EP2564144A2 - Échangeur thermique - Google Patents

Échangeur thermique

Info

Publication number
EP2564144A2
EP2564144A2 EP11721636A EP11721636A EP2564144A2 EP 2564144 A2 EP2564144 A2 EP 2564144A2 EP 11721636 A EP11721636 A EP 11721636A EP 11721636 A EP11721636 A EP 11721636A EP 2564144 A2 EP2564144 A2 EP 2564144A2
Authority
EP
European Patent Office
Prior art keywords
heat
chamber
heat exchanger
coolant
heat exchanging
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.)
Withdrawn
Application number
EP11721636A
Other languages
German (de)
English (en)
Inventor
Dumitru Fetcu
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.)
Econotherm UK Ltd
Original Assignee
Econotherm UK 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 Econotherm UK Ltd filed Critical Econotherm UK Ltd
Publication of EP2564144A2 publication Critical patent/EP2564144A2/fr
Withdrawn legal-status Critical Current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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D1/00—Evaporating
    • B01D1/06—Evaporators with vertical tubes
    • B01D1/08—Evaporators with vertical tubes with short tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates to a heat exchanger and particularly, but not exclusively to a heat exchanger comprising heat pipes.
  • a heat pipe is a hermetically sealed evacuated tube typically comprising a mesh or sintered powder wick and a working fluid in both the liquid and vapor phase.
  • the liquid turns to vapor upon absorbing the latent heat of vaporization.
  • the hot vapor subsequently passes to the cooler end of the tube where it condenses and gives out the latent heat to the tube.
  • the condensed liquid then flows back to the hot end of the tube and the vaporization-condensation cycle repeats. Since the latent heat of vaporization is usually very large, considerable quantities of heat can be transported along the tube and a substantially uniform temperature distribution can be achieved along the heat pipe.
  • a problem with this arrangement is that even though the heat transfer area on the inside of the tube, namely the liquid side, is substantially the same as the heat transfer area on the outside of the tube, namely the vapour side, the heat transfer coefficient on the liquid side is much less that on the vapour side.
  • the heat transfer coefficient on the cooling side is largely dependent on the velocity of the liquid through the tube. It is found that increasing the liquid velocity causes the heat transfer coefficient to increase. As a result, it is common to utilise high liquid velocities to increase the heat transfer coefficient on the liquid side. However, this requires large pumps and an increase in liquid pressure within the heat exchanger.
  • the heat transfer across the tube will also be influenced by the material of the tube and the thickness of the tube wall. Accordingly, brass and copper are typically utilised since these materials provide a good thermal conductivity, and the tube wall is kept as thin as possible to ensure a suitable transfer of heat across the tube wall. Brass and copper however, are expensive materials and owing to the reduced thickness of the tube wall, it is found such tubes are sensitive to thermal stresses, particularly during the start-up and shut-off periods when there is a significant change in temperature. We have now devised an improved heat exchanger comprising a plurality of heat pipes, which alleviates the above-mentioned problems.
  • a heat exchanger for condensing a vapour to a condensate, the exchanger comprising a first heat exchanging chamber, a second heat exchanging chamber and an array of heat pipes which are arranged to extend from within the first heat exchanging chamber to within the second heat exchanging chamber;
  • the first heat exchanging chamber comprising an inlet for receiving a coolant into the chamber and an outlet through which the coolant can exit the first chamber, the coolant being arranged to pass over the portion of the heat pipes which extend within the first chamber;
  • the second heat exchanging chamber comprising an inlet for receiving the vapour into the chamber and an outlet through which the condensate can exit the second chamber, the vapour being arranged to pass over the portion of the heat pipes which extend within the second chamber;
  • the portion of at least one of the heat pipes within the first heat exchanging chamber comprises a fin arranged in contact therewith which is arranged to increase thermal transfer between said portion of the heat pipe and the coolant.
  • the provision of at least one fin increases thermal transfer between said portion of the heat pipe and the coolant to compensate for the reduced heat transfer coefficient of the coolant within the first heat exchanging chamber compared with the heat transfer coefficient of the vapour within the second heat exchanging chamber.
  • the portion of each of the heat pipes within the first heat exchanging chambers comprises a fin.
  • the or each fin is arranged to extend in a substantially helical path around the portion of the at least one or each heat pipe within the second heat exchanging chamber.
  • the portion of at least one of the heat pipes within the second heat exchanging portion comprises a fin arranged in contact therewith, which is arranged to increase thermal transfer between said portion of heat pipe and the coolant.
  • each of the heat pipes within the second heat exchanging portion comprises a fin arranged in contact therewith which is arranged to increase thermal transfer between said portion of the heat pipe and the coolant.
  • the or each fin is arranged to extend in a substantially helical path around the portion of the at least one or each heat pipe within the second heat exchanging chamber.
  • the condensate film which develops upon the tubes acts as a thermal barrier which prevents further vapour from becoming suitably cooled.
  • This film typically increases in thickness until the force of gravity overcomes the surface tension of the condensate upon the tube and thus causes the condensate to move off the tube.
  • the provision of the helical fins on the portion of the heat pipes in the second heat exchanging chamber provides for an additional surface for the film to develop and thus serves to reduce the overall thickness of the film upon the surface of the heat pipe.
  • the helical fin serves to channel the condensate off the heat pipe.
  • the number of turns of the or each fin per unit length around the or each heat pipe in the first heat exchanging chamber is greater than number of turns of the or each fin per unit length around the or each heat pipe in the second heat exchanging chamber.
  • the first and second heat exchanging chambers are preferably separated by a separation plate.
  • the plurality of heat pipes are preferably supported within the heat exchanger by the support plate which is coupled to the heat pipes intermediate opposite ends thereof. Accordingly, the separation plate obviates the requirement to support the heat pipes at their free end and as such the free ends of the heat pipes can be left uncoupled and spaced from respective first and second chamber walls. This therefore enables the heat pipes to expand and contract along their length during use thereby minimizing thermal stresses upon the heat pipes.
  • the first and second heat exchanging chambers preferably further comprise at least one baffle for directing the flow of liquid and vapour, respectively, over the respective portions of the heat pipes.
  • the inlet and outlet of the first heat exchanging chamber are arranged to pass the coolant into and out of the first chamber in a direction which is substantially transverse to a longitudinal axis of the heat pipes.
  • the inlet and the outlet of the second heat exchanger are arranged to pass the coolant into and out of the second chamber in a direction which is substantially parallel to a longitudinal axis of the heat pipes.
  • Figure 1 is a longitudinal sectional view through a conventional U-tube shell and tube type condenser
  • Figure 2 is a longitudinal sectional view of the heat exchanger according to an embodiment of the present invention.
  • Figure 3 is a transverse sectional view of the heat exchanger of figure 2, at position A-A;
  • FIG 4 is a transverse sectional view of the heat exchanger of figure 2, at position B-B.
  • the heat exchanger 10 comprises a first heat exchanging chamber 1 1 and a second heat exchanging chamber 12.
  • Each chamber 1 1 , 12 comprises a substantially cylindrical housing 13, 14 having substantially the same diameter, which are mounted one on top of the other such that a longitudinal axis of the first chamber 1 1 extends in a substantially collinear relationship with a longitudinal axis of the second chamber 12 and thus the heat exchanger 10.
  • the first chamber 1 1 of the heat exchanger 10 is disposed above the second chamber 12 and comprises an inlet 15 and an outlet 16 which are disposed within an arcuate side wall of the housing 13.
  • the inlet and outlet 15, 16 of the first chamber 1 1 are spaced longitudinally of the chamber 1 1 and are arranged to enable a coolant such as water, to pass into and out from the chamber 1 1 , respectively.
  • the first chamber 1 1 further comprises a passage 17 which extends along the first chamber 1 1 substantially along the longitudinal axis thereof.
  • the passage 17 is defined by a substantially cylindrical wall 18 which seals the interior of the first chamber 1 1 from the passage 17, and extends from an opening 19 disposed in an upper end wall 20 of the first chamber 1 1 to an upper region of a separation plate 21 .
  • the separation plate 21 comprises a first aperture 22 disposed substantially at the centre thereof which is arranged to align with the cylindrical wall 18 defining the passage 17, such that the wall 18 extends substantially around a periphery of the first aperture 22.
  • the second chamber 12 is secured to the underside of the separation plate 21 and thus the first chamber 1 1 , and comprises an outlet 23 disposed substantially upon the longitudinal axis of the chamber 12, within a lower end wall 24 thereof.
  • the first aperture 22 disposed within the separation plate 21 serves as an inlet to the second chamber 12, such that the vapour to be condensed, for example steam, can pass into the second chamber 12 from the opening 19 disposed in the upper end wall 20 of the first chamber 1 1 through the passage 17 and into the second chamber 12.
  • the heat exchanger 10 further comprises a plurality of substantially linear heat pipes 25 which extend from within the first chamber 1 1 , through an array of second apertures 26 disposed within the plate 21 around the first aperture 22, and terminate in the second chamber 12 so as to enable heat to be transferred between the chambers 1 1 , 12.
  • the heat pipes 25 extend substantially parallel to the longitudinal axis of the first and second chambers 1 1 , 12 and are configured in a substantially arcuate arrangement of rows of heat pipes 25, as illustrated in figures 3 and 4 of the drawings, the radius of curvature of each arcuate row being centered substantially on the longitudinal axis.
  • each chamber 1 1 , 12 comprises a plurality of arcuate rows of heat pipes 25, having different radii of curvature.
  • the heat pipes 25 are supported within the heat exchanger 10 by the separation plate 21 by a series of collars 27 which separately extend within each of the second apertures 26 and which further serve to seal the heat pipes 25 to the separation plate 21 such that the interior of the first and second chambers 1 1 , 12 remain isolated from each other.
  • the longitudinal ends of the heat pipes 25 are uncoupled and spaced from the upper end wall 20 of the first chamber 1 1 and the lower end wall 24 of the second chamber 12, such that the heat pipes 25 are free to expand and contract and thus relieve any thermal stresses which would otherwise develop during use of the heat exchanger 10.
  • each of the heat pipes 25 which extend in the first chamber 1 1 comprise a helical fin 28 disposed around the outer surface thereof which extend substantially along the length of the portion of the respective heat pipe 25 within the first chamber 1 1 .
  • the fins 28 comprise a metallic strip which extends away from the outer surface of the respective heat pipe 25, in direction which is substantially perpendicular to the longitudinal axis of the respective heat pipe 25.
  • the fins 28 are found to increase the transfer of heat between said portion of the heat pipes 25 and the coolant to compensate for the reduced heat transfer coefficient of the coolant within the first heat exchanging chamber 1 1 , compared with the heat transfer coefficient of the vapour within the second heat exchanging chamber 12.
  • each of the heat pipes 25 which extend in the second chamber 12 similarly comprise a helical fin 29 disposed around the outer surface thereof which extend substantially along the length of the portion of the respective heat pipe 25 within the second chamber 12.
  • the fins 29 similarly comprises a metallic strip which extend away from the outer surface of the respective heat pipe 25, in direction which is substantially perpendicular to the longitudinal axis of the respective heat pipe 25.
  • the number of turns of the fins 28 per unit length around the heat respective pipe 25 in the first heat exchanging chamber 1 1 is arranged to be greater than in the second heat exchanging chamber 12 to ensure that the increase in heat transfer coefficient associated with the coolant in the first chamber 1 1 due to the presence of the fins 28, is not offset by the provision of fins 29 on the portion of the heat pipes 25 in the second chamber 12.
  • the first chamber 1 1 of the heat exchanger 10 further comprises a plurality of baffles 30 which extend across the first chamber 1 1 substantially transverse to the longitudinal axis of the heat exchanger 1 1 , and serve to direct the flow of coolant back and forth across the portion of the heat pipes 25 within the first chamber 1 1 , as the coolant flows along the chamber 1 1 between the inlet 15 and the outlet 16.
  • the second chamber 12 similarly comprises a plurality baffles 31 which extend across the second chamber 12, substantially transverse to the longitudinal axis of the heat exchanger 10, and serve to direct the flow of vapour back and forth across the portion of the heat pipes 25 within the second chamber 25, to ensure that the vapour becomes cooled and thus condenses within the second chamber 12.
  • hot gas from an industrial process (not shown) for example, is passed into the passage 17 of the first chamber 1 1 through the opening 19 disposed in an end wall 20 of the first chamber 1 1 .
  • the gas subsequently passes into the second chamber 12 where it becomes redirected radially outwardly of chamber 12, back and forth across the heat pipes 25 by the baffles 31 .
  • the hot gas passes across the heat pipes 25, it gives up the heat associated therewith to the heat pipes 25 thereby causing the temperature of the heat pipes 25 to rise.
  • the hot gas thus becomes cooled in moving along the second chamber 12 between the inlet 22 and the outlet 23.
  • the increase in temperature of the portion of the heat pipes 25 within the second chamber 12 becomes transferred to the portion of the heat pipes 25 within the first chamber 1 1 , which subsequently becomes cooled by the flow coolant therein.
  • the intimate contact and increased surface area of the portion of the heat pipes 25 in the first chamber 1 1 due to the presence of the fins 28, provides an efficient removal of heat from the heat pipe 25, such that the portion of the heat pipes 25 in the second chamber 12 can further absorb the heat from the gas and thus cool the gas.
  • This increased surface area provides for an increased effective thermal coefficient and thus a reduced length of the portion of the heat pipe 25 in the first chamber 1 1 compared to the conventional tube of the shell and tube condenser.
  • the gas As the gas becomes cooled along the second chamber 12, it condenses upon the fins 29 associated with the portion of the heat pipes 25 in the second chamber 12, and a film of liquid (not shown) develops thereon.
  • the fins 29 provide an alternative, or at least an additional surface to the surface of the respective heat pipe 25, for the film (not shown) to develop and therefore the ensures that the thickness of the film (not shown) does not exceed a threshold whereby it would insulate the respective heat pipe 25 from further hot gases and thus reduce the ability of the heat pipes 25 to suitably condense the hot gas.
  • the helical nature of the fins 29 upon the portion of the heat pipes 25 within second chamber 12 provides a run-off slope for the condensate along the respective heat pipes 25 and out of the chamber 12 through the outlet 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur thermique conçu pour condenser de la vapeur en un condensat, L'échangeur thermique comprend une première chambre d'échange thermique, une seconde chambre d'échange thermique et un réseau de caloducs qui sont disposés de manière à s'étendre depuis l'intérieur de la première chambre d'échange thermique jusqu'à l'intérieur de la seconde chambre d'échange thermique. La première chambre d'échange thermique comprend un orifice d'amenée pour recevoir un fluide de refroidissement dans la chambre et un orifice de sortie à travers lequel le fluide de refroidissement peut sortir de la première chambre; le fluide de refroidissement étant conçu pour passer par dessus la portion des caloducs qui s'étendent à l'intérieur de la première chambre. La seconde chambre d'échange thermique comprend un orifice d'amenée pour recevoir la vapeur dans la chambre et un orifice de sortie à travers lequel le condensat peut sortir de la seconde chambre, la vapeur passant par dessus la portion des caloducs qui s'étendent à l'intérieur de la seconde chambre. L'échangeur thermique comprend également une ailette ménagée de manière à être en contact avec la portion d'au moins l'un des caloducs se trouvant à l'intérieur de la première chambre d'échange thermique, laquelle ailette est conçue pour augmenter le transfert thermique entre la portion du caloduc et le fluide de refroidissement.
EP11721636A 2010-04-26 2011-04-19 Échangeur thermique Withdrawn EP2564144A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1006863.3A GB2479867B (en) 2010-04-26 2010-04-26 Heat exchanger
PCT/GB2011/050775 WO2011135334A2 (fr) 2010-04-26 2011-04-19 Échangeur thermique

Publications (1)

Publication Number Publication Date
EP2564144A2 true EP2564144A2 (fr) 2013-03-06

Family

ID=42270775

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11721636A Withdrawn EP2564144A2 (fr) 2010-04-26 2011-04-19 Échangeur thermique

Country Status (4)

Country Link
US (1) US20130075064A1 (fr)
EP (1) EP2564144A2 (fr)
GB (1) GB2479867B (fr)
WO (1) WO2011135334A2 (fr)

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US20140158514A1 (en) * 2012-12-07 2014-06-12 Advanced Water Recovery, Llc Methods of separating salts and solvents from water
US20160216040A1 (en) * 2015-01-23 2016-07-28 Indigo Power Systems Llc Heat exchanger
ITUB20150576A1 (it) * 2015-04-24 2016-10-24 Hexsol Italy Srl Scambiatore di calore a fascio tubiero e struttura perfezionata
WO2017100604A1 (fr) * 2015-12-09 2017-06-15 Fulton Group N.A., Inc. Système compact de chauffage de fluide à grand volume de flux thermique utilisant une chute élevée de pression de l'échangeur de chaleur
US10962257B2 (en) 2015-12-09 2021-03-30 Fulton Group N.A., Inc. Compact fluid heating system with high bulk heat flux using elevated heat exchanger pressure drop
CN111964499A (zh) * 2020-08-18 2020-11-20 哈尔滨工业大学（深圳） 热管与地热采集装置
CN113532169B (zh) * 2021-07-23 2023-08-08 福建龙净环保股份有限公司 一种热管烟气换热器

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Also Published As

Publication number Publication date
WO2011135334A3 (fr) 2012-01-12
US20130075064A1 (en) 2013-03-28
WO2011135334A2 (fr) 2011-11-03
GB2479867A (en) 2011-11-02
GB201006863D0 (en) 2010-06-09
GB2479867B (en) 2016-03-02

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