US3749160A - Tube bank heat exchanger and unit of such heat exchangers - Google Patents

Tube bank heat exchanger and unit of such heat exchangers Download PDF

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Publication number
US3749160A
US3749160A US00051414A US3749160DA US3749160A US 3749160 A US3749160 A US 3749160A US 00051414 A US00051414 A US 00051414A US 3749160D A US3749160D A US 3749160DA US 3749160 A US3749160 A US 3749160A
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United States
Prior art keywords
heat exchanger
mantle
jacket
gas
flow
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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.)
Expired - Lifetime
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US00051414A
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English (en)
Inventor
R Vestre
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Norsk Hydro ASA
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Norsk Hydro ASA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1838—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines the hot gas being under a high pressure, e.g. in chemical installations
    • 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
    • F28D7/06—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 having a single U-bend
    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the tube bank in the heat exchanger mantleis encompassed by a jacket extending coaxially through the mantle spaced from the inside of the mantle.
  • the heat exchanger mantle is provided with two gas access openings positioned at the same crosssectional plane on the mantle and substantially at the mid-point thereof.
  • One of the accesses communicates directly with the inside of the jacket, the other access opening communicates with the spacing between the inside of the mantle and the outside of the jacket.
  • the jacket is open at both ends, whereby the gas stream when introduced into one of the access openings is divided into two gas streams each of which flows in opposite directions through the heat exchanger, the streams tuming at each respective end of the heat exchanger and being unified anew before leaving the heat exchanger.
  • the present invention relates to improvements in tube bank heat exchangers of the kind provided with an internal jacket encompassing the tube bank in the mantle resulting in a two-way gas flow through the heat exchanger, namely through the jacket and through the spacing between the jacket and the inside of the heat exchanger mantle, respectively.
  • the gas may after introduction into the heat exchanger first flow through said spacing or alternatively first flow through the jacket, depending upon whether the heat exchanger shall be used as a cooler or as a heater.
  • the present invention relates furthermore to a unit of such heat exchangers coupled together in series.
  • a particular object of the invention is to solve the problems prevailing when large gas quantities having high temperature, possibly also high pressure, shall be cooled, for instance by means of feed water or steam which is pre-heated in pre-heaters, and the invention shall in the following be described with these objects in mind, but it shall be understood that the heat exchanger in accordance with the invention and units of such, also can be used for other purposes with similar advantages.
  • the tube bank heat exchangers preferably used When cooling large quantities of gas having high temperature and also having large pressure the tube bank heat exchangers preferably used will most often attain a somewhat slender, elongated shape and in order to avoid too large sizes one must utilize several .heat exchangers which are coupled in series and/or parallelly coupled units. With these types of heat exchangers the gas flow speed or gas rate will be high, which again results in a relatively high pressure loss through the system. This problem can be solved by employing a greater number of heat exchangers, and for instance introducing the gas at the mid-point of the heat exchanger and arranging outlets at both ends.
  • a further problem in connection with known methods and heat exchangers is that when the gas temperature exceeds 500 550 C, one cannot utilize ferritic steel material in the pressure mantle, but must instead utilize austenitic 18/8 steel, or for instance highpercentage nickel alloy, which as known is very expensive.
  • the main object of the invention is to provide a new type of heat exchanger whereby there can be reduced or eliminated the problem arising in consequence of the expansions and contractions in the heat exchanger and tubing materials.
  • a further object of the invention is to provide a new type of heat exchanger making it possible to reduce or avoid the corrosion problems due to high temperatures, tensions and stresses in the material, etc.
  • a particular object of the invention is to provide an improved type of heat exchanger and heat exchanger units for heating or cooling hot gases subjected to high pressure which simultaneously renders it possible to utilize relatively reasonable material in the heat exchanger systems.
  • a further aim of the invention is to provide a new type of heat exchanger making it possible to increase the gas flow rate through the heat exchanger.
  • a further object of the invention is to provide a new type of heat exchangers which in a particularly desirable manner can be-coupled together in series providing a unit which presents a special advantageous flow pattern.
  • the tube bank heat exchanger in accordance with the invention is of the kind wherein the tube bank in the heat exchanger mantle is encompassed by a jacket extending coaxially through the mantle with a spacing from the inside of the mantle, the heat exchanger mantle provided with two accesses serving as gas inlet and outlet respectively, one of the accesses communicating directly with the inside of the jacket, for providing a flow of gas through the jacket between the heat exchanger tubes, the other access opening communicating with the spacing between the inside of the mantle and the outside of the jacket.
  • the heat exchanger in accordance with the invention is characterized therein that both access openings are positioned at the same cross-sectional plane and substantially at the mid-point of the tube bank, the jacket being open at both ends,
  • a unit comprising at least two heat exchangers in accordance with the invention coupled in series is characterized therein that the said heat exchangers are coupled in opposite directions with respect to the gas flow pattern therein so that the gas in the first heat exchanger firstly flows through the inner jacket and thereafter leaves the jacket at both ends of the mantle and flows back between the jacket and the inside of the mantle in a two-way, oppositely directed flow, being unified at the access opening serving as outlet, said outlet being coupled to the access opening on the second heat exchanger.
  • the access opening on the second heat exchanger leads into the spacing between the jacket and the mantle inside whereby the gas flow here firstly will streams the spacing and then return to the midpoint of the second heat exchanger and leaves the second heat exchanger to the access opening leading from the jacket and to the access on the mantle.
  • FIGS. 1 shows a longitudinal cross-sectional view through a preferred embodiment of a heat exchanger in accordance with the invention
  • FIG. 2 shows a similar longitudinal cross-sectional view through two such heat exchangers coupled in senes.
  • reference 2 designates the pressure mantle on an elongated heat exchanger which at the mid-point is provided with two tube connections 4 and 6 which serve as the inlet and the outlet of the heat exchanger, respectively, for the gas which shall be cooled or heated.
  • a head 8 At the one end of the heat exchanger is mounted a head 8 with a U-shaped tube bank l which extends through the inside of the mantle and which in known fashion is provided with inlet and outlet designated and 12, respectively, such that said tube bank can be supplied with a heat treatment media, for instance cooling water or steam.
  • a tube-shaped jacket 16 which as shown encompasses the tube bank 10.
  • the jacket 16 is open at both ends .18 and 20 and is at the mid-point provided with a pipe connection 22 which extends outwards and into the pipe connection 4 on the mantle.
  • the jacket 16 is provided with a substantially smaller diameter than the diameter of the mantle so that between the jacket and the inside of the mantle there is provided a relatively large spacing 17, the jacket being kept in place by means of circumferentially arranged spacers 24 which rest displaceably against the inside space of the mantle, or vice versa.
  • the jacket 16 is thus fixed in the mantle only by means of the pipe connection 22, which as mentioned is journalled into the pipe connection 4 on the mantle.
  • gas volumes par example shall be cooled down from a high temperature
  • the gas is introduced in the direction of the arrow A into the pipe connection 4 and the gas will flow from same via the pipe connection 22 into the jacket 16 directly into the tube bank wherein the gas flow will divide into two equal streams which will flow in opposite directions and are designated with the arrows 8-8.
  • the tube bank an in a known manner be provided with baffles such that the gas will flow partly longitudinally and partly transversely through the tube bank).
  • the gas streams will flow out of the jacket through the opening 18 and and will turn 180 as shown with the arrows C-C and thereafter flow back through the spacing 26 to the midpoint of the heat exchanger where the gas streams anew will be unified at the arrows D-D and flow together out of the pipe connection 6.
  • the flow pattern as shown for the gas will (as mentioned) be utilized when gas is to be cooled.
  • the flow pattern through the heat exchanger is reversed so that the gas initially is introduced through the outlet 6, and flows through the spacing 17.
  • the gas will then primarily be heated in the jacket and will reach the highest temperature towards the outlet of the jacket, that is at the inlet 4 whereby the heated gas will not come into direct contact with the pressure mantle 2.
  • thermo-dynamical imperfection of the operation of the heat exchanger illustrated in H6. is that only one half of the U-shaped tube bank will be utilized in accordance with the counter flow heat exchanger principle, but thermodynamical and economical calculations show that these circumstances are of minor importance compared with the advantages which are obtained.
  • thermodynamical and economical calculations show that these circumstances are of minor importance compared with the advantages which are obtained.
  • the fact that the gas is flowing in two directions through the heat exchanger so that the gas speed or rate can be increased substantially is a large advantage.
  • a heat exchanger in accordance with the invention can with rather special thermodynamical and structural advantages be utilized in connection with two or more such heat exchangers coupled in series.
  • Such in series coupling or heat exchangers are utilized, as known, particularly in connection with the cooling of very hot gases subjected to high pressures.
  • problems in connection with the size and the weight of the heat exchanger it is not possible to obtain the desired temperature fall across one single heat exchanger, and one utilizes therefore a number of parallelly and/or in series coupled heat exchangers.
  • Series coupled heat exchangers cause however particular problems, for instance because the temperatures in adjacent that exchangers then necessarilywill be different due to the stepwise heat exchanging which will take place.
  • the gas will in one first heat exchanger initially flow directly into the internal jacket and from this return in the opposite direction through the spacing between the jacket and the mantle, flow out through the outlet and from said outlet of the first heat exchanger flow into the inlet on the second heat exchanger and in this initially flow through the spacing between the inside of the mantle and the jacket and thereafter flow through the jacket and from the same directly out through the outlet of the jacket and out through the pipe connection on the mantle.
  • FIG. 2 Two heat exchangers, coupled into seriesas above described, are illustrated in FIG. 2, the flow pattern being illustrated by means of arrows and heat exchanger process which here takes place shall in the following be illustrated in connection with a practical example.
  • a gas quantity of 250,000 m /h and a maximum temperature of 570 C and pressure of 30 kp/cm shall be cooled by means of high pressure steam (1 l0 kplcm which shall be superheated.
  • the high steam pressure uses a heat exchanger with a tube bank consisting of U- tubes where the steam pass through the tubing and the gas on the outside of the tubing.
  • the large gas quantity makes it preferable to divide the gas flow into two parallel flows and the large cooling ratemakes it necessary to lead each flow through two in series coupled heat exchangers, such that the unit comprises all together four heat exchangers which all are of the same size.
  • FIG. 2 shows only two in series coupled heat exchangers designated A and B.
  • the reference numbers 70 and 72 designate the outlet and inlet headers for the high pressure steam and also the header plates, 74 is the U-shaped tube bank, 76 the baffles, 78 and 80 the pressure'mantles, 82, 84, 86, and 88 are the gas pipe connections including flanges, 90, 92 are jackets for guiding the gas in accordance with the invention, while the reference numbers 93, 94, 95, 96 and 97 are pipes and flanges for high pressure steam.
  • the hot gas comes in through the pipe 82 on the midpoint of the heat exchanger and is passed through the inside of the jacket 90 which is not pressure sustaining.
  • the hot gas flow is divided into two parts which flows towards each respective end of the heat exchanger.
  • the gas will here be cooled down and is now passed back through the spacing between the jacket 90 and the inside of the pressure mantle 78 to the central outlet 84.
  • the jacket 90 is fixed at the centre and it can therefore expand and contract freely towards both ends.
  • the gasv is passed to heat exchanger B between the pressure mantle 80 and the jacket 92.
  • the gas stream is again divided into two parts which are passed towards each respective end, whereafter the streams will pass back through the jacket 92 through the tube bank and are finally gathered together into one stream at the outlet of the second heat exchanger.
  • jackets 90 and 92 which guide the gas flow in this fashion, one avoids the necessity of utilizing two external connecting pipes, one in each end, between the respective heat exchangers and one avoids therefore the problems in this connection due to the different expansion in the material. Furthermore is obtained the advantage that the gas temperature is substantially equal between the mantle and the jacket in both heat exchangers and thereby is eliminated also the expansion difference at the steam pipe 95. Furthermore the gas will be cooled prior to it reaching the pressure mantle 80 such that one can utilize normal ferritic steel material in the mantle. Without the jacket 90 one had to, in the present example, utilize a very expensive high-percentage nickel/chrome alloy (for instance lncoloy 825) due to the hazard of stress corrosion.
  • a very expensive high-percentage nickel/chrome alloy for instance lncoloy 825
  • a tube bank heat exchanger for the heat treatment of gas comprising:
  • a heat exchanger mantle having first and second access openings therein, both of said access openings opening into said mantle at the same crosssectional plane at the midpoint of said mantle;
  • a tube bank positioned within said mantle and extending from one end to the other thereof;
  • means positioned coaxially within said mantle for providing two separate, divided unobstructed gas flow streams through said mantle, of said gas being treated;
  • said means for providing comprising a single internally open jacket positioned coaxially within said matle, said jacket surrounding said tube bank substantially from one end thereof to the other, the outer surface of said jacekt being spaced from the inner surface of said mantle, thus forming a chamber therebetween, the opposite ends of said jacket being completely open, the inner surface of said jacket being continuous and unobstructed from one of said opposite open ends thereof to the other; and
  • said jacket being operative to divide gas from one of said access openings into two equal gas streams which flow unobstructedly in opposite directions and which at said opposite open ends of said jacket are turned around to flow unobstructedly and unite at the other of said access openings.
  • a heat exchanger unit comprising a plurality of heat exchangers as recited in claim 1, wherein said plurality of heat exchangers are coupled in series, the communication between said plurality of heat exchangers taking place via the access opening thereof which communicate with said chambers between said jackets and mantles thereof, such that the gas flows into a first heat exchanger and out of a second heat exchanger via said access openings thereof which communicate directly with the interiors of said jackets.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Manufacture And Refinement Of Metals (AREA)
US00051414A 1969-07-04 1970-07-01 Tube bank heat exchanger and unit of such heat exchangers Expired - Lifetime US3749160A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NO2817/69A NO125206B (ko) 1969-07-04 1969-07-04

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US3749160A true US3749160A (en) 1973-07-31

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US00051414A Expired - Lifetime US3749160A (en) 1969-07-04 1970-07-01 Tube bank heat exchanger and unit of such heat exchangers

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US (1) US3749160A (ko)
CH (1) CH519693A (ko)
DE (1) DE2033128C3 (ko)
GB (1) GB1320788A (ko)
NL (1) NL7009885A (ko)
NO (1) NO125206B (ko)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4010797A (en) * 1974-03-04 1977-03-08 C F Braun & Co Heat exchanger
US4029055A (en) * 1974-10-11 1977-06-14 Dr. C. Otto & Comp. G.M.B.H. Boiler apparatus
US4252186A (en) * 1979-09-19 1981-02-24 Borg-Warner Corporation Condenser with improved heat transfer
US4299276A (en) * 1980-04-21 1981-11-10 Phillips Petroleum Company Heat exchanger having radial support
US4382467A (en) * 1978-08-17 1983-05-10 American Precision Industries Inc. Heat exchanger of the tube and plate type
US4513814A (en) * 1981-10-27 1985-04-30 Langbein & Engelbracht Gmbh & Co. Kg Glass pipe heat exchanger
US4694897A (en) * 1985-08-19 1987-09-22 L. & C. Steinmuller Gmbh Heat exchanger for heat exchange between hot gas and medium flowing through tube bundles
US4694896A (en) * 1985-11-05 1987-09-22 Frank Navratil Heat exchanger
US5390730A (en) * 1993-05-27 1995-02-21 Sterling, Inc. Fluid cooling system
US5509466A (en) * 1994-11-10 1996-04-23 York International Corporation Condenser with drainage member for reducing the volume of liquid in the reservoir
EP0752569A3 (de) * 1995-07-01 1997-11-26 BDAG Balcke-Dürr Aktiengesellschaft Wärmetauscher
US5771963A (en) * 1995-12-05 1998-06-30 Asea Brown Boveri Ag Convective countercurrent heat exchanger
WO1999050609A1 (en) * 1998-03-30 1999-10-07 Kfx Inc. Stackable heat exchanger for processing carbonaceous material
US20100243228A1 (en) * 2009-03-31 2010-09-30 Price Richard J Method and Apparatus to Effect Heat Transfer
US20100282451A1 (en) * 2009-05-06 2010-11-11 Singh Krishna P Heat exchanger apparatus
RU2451887C1 (ru) * 2010-11-12 2012-05-27 Марина Викторовна Мирзоян Кожухотрубный теплообменник
EP3406999A1 (en) 2017-05-26 2018-11-28 ALFA LAVAL OLMI S.p.A. Shell-and-tube heat exchanger
US11536447B2 (en) 2017-05-26 2022-12-27 Alfa Laval Olmi S.P.A. Vapour and liquid drum for a shell-and-tube heat exchanger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19501400C1 (de) * 1995-01-19 1996-06-05 Bresch Entsorgung Gmbh Vorrichtung zur Kühlung gasförmiger Medien und Verfahren unter Verwendung der Vorrichtung
DE59705073D1 (de) 1997-03-14 2001-11-29 Borsig Babcock Ag Wärmetauscher mit U-Rohren

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4010797A (en) * 1974-03-04 1977-03-08 C F Braun & Co Heat exchanger
US4029055A (en) * 1974-10-11 1977-06-14 Dr. C. Otto & Comp. G.M.B.H. Boiler apparatus
US4382467A (en) * 1978-08-17 1983-05-10 American Precision Industries Inc. Heat exchanger of the tube and plate type
US4252186A (en) * 1979-09-19 1981-02-24 Borg-Warner Corporation Condenser with improved heat transfer
FR2465979A1 (fr) * 1979-09-19 1981-03-27 Borg Warner Condenseur a caracteristiques de transfert de chaleur
US4299276A (en) * 1980-04-21 1981-11-10 Phillips Petroleum Company Heat exchanger having radial support
US4513814A (en) * 1981-10-27 1985-04-30 Langbein & Engelbracht Gmbh & Co. Kg Glass pipe heat exchanger
US4694897A (en) * 1985-08-19 1987-09-22 L. & C. Steinmuller Gmbh Heat exchanger for heat exchange between hot gas and medium flowing through tube bundles
US4694896A (en) * 1985-11-05 1987-09-22 Frank Navratil Heat exchanger
US5390730A (en) * 1993-05-27 1995-02-21 Sterling, Inc. Fluid cooling system
US5509466A (en) * 1994-11-10 1996-04-23 York International Corporation Condenser with drainage member for reducing the volume of liquid in the reservoir
AU688107B2 (en) * 1994-11-10 1998-03-05 York International Corporation Condenser with drainage member for reducing the volume of liquid in the reservoir
EP0752569A3 (de) * 1995-07-01 1997-11-26 BDAG Balcke-Dürr Aktiengesellschaft Wärmetauscher
US5771963A (en) * 1995-12-05 1998-06-30 Asea Brown Boveri Ag Convective countercurrent heat exchanger
WO1999050609A1 (en) * 1998-03-30 1999-10-07 Kfx Inc. Stackable heat exchanger for processing carbonaceous material
US20100243228A1 (en) * 2009-03-31 2010-09-30 Price Richard J Method and Apparatus to Effect Heat Transfer
US20100282451A1 (en) * 2009-05-06 2010-11-11 Singh Krishna P Heat exchanger apparatus
RU2451887C1 (ru) * 2010-11-12 2012-05-27 Марина Викторовна Мирзоян Кожухотрубный теплообменник
EP3406999A1 (en) 2017-05-26 2018-11-28 ALFA LAVAL OLMI S.p.A. Shell-and-tube heat exchanger
WO2018215160A1 (en) 2017-05-26 2018-11-29 Alfa Laval Olmi S.P.A Shell-and-tube heat exchanger
US11054196B2 (en) 2017-05-26 2021-07-06 Alfa Laval Olmi S.P.A. Shell-and-tube heat exchanger
US11536447B2 (en) 2017-05-26 2022-12-27 Alfa Laval Olmi S.P.A. Vapour and liquid drum for a shell-and-tube heat exchanger

Also Published As

Publication number Publication date
DE2033128A1 (ko) 1971-02-04
DE2033128C3 (de) 1979-10-18
GB1320788A (en) 1973-06-20
DE2033128B2 (de) 1979-03-01
NO125206B (ko) 1972-07-31
NL7009885A (ko) 1971-01-06
CH519693A (fr) 1972-02-29

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