having a round cross-section profile when oriented along the straight sections, FIGS. 4-10 show that such round cross-sectional profile is compressed through the twisting of the tube bodies.
  • such compression can flatten the round-cross sectional profile such that the tubes take on a generally elliptical shape as shown in FIGS. 4-10.
  • Such compression can reduce the cross-sectional area of the tubes and causes opposing points on the sides of the tubes to protrude outward. As shown schematically in FIGS 4-10, such protrusion can bring about contact 170 between exterior surfaces of tube bodies of adjacent tubes.
  • exterior surfaces of adjacent tubes 120 of the tube bundle 140 can have a plurality of points of contact 170 along the twisted section at certain rotation intervals.
  • rotation of the tube body of each of the plurality of tubes 120 in the twisted section can be synchronized such that the tubes 120 rotate together.
  • the plurality of tubes 12 can be in an initial rotation orientation. From this orientation, as the tubes twist along the twisted segment, the tube body of each tube rotate together (tubes shown as being horizontally adjacent to one another in FIG. 4 with their end points in contact are shown as rotating counterclockwise towards the rotation interval shown in FIG. 5).
  • FIG. 7 represents a rotation interval taken on the order of 180° from the initial rotation orientation of FIG. 4. Accordingly, the right side of a tube in FIG. 4 would be shown as being the left side in FIG. 7.
  • FIGS. 4-10 show tubes 120 of an exemplary tube bundle 140 at a particular rotation interval taken on the order of 60° through a full 360° of rotation of a twisted segment.
  • such interior tube 120 can have a first point of contact 170 with an adjacent tube 120 directly to its right and a second point of contact 170 with the adjacent tube 120 directly to its left.
  • the centermost tube has the first point of contact 170 with the adjacent tube 120 to its upper-right and the second point of contact 170 with the adjacent tube 120 to its lower-left.
  • the centermost tube 120 has the first point of contact 170 with the adjacent tube 120 to its upper-left and the second point of contact 170 with the adjacent tube 120 to its lower-right. Then, in FIG. 7, the centermost tube 120 has the first point of contact 170 with the adjacent tube 120 directly to its left and the second point of contact 170 with the adjacent tube 120 directly to its right. In this way, the centermost tube 120 can encounter eight (8) different points of contact 170 through 180 s of revolution along a portion of segment S, as represented by FIGS. 4-7. In contrast, as shown in FIGS. 4-7, with respect to any tube 120 other than the centermost tube 120 in tube bundle 140, such tube can encounter four (4) different points of contact 170 through 180 s of revolution along a portion of segment S. Although FIGS. 4-10 depict twisted section 154 of a tube bundle 140 comprising seven individual tubes 120, with various points of contact 170, it will be understood that the tube bundle 140 can comprise any number of tubes 120 with any number of points of contacts 170 without limitation.
  • the intermittent twisted sections 154 of the tubes 120 can act as a support mechanism within the heat exchanger shell and further eliminate the need for baffles altogether. Further, the twisted nature of the twisted sections 154 permits for larger voids 180 between each tube 120 in a tube bundle 140, as best illustrated in the cross-sections in FIGS. 4-10. The efficiency of heat exchange between the tube-side fluid and the shell-side fluid, via the tube wall, can be further improved over known heat exchangers by a swirl flow created by the twisted segments of tubes 120 and the voids 180.
  • the swirl flow can be created by a swirling region defined by the individual tubes 120 of the tube bundle 140, and generally comprising the voids 180 along the twisted sections.
  • the shell-side fluid can travel between the voids 180, and the varying space defined thereby, and generally along the length of the tubes 120 and tube bundle 140.
  • the shell-side fluid can be acted upon by the tubes 120 depending on the orientations thereof relative to segment S, as best depicted in FIGS. 4-10, to create a swirl effect in the shell-side fluid, which can produce a swirl flow.
  • a twisted section 154 is generally adjacent to an at least one straight section 152, wherein the tubes 120 of the tube bundle 140 are generally arranged in a tighter arrangement with fewer and smaller voids between the tubes, the overall mechanical resonance of the tube 120 is not adversely affected by the spacing and voids 180 of the twisted section 154.
  • the intermittent twisted segments 154 can support the tubes 120 and tube bundles 140 within the shell in a manner that provides a highly flexible support system with enhanced heat transfer on the tube- and shell-side flows, such that each tube 120 or tube bundle 140 is generally self- supporting, even without the use of baffles.
  • Such support can be achieved, at least in part, by the twisted segments 154 which can produce tube-to-tube spaced-apart contact points 170 between adjacent tubes 120, while also defining the voids 180 discussed herein, with each individual tube 120 being secured in place by adjacent tubes 120, and facilitating securement of adjacent tubes 120.
  • Such arrangement can reduce vibration and promote easier cleaning on the shell-side through the heat exchanger 100.
  • the present inventions may comprise conventional technology (e.g., as implemented and/or integrated in exemplary embodiments, modifications, variations, combinations, equivalents, and so on) or may comprise any other applicable technology (present and/or future) with suitability and/or capability to perform the functions and processes/operations described in the specification and/or illustrated in the FIGURES. All such technology (e.g., as implemented in embodiments, modifications, variations, combinations, equivalents, and so on) is considered to be within the scope of the present inventions of the present patent document.

Landscapes

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

Abstract

Appareil d'échange de chaleur comprenant une pluralité de tubes regroupés ensemble, chacun ayant des segments torsadés segmentés. Chaque tube de la pluralité de tubes fournit un corps de tube délimitant un passage intérieur pour transporter un premier fluide et une pluralité de segments sur sa longueur comprenant une section droite et une section torsadée qui sont en communication fluidique l'une avec l'autre. Chaque tube de la pluralité de tubes fournit un axe longitudinal central sur sa longueur. Le corps de tube le long de la section torsadée présente une rotation autour de l'axe longitudinal central et le corps de tube le long de la section droite ne présente pas de rotation. Une surface extérieure du corps de tube d'un tube peut entrer en contact avec une surface extérieure du corps de tube d'un autre tube le long de la section torsadée, tandis que les surfaces extérieures de ces tubes évitent un contact le long de la section droite.
EP19727493.9A 2018-04-19 2019-04-18 Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur Pending EP3781887A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862660089P 2018-04-19 2018-04-19
PCT/IB2019/053246 WO2019202557A1 (fr) 2018-04-19 2019-04-18 Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur

Publications (1)

Publication Number Publication Date
EP3781887A1 true EP3781887A1 (fr) 2021-02-24

Family

ID=66676847

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19727493.9A Pending EP3781887A1 (fr) 2018-04-19 2019-04-18 Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur

Country Status (6)

Country Link
US (1) US20210140715A1 (fr)
EP (1) EP3781887A1 (fr)
KR (1) KR20200143396A (fr)
CN (1) CN112105882B (fr)
CA (1) CA3095856A1 (fr)
WO (1) WO2019202557A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021244433A1 (fr) * 2020-05-31 2021-12-09 杭州三花微通道换热器有限公司 Échangeur de chaleur et procédé de traitement associé

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KR100607160B1 (ko) * 2005-03-31 2006-08-02 조연섭 열교환기의 뱀브형 튜브
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CN105202950A (zh) * 2014-06-24 2015-12-30 华东理工大学 管壳式换热器
CN205784731U (zh) * 2016-05-25 2016-12-07 上海发电设备成套设计研究院 一种用于尿素热解的扭曲椭圆管空气换热器系统

Also Published As

Publication number Publication date
KR20200143396A (ko) 2020-12-23
WO2019202557A1 (fr) 2019-10-24
CA3095856A1 (fr) 2019-10-24
CN112105882B (zh) 2023-03-28
CN112105882A (zh) 2020-12-18
US20210140715A1 (en) 2021-05-13

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