WO2020141432A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2020141432A1
WO2020141432A1 PCT/IB2019/061429 IB2019061429W WO2020141432A1 WO 2020141432 A1 WO2020141432 A1 WO 2020141432A1 IB 2019061429 W IB2019061429 W IB 2019061429W WO 2020141432 A1 WO2020141432 A1 WO 2020141432A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tubular wall
shell
tube
pass
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.)
Ceased
Application number
PCT/IB2019/061429
Other languages
English (en)
Inventor
Senthilkumar Sankaralingam
Charles Philominraj
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.)
Thermax Ltd
Original Assignee
Thermax Ltd
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 Thermax Ltd filed Critical Thermax Ltd
Publication of WO2020141432A1 publication Critical patent/WO2020141432A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F28D7/1607—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 particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D7/1638—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 with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • F28D7/1646—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 with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one with particular pattern of flow of the heat exchange medium flowing outside the conduit assemblies, e.g. change of flow direction
    • 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
    • F28D7/1676—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions

Definitions

  • the present disclosure relates to the field of heat exchangers.
  • pass used hereinafter in this specification refers to, but is not limited to, a singular passage of a fluid through an enclosed space (i.e., a shell or a tube) of a heat exchanger, relative to the flow of another fluid flowing through the heat exchanger in an adjacent enclosed space (i.e., a tube or a shell respectively).
  • the pass may be made in parallel, anti-parallel, circumferential or any other manner.
  • Heat exchangers of the shell- and- tube type are known for efficiently carrying out transfer of heat from one fluid to another, thereby heating one fluid and cooling the other.
  • One fluid is made to flow through the tubes and the other, through the space in the shell exterior to the tubes.
  • a shell-and-tube heat exchanger can be used in a wide range of pressure and temperatures, and is preferred in high pressure applications such as for feedwater heating with steam, in power plant condensers, in oil refineries and in chemical industries.
  • a shell-and-tube heat exchanger is a multiple-effect evaporator system for different applications such as treatment of municipal waste and industrial effluents, use in food industry, etc.
  • preheaters use the non-condensed steam from the evaporator as heat source (only latent heat) and use it to preheat the incoming feed solution.
  • the preheaters are of shell-and-tube type with steam in the shell side and the feed solution in the tube side.
  • the preheater tubes usually get choked first due to evaporation of feed solution inside the tubes resulting in formation of hard scales, especially during turn-down operating conditions.
  • the steam condenses at a constant temperature and the wall temperature will not change due to flow turn-down conditions. Since the flow is reduced through tubes at turn down, the fluid will start to evaporate especially near tube wall due to high source temperature (i.e. steam temperature) resulting in formation of suspended solids and hard scale formation.
  • hot condensate water can be used as the heat source (sensible heat recovery) by ensuring complete condensation of steam in the evaporator itself instead of non-condensable steam (latent heat recovery).
  • the source temperature will also decrease during preheating of the feed solution at full and turn-down operating conditions resulting in avoidance of evaporation inside the tubes.
  • the flow rate of hot source fluid i.e. condensate water
  • the flow rate of hot source fluid is significantly small (for example, almost 1/3 to l/10 th of feed solution) when compared to the feed flow, based on the number of stages to effect the evaporation. It is difficult to get high heat transfer coefficient for such applications (i.e. liquid-to-liquid heat exchanger applications) where the flow of one liquid is much smaller than the other liquid resulting in big and costly heat exchangers.
  • the compaction of the heat exchanger can be done if plate heat exchangers are used. However, the plate heat exchangers will get frequently choked even if the feed solution contains less suspended solids. The plate heat exchangers then have to be frequently cleaned by opening the frame and all gaskets have to be replaced resulting in high down time and high gasket replacement costs.
  • the shell-and-tube heat exchangers are very good in terms of resistance to scale formation, ease of cleaning and less cost for gasket replacement. Therefore, a heat exchanger which is compact and capable of achieving high heat transfer coefficient is required.
  • Compact heat exchangers of the shell-and-tube type have been designed where a reversal chamber is required for added compactness.
  • the use of a reversal chamber leads to the usage of an additional element in the fabrication process, thereby increasing cost, possibly increasing size, and at the same time, not utilizing the fluid reversal process part for heat exchange.
  • This design also leads to unfavorable liquid velocity variation if used for liquid-liquid heat transfer applications.
  • the prior art design fails to provide an optimum heat transfer efficiency. There is, therefore, felt a need of a heat exchanger which eliminates the shortcomings of the arrangements as described hereinabove.
  • An object of the present disclosure is to provide a heat exchanger. Another object of the present disclosure is to provide a heat exchanger, which is compact.
  • Yet another object of the present disclosure is to provide a heat exchanger, which gives highly efficient heat transfer.
  • the present disclosure envisages a heat exchanger.
  • the heat exchanger comprises an outer tubular wall, an inner tubular wall and a plurality of tubes.
  • the inner tubular wall is spaced apart from the outer tubular wall.
  • the inner tubular wall defines a vacant tubular space on its inner side.
  • An annular space defined between the outer tubular wall and the inner tubular wall defines a shell side of the heat exchanger for transmitting a first fluid therethrough.
  • the plurality of tubes is disposed in the annular space, which transmit a second fluid therethrough. Temperature of the second fluid is different from temperature of the first fluid.
  • the outer tubular wall and the inner tubular wall have similar cross-sectional contours.
  • the outer tubular wall and the inner tubular wall have different cross-sectional contours.
  • the first fluid flows along longitudinal axis of the heat exchanger through the space between the outer tubular wall and the inner tubular wall exterior to the tubes, defining a single shell-side passes.
  • a plurality of transverse baffles is placed longitudinally between the outer tubular wall and the inner tubular wall, defining a plurality of shell-side passes.
  • a channel header is provided at each longitudinal end of the heat exchanger.
  • a plurality of partition plates is placed in the channel header.
  • the tubes passing through the channel header are configured to permit at least one tube-side pass.
  • the flow of the first fluid and the second fluid on the shell-side and the tube-side respectively can be either a co-current flow or a counter-current flow.
  • Figure 1 illustrates a schematic cross-sectional view of tube-side and shell-side flow of a heat exchanger to depict counter-current flow, having multiple (four) shell-side passes and multiple (four) tube-side passes, according to an embodiment of the present disclosure
  • Figure 2 illustrates a schematic cross-sectional view of a multi-pass shell-side flow and single tube-side pass in a heat exchanger according to another embodiment of the present disclosure
  • Figure 3 illustrates a schematic cross-sectional view of a heat exchanger with multiple passes on tube side and single pass on shell side, according to yet another embodiment of the present disclosure
  • Figure 4 illustrates a schematic cross-sectional view of a heat exchanger with a single pass on tube side and a single pass on shell side, according to still another embodiment of the present disclosure.
  • Figure 5 illustrates a schematic cross-sectional view of tube-side and shell-side flow of a heat exchanger to depict co-current flow, having multiple (four) shell-side passes and multiple (four) tube-side passes, according to an embodiment of the present disclosure.
  • first, second, third, etc. should not be construed to limit the scope of the present disclosure as the aforementioned terms may be only used to distinguish one element, component, region, layer or section from another component, region, layer or section. Terms such as first, second, third etc., when used herein do not imply a specific sequence or order unless clearly suggested by the present disclosure. Terms such as“inner”,“outer”,“beneath”,“below”,“lower”,“above”,“upper” and the like, may be used in the present disclosure to describe relationships between different elements as depicted from the figures.
  • the shell-and-tube heat exchanger 100 of the present disclosure comprises an outer tubular wall 10, an inner tubular wall 20 and a plurality of tubes 30.
  • the inner tubular wall 20 is spaced apart from the outer tubular wall 10.
  • the inner area of the inner tubular wall 20 defines a vacant tubular space 25.
  • An annular space 15 is defined between the outer tubular wall and the inner tubular wall.
  • the plurality of tubes 30 is disposed between the outer tubular wall 10 and the inner tubular wall 20 in the annular space 15.
  • a first fluid flows through the annular space 15 between the outer tubular wall 10 and the inner tubular wall 20 exterior to the tubes 30 and a second fluid flows through the tubes 30.
  • the flow of process fluids in the heat exchanger 100 is“straight flow through path” both on the shell-side which includes the annular space 15 and on the tube-side.
  • the first fluid and the second fluid flow along the longitudinal axis of the heat exchanger 100 through the annular space 15 and through the tubes 30 respectively.
  • transverse baffles 40 are placed end- to-end along the length of the tubular walls 10 and 20, wherein the length of baffles 40 is lesser than the tubes 30 such that it facilitates multiple shell-side passes.
  • one or more channel headers are provided at each longitudinal end of the heat exchanger 100.
  • partition plates are placed in the channel headers of the heat exchanger 100. Based on design requirements and optimization, the number of tube-side passes and shell-side passes can be determined. The number of passes on the shell side is maintained by the transverse baffles 40, whereas the number of passes on the tube side is maintained by the partition plates in the channel headers of the heat exchanger 100. The number of tube-side passes is one more than the number of the partition plate(s) in the channel headers. The number of shell-side passes is equal to the number of baffles.
  • the shell-side passes are marked as T, TG, TIG and TV’ in Figure 1, 2 3, 4 and 5 and the tube-side passes are marked as T’,‘2’,‘3’ and‘4’.
  • the arrangement is a shell and tube heat exchanger 100 which is configured to permit four passes on shell side and four passes on tube side.
  • the tube-side passes and the shell-side passes are such that the first tube-side pass (pass 1) is associated with the fourth shell-side pass (pass IV), the second tube-side pass (pass 2) is associated with the third shell-side pass (pass III), third tube-side pass (pass 3) is associated with the second shell-side pass (pass II) and a fourth tube-side pass (pass 4) is associated with the first shell- side pass (pass I).
  • the arrangement in Figure 1 depicts counter-current flow on tube side and shell side of the heat exchanger 100.
  • the arrangement corresponds to a shell and tube heat exchanger 100 which is configured to permit four passes on shell side and one pass on tube side.
  • the tube-side pass 1 is associated with four shell-side passes i.e. pass I, pass II, pass III and pass IV.
  • the arrangement corresponds to a shell and tube heat exchanger 100 which is configured to permit one pass on shell side and four passes on tube side.
  • the tube-side passes 1, 2, 3 and 4 are associated with single shell-side pass I.
  • the arrangement corresponds to a shell and tube heat exchanger 100 which is configured to permit a single tube-side pass 1 associated with a single shell-side pass I.
  • the arrangement corresponds to a shell and tube heat exchanger 100 which is configured to permit four passes on shell side and four passes on tube side.
  • the tube-side passes and the shell-side passes are such that the first tube- side pass (pass 1) is associated with the first shell-side pass (pass I), the second tube-side pass (pass 2) is associated with the second shell-side pass (pass II), third tube-side pass(pass 3) is associated with the third shell-side pass (pass III) and a fourth tube-side pass (pass 4 ) is associated with the fourth shell-side pass (pass II).
  • the arrangement in Figure 5 depicts co current flow on tube side and shell side of the heat exchanger.
  • Figures 1, 2, 3, 4 and 5 illustrate few of the various possible configurations of having either a single pass or a multiple pass of both tube-side and shell-side process fluids. Since provision of the inner tubular wall 20 allows having a relatively smaller flow area in the shell side, the process fluid with less flow rate can be allotted to the shell side, in a preferred embodiment of the present invention.
  • velocity of the process fluid allotted in the shell side is further increased by increasing the number of baffles 40 in the shell side.
  • feed solution with scaling tendency is passed through the heat transfer tubes.
  • the number of tube-side passes is increased based on compaction requirements and pressure drop penalty.
  • the allocation of process fluids in the annular space 15 and the tube 30 is done based on process requirements and design optimization. Diameter of heat transfer tubes 30, number of heat transfer tubes 30, number of tube side -passes, number of longitudinal baffles 40 (or shell-side passes), diameter of outer tubular wall 10 and diameter of inner tubular wall 20 are variables and are designed based on process requirements on a case-to-case basis. Also, in the exemplary embodiments of the invention, the flow configuration of the hot and the cold fluid is either“co-current” or“counter current” based on process requirements.
  • pressure drop in the heat exchanger of the present disclosure is within an acceptable range. Even stringent pressure drop constraints of vacuum systems can also be achieved by means of“straight flow through path” and appropriate selection of diameters of tubes, inner tubular wall 20, outer tubular wall 10, number of tube-side and shell-side passes.
  • the inner tubular wall 20 enhances the heat transfer by reducing the available flow area in the shell-side and maintaining a“straight flow through path” for very less pressure drop resulting in a compact and energy-efficient heat exchanger.
  • the heat exchanger of the present disclosure also provides an optimum heat transfer efficiency especially for liquid-to-liquid heat exchange applications. Since the flow area is reduced due to the inner tubular wall, the heat transfer efficiency is quite good even at turn down operating conditions. Thus, the heat exchanger has a good turndown operating capability.
  • the heat exchanger of the present disclosure is also resistant to scale formation, on both shell and tube sides. The sensible heat recovery process will ensure that evaporation of feed solution will not take place inside the heat transfer tubes during rated and turn down operating conditions. Since the evaporation of the feed solution does not occur, scale formation will also be very less as compared to prior art.
  • the walls (i.e., shells) or tubes can be cleaned easily, as compared to the conventional shell-and-tube heat exchangers, in which the shell cannot be easily cleaned due to transverse baffles).
  • Embodiments are provided so as to thoroughly and fully convey the scope of the present disclosure to the person skilled in the art. Numerous details are set forth, relating to specific components, and methods, to provide a complete understanding of embodiments of the present disclosure. It will be apparent to the person skilled in the art that the details provided in the embodiments should not be construed to limit the scope of the present disclosure. In some embodiments, well-known processes, well-known apparatus structures, and well-known techniques are not described in detail.
  • the heat exchanger of the present disclosure is highly resistant to scale formation on both shell and tube sides;
  • o Walls i.e., shells
  • tubes can be cleaned easily (in conventional design the shell cannot be easily cleaned due to transverse baffles);

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  • 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

La présente invention concerne un échangeur de chaleur (100). L'échangeur de chaleur (100) comprend une paroi tubulaire externe (10), une paroi tubulaire interne (20) et une pluralité de tubes (30). La paroi tubulaire interne (20) est disposée à distance de la paroi tubulaire externe (10). La paroi tubulaire interne (20) définit un espace tubulaire (25) sur son côté interne. Un espace annulaire (15) entre la paroi tubulaire externe (10) et la paroi tubulaire interne (20) définit un côté coque de l'échangeur de chaleur (10) à travers lequel un premier fluide est transmis. La pluralité de tubes (30) est disposée dans l'espace annulaire (15), ce qui permet de transmettre un second fluide à travers celui-ci. La présence de la paroi tubulaire interne (20) améliore l'efficacité de transfert de chaleur, optimise les variations de pression et améliore la résistance à l'entartrage sur le côté coque et le côté tube.
PCT/IB2019/061429 2019-01-02 2019-12-30 Échangeur de chaleur Ceased WO2020141432A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN201921000201 2019-01-02
IN201921000201 2019-01-02

Publications (1)

Publication Number Publication Date
WO2020141432A1 true WO2020141432A1 (fr) 2020-07-09

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ID=71406819

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2019/061429 Ceased WO2020141432A1 (fr) 2019-01-02 2019-12-30 Échangeur de chaleur

Country Status (1)

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WO (1) WO2020141432A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113465414A (zh) * 2021-07-06 2021-10-01 包头华鼎铜业发展有限公司 一种低压降耐腐管壳式换热器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4871014A (en) * 1983-03-28 1989-10-03 Tui Industries Shell and tube heat exchanger
US9127894B2 (en) * 2011-04-13 2015-09-08 Emitec Gesellschaft Fuer Emissiontechnologie Mbh Device having a heat exchanger for a thermoelectric generator of a motor vehicle and motor vehicle having the device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4871014A (en) * 1983-03-28 1989-10-03 Tui Industries Shell and tube heat exchanger
US9127894B2 (en) * 2011-04-13 2015-09-08 Emitec Gesellschaft Fuer Emissiontechnologie Mbh Device having a heat exchanger for a thermoelectric generator of a motor vehicle and motor vehicle having the device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113465414A (zh) * 2021-07-06 2021-10-01 包头华鼎铜业发展有限公司 一种低压降耐腐管壳式换热器

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