WO2007012171A1 - Improved heat exchanger - Google Patents
Improved heat exchanger Download PDFInfo
- Publication number
- WO2007012171A1 WO2007012171A1 PCT/CA2005/001592 CA2005001592W WO2007012171A1 WO 2007012171 A1 WO2007012171 A1 WO 2007012171A1 CA 2005001592 W CA2005001592 W CA 2005001592W WO 2007012171 A1 WO2007012171 A1 WO 2007012171A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tubes
- ring
- arc
- heat exchanger
- adjacent
- Prior art date
Links
Classifications
-
- 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
- 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
-
- 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
- F28F2009/226—Transversal partitions
Definitions
- This invention relates to shell and tube heat exchangers for exchanging heat between a gas and another fluid, particularly of use in the manufacture of sulfuric acid. It is of further particular value in the manufacture of large heat exchangers which may be assembled in-situ. on site from a plurality of segments, and to each of the segments per se.
- Shell and tube heat exchangers are used extensively in the manufacture of sulfuric acid to exchange heat between a hot fluid and a colder fluid, such as a hot sulfur trioxide or sulfur dioxide-containing gas or sulfuric acid and cold air or a colder sulfur-dioxide containing gas.
- a gas generally sulfur dioxide/ trioxide-containing gas or air is fed to a vestibule within a lower part of the shell and, subsequently, passed through the shell space containing the tube bundle and suitably arranged baffles to effect radial flow of the gas across the tube bundle, prior to exit.
- a gas generally sulfur dioxide/ trioxide-containing gas or air is fed to a vestibule within a lower part of the shell and, subsequently, passed through the shell space containing the tube bundle and suitably arranged baffles to effect radial flow of the gas across the tube bundle, prior to exit.
- Such heat exchangers like other prior art heat exchangers, while being successful in commercial use over a long period of time, suffer from the disadvantage of being 1 limited in size, particularly in diameter, since transportation from the engineering manufacturing facility to the in-situ site of operation is severely restricted by road width, weight, geography and other physical limitations.
- Aforesaid USP 4,357,991 describes a heat exchanger having a tube layout which produces more constant mass flow velocities in the area near the tubes and in which the heat transfer coefficient and pressure drop are more favorable than in other prior art exchanger arrangements.
- the heat exchanger has a plurality of tubes of circular cross-section, the tubes all having the same outer diameter and laid out according to a specific relationship wherein the tubes are arranged with their centers located on a plurality of concentric circular arcs, a plurality of tubes on each arc; the number of tubes in each arc differs from the number of tubes in each other arc by not more than one; the tubes in each arc are spaced uniformly apart along such arc; each tube in each arc, other than such end tubes as may be present in some of said arcs, is located circumferentially midway between the two adjacent tubes of each neighboring arc so that the centers of such three tubes form an isosceles triangle, each such tube in each arc being separated from each of the adjacent tubes in each adjacent
- the invention provides a heat exchanger for exchanging heat between fluids and having a heat exchanger shell and a plurality of parallel tubes of circular cross-section, said tubes all having the same outer diameter, the improvement wherein said tubes are laid out according to the following relationship: (i) said tubes are arranged with their centers located on a set of concentric circular arcs, said set comprising at least first, second and third such arcs, a plurality of tubes on each arc,
- each tube in each arc is spaced uniformly apart along such arc
- each tube in each arc, other than such end tubes as may be present in some of said arcs is located circumferentially midway between the two adjacent tubes of each neighboring arc so that the centers of each such three tubes form an isosceles triangle, each tube in each arc being separated from each of said adjacent tubes in each adjacent arc by a diagonal ligament distance h, said distance h being constant for all said tubes, and
- each two adjacent tubes in any said arc is at least as great as twice said diagonal ligament distance h, so that the minimum cross-sectional area for radial fluid flow between adjacent arcs of said set is defined as to its circumferential dimension by the sum of said diagonal ligament distances h between the tubes of said adjacent arcs and is substantially constant independent of the radial position of said arcs, the improvement wherein said exchanger further comprises a plurality of an adjacent pair of longitudinal baffle plates located symmetrically and intermittently between transverse disc and donut baffles and extending the length of said plurality of tubes.
- each of the arcs extends through 360° so that each arc is a closed circular ring without end tubes, each ring having the same number of tubes as each other ring and is coaxial with said heat exchanger shell.
- each said arc extends through 360° so that each arc is a closed circular ring without end tubes, each ring having the same number of tubes as each other ring and is non-coaxial with said heat exchanger shell.
- each said arc comprises a plurality of arc segments, each segment extending through 360° divided by said plurality, such that each arc is a part of a closed
- each non-adjacent arc has the same number of tubes, and adjacent arcs have a number of tubes differing by not more then one, and each arc is off-centered with said heat exchanger shell.
- the radius of one of the rings is R n and the radius of the next ring radially within the ring is R n+ i and the radii are related by the relationship Rn+1 + b n — R n .
- Ntr is the number of tubes per ring
- D 0 is the outer diameter of said tubes.
- the tubes are arranged subject to the restriction that R n -R n+ 2 > D o + h so that for the outermost ring R n ,
- the heat exchanger includes a wall defining a shell extending parallel to and encircling said tubes, and first and second baffles each extending " at right angles to said wall and intersecting at least some of said tubes, said first baffle extending to said wall and having an inner opening within the innermost of said rings, and hence being of donut configuration, said second baffle being of disc shape and extending from the centre of said innermost ring outwardly past said tubes and having an annular gap between its periphery and said wall, said first and second baffles alternating with each other to form a disc and donut baffle configuration.
- each of the baffles intersects all of the tubes.
- a heat exchanger includes two sets of said rings, each set containing a plurality of rings, the number of tubes in each ring of one set being different from the number of tubes in each ring of the other set.
- the heat exchanger has said diagonal ligament distance h in said one set is different from said diagonal ligament distance in said other set.
- the number of tubes in each ring of said one set multiplied by said diagonal ligament distance of said one set is equal to the number of tubes in each ring of said other set multiplied by said diagonal ligament distance of said other set, so that said minimum cross-sectional area for said one set is equal to said minimum cross-sectional area for said other set.
- the heat exchanger includes two sets of said arcs, each said set containing a plurality of arcs, the number of tubes in each arc of one set being different from the number of tubes in each arc of the other set.
- said diagonal ligament distance h in said one set is different from said diagonal ligament size distance in said other set.
- a heat exchanger as hereinabove defined comprises an odd integer selected from 3 to 15 of said plurality of said longitudinal baffle plates. More preferably, an integer selected from 5, 7 and 9.
- the plurality of tubes extend between tube sheet end plates; and said plurality of longitudinal baffle plates extend between said tube sheet end plates.
- a heat exchanger as hereinabove defined has a diameter selected from 3m to 8m, and more preferably a diameter selected from 4m and 5m.
- the invention provides a method of manufacturing a heat exchanger having the tube layout as hereinabove defined which method comprises (A) providing a plurality of exchanger segments, wherein each of said segments
- said tubes are arranged with their centers located on a set of concentric circular arcs, said set comprising at least first, second and third such arcs, a plurality of tubes on each arc,
- each tube in each arc is spaced uniformly apart along such arc
- each tube in each arc, other than such end tubes as may be present in some of said arcs is located circumferentially midway between the two adjacent tubes of each neighboring arc so that the centers of each such three tubes form an isosceles triangle, each tube in each arc being separated from each of said adjacent tubes in each adjacent arc by a diagonal ligament distance h, said distance h being constant for all said tubes, and
- the segment of an annulus as termed herein may be also considered to be a double arc sector of a right circular cylinder.
- the requisite number of segments is an odd number selected from 3 to 15, more preferably, 5, 7 or 9.
- each of the double arc sectors is as hereinabove defined. Accordingly, in a further aspect the invention provides a heat exchanger segment as hereinabove defined of use in the method as hereinabove defined.
- the segment has longitudinal baffle plates which subtend an angle therebetween, selected from the group consisting of about 120°; 72°; 51.5°; 40°; 33°; 28° and 24°.
- the invention provides a plant for the manufacture of sulfuric acid by the oxidation of sulfur dioxide to sulfur trioxide in a catalytic converter and subsequent absorption of the sulfur trioxide in sulfuric acid, the plant comprising an absorption tower, a heat exchanger and a catalytic converter, the improvement comprising a heat exchanger as hereinabove defined.
- FIG. 1 is a diagrammatic view of a typical prior art heat exchanger, illustrating a disc and donut baffle configuration
- FIG. 2 is a view of a portion of a tubesheet of a prior art heat exchanger showing the layout of the tubes
- FIG. 3 is a view of a more complete portion of a tubesheet showing the layout of tubes therein according to the prior art
- FIG. 4 is a view showing the layout of five tubes according to the prior art and illustrating the mathematical design by which the tubes are laid out;
- FIG. 5 is a view showing the layout of six tubes according to the prior art for calculation of certain limits
- FIG. 6 is a view showing a heat exchanger according to the prior art and having the form of a section of an annulus
- FIG. 7 is a diagrammatic isometric view of a heat exchanger segment, according to the invention.
- FIG. 8 is an end view of a tube array in a heat exchanger according to the invention.
- FIG. 9 is a diagrammatic, partly-exploded, isometric view of a plurality of segments of Fig. 7 suitably arranged according to the invention.
- FIG. 10 is a radical sectional view along the line 10-10' of Fig. 9;
- FIG. 11 is a diagrammatic end view of the tube array showing the arc layouts of use in the heat exchanger and segments according to the invention; and wherein the same numerals denote like parts.
- FIG. 1 shows diagrammatically a typical cylindrical heat exchanger 2.
- the heat exchanger 2 has a cylindrical shell 4 having an inlet conduit 6 and an outlet conduit 8 for fluid which is to be heated or cooled.
- Located within the shell 4 are a number of annular or donut shaped baffles 10 which extend to and are adjacent to the wall of the shell 4 and which have central apertures 12.
- Located between each pair of donut baffles 10 is a disc-shaped baffle 14, of smaller diameter than that of the shell 4 and therefore leaving an annular gap 16 extending there around.
- Both sets of baffles 10, 14 are intersected by all the tubes 18 of the heat exchanger.
- the tubes 18 extend parallel to the shell 4 and at right angles to the baffles 10, 14.
- Heating or cooling fluid (liquid or gas) from a source not shown, is directed into the tubes 18 of the heat exchanger from outside one tube sheet 20 and leaves the tubes 18 at the outside of the other tube sheet 22.
- Fluid (liquid or gas) from the conduit 6 passes through the heat exchanger in the path indicated by arrows 24 and is warmed or cooled by the fluid in the tubes 18.
- the central aperture 12 and the annular gap 16 are made sufficiently large that the baffles 10, 14 intersect only some of the tubes 18.
- FIG. 2 shows a set of tubes 18 according to the prior art shown as being located in rings identified by their radii, namely rings R 1 , R 2 , R 3 , R 4 and R 5 .
- the design parameters used to lay out the tubes 18 include the following. Firstly, the diagonal distance between each tube in any ring and its adjacent tubes in the neighboring ring is a constant distance h (referred to as the ligament size or ligament width). Secondly, the shortest distance between two adjacent tubes in the same ring (such distances are identified by reference characters d ⁇ , d 2 , etc.) is a constant in each ring but varies from ring to ring and is always greater than or equal to 2h. Thirdly the number of tubes in each ring is always the same.
- the radial distance between rings is varied so that the ligament size h between a tube in one ring and its adjacent tubes in each neighboring ring is as mentioned always the same.
- a mathematical design procedure for calculating the various radii will be set forth shortly. It will be seen from FIG. 2 that so long as the ligament gaps h adjacent to a tube 18 are no more than half as large as the gaps dj, d 2 , etc., the ligament gaps and not the gaps d ls d 2 , etc. will determine the maximum fluid velocity near that tube. This is the opposite of the conventional concentric ring arrangement in which the tube count is varied for constant distance between the tubes of a ring. It will also be seen from FIG.
- FIG. 3 illustrates portions of two sets of circular rings, indicated at 26 and 28.
- the ligament size hi between each tube 18 and its adjacent tubes 18 in each neighboring ring is always the same constant distance, and the number of tubes 18 in each ring Ri to R 7 is the same.
- the ligament size h 2 between each tube 18 and its adjacent tubes in each neighboring ring is also a constant, but ligament size distance h 2 is greater than ligament size hi.
- the number of tubes in each ring R 8 to Ri i is constant, but this number is less than the number of tubes in each ring Ri to R 7 .
- controlling flow distance or AFC between the tubes of any two adjacent rings of set 26 is the same as the controlling flow distance or AFC between the tubes of any two adjacent rings of set 28.
- distance hi multiplied by the number of tubes in any ring of set 26 is equal to distance h 2 multiplied by the number of tubes in any ring of set 28. Therefore fluid flowing through tube sets 26, 28 will always be subject to the same controlling AFC and the flow velocities through both sets of rings 26, 28 will be nearly constant.
- the AFC between the adjacent rings of sets 26, 28 will of course normally be greater than the AFC of each of the two sets.
- h is the diagonal distance between each tube and the adjacent tubes in each neighboring ring, or in other words is the ligament width
- n is the ring number
- Ri, R 2 , R 3 - R n are the ring radii
- ⁇ is the angle between radii directed through the centers of adjacent tubes in a ring
- a n is a chord of the circle having radius R n extending between the centers of two adjacent tubes on the circle of radius R n ,
- D 0 is the outer diameter of each tube, assumed to be the same for all tubes
- N tr is the number of tubes per ring, assumed to be the same for all rings in each set of rings
- P is the pitch, i.e. the distance between the centers of adjacent tubes in adjacent rings, and is to be constant.
- the radius R n +i is related to radius R n by
- the design may be started by selecting the required area for flow, i.e. the AFC, which is 2h.N tr . If a ligament width h is chosen, this determines the number of tubes for the first ring of radius Ri, which is laid out adjacent the shell 4 of the heat, exchanger.
- Equation (6) gives the minimum ring radius which may be used in order to satisfy equation
- Equation (6) The derivation of equation (6) is as follows with reference to FIG. 5. Assuming that a n > D 0 +2h
- the chord distance between two adjacent tubes in the same ring will be less than twice the ligament width, so that the minimum flow area will no longer be governed by the ligaments, which is undesirable. It will however be appreciated that when a number of rings of tubes are to be packed into a heat exchanger, and if space considerations so demand, one or more of the inner rings can be more tightly packed, so that the chord distance between two adjacent tubes in ring is in fact less than 2h. This of course has the disadvantage that the flow through these rings will not behave as ideally as the flow through the rings laid out as described. Such rings, where the chord distance is less than 2h, would not be considered as being members of the set of rings laid out according to the invention.
- an outer ring or rings can be provided near the shell with tube spacing other than those described, to provide higher or lower heat transfer near the shell wall.
- the second limit for tubes laid out as described is as follows. It is normally necessary to ensure that the radial distance between any two rings which are separated by one ring is
- Equation (7) represents a normal limit on how closely the rings can be spaced without unduly weakening the tube sheets 20, 22 and the baffles 10, 14. In some special cases it may be possible to achieve slightly closer spacing.
- the AFC of each set is as discussed normally held the same as that of the other set. If ring n is the last ring in one set and ring n-1 is the first ring in the second set, this is accomplished by maintaining where P n is the pitch for ring n and P n-I is the pitch for ring n-1. This ensures that the mass flow velocity is nearly constant throughout the tube bundle. If in special cases it is desired to have a different AFC in each set of tube rings, for example more rapid flow through the outer set than through the inner set, then the AFC can be made larger in the outer set than the inner set.
- each tube 18 is laid so that each tube is located circumferentially midway between the two adjacent tubes in each neighboring arc, so that the centers of such three tubes form an isosceles triangle.
- FIG. 3 When two sets of rings are used, as shown in FIG. 3, then since each set of tubes has a different spiral configuration, it is necessary to clean the outer set of rings by a tool inserted from the outside, and the inner set of rings by a tool inserted from the inside.
- each ring Rl to R7 contains 68 tubes (total 476), and the radii are
- Rl 35.90 inches
- R5 30.84 inches
- R2 34.745 inches
- R6 29.40 inches
- each ring R8 to Rl 1 contains 43 tubes, and the radii are
- the tube outer diameter remains 1.5 inches and the pitch is 2.29 inches.
- the values given for FIG. 3 are exemplary only and will of course vary depending on the application. In FIG. 3 it is assumed that each set of rings 26, 28 extends through a full circle of
- each ring Rl to RIl is a closed circle.
- the sets of rings 26, 28 may be arranged not as closed rings but as sections of annuli.
- This arrangement is shown in FIG. 6, where the heat exchanger 2 is shown in section as a section of an annulus and the tubes 18 are arranged along concentric arcs where the arcs do not extend through a full 360 degrees.
- the FIG. 6 arrangement of tubes is in fact simply a portion of the FIG. 3 set 26, and the same radii Rl to R7 are shown in the drawings.
- the shell of the heat exchanger is shown at 40.
- all of the relationships previously described remain applicable, except that the arcs may not all have the same number of tubes 18.
- FIG. 6 all of the relationships previously described remain applicable, except that the arcs may not all have the same number of tubes 18.
- each arc would have the same number of tubes (nine tubes in the FIG. 6 embodiment).
- the number of tubes in each arc will be either the same as the number in each other arc or may differ from the number of tubes in each other arc by not more than one.
- end tubes in the odd numbered arcs do not of course form an isosceles triangle with the two adjacent tubes of each neighboring arc, because of the end walls 42, 44, but these walls are sufficiently close to the end tubes of the odd numbered arcs to prevent "punch-through".
- this shows generally as 50 a diagrammatic isometric view of a segment, in the form of part of an annulus for use in the construction of a heat exchanger to comprise seven such segments.
- the segment has a radial tube layout of tubes 52 between tube sheet end plates 54 and a pair of longitudinal baffle plates 56, 58 (with only 56 being seen), extending the length between end plates 54. Radial edges 60, 62 of each of end plates 54 subtend on angle ⁇ of about 51.4° in the embodiment shown. In field assembly, the longitudinal baffle plate 56A adjacent to end plate 54 is not present.
- a pair of segments 50 is positioned longitudinally adjacent one to the other with a radial edge 60 abutting radial edge 62 of adjacent segment 50.
- FIG. 8 shows generally as 60, a end view of a heat exchanger having a plurality of segment tube arrays 50 welded together and having a pair of adjacent longitudinal baffle plates 56 between adjacent arrays according to the invention.
- FIG. 9 shows generally as 70 a plurality of seven segments 60 in the process of construction of the complete tube 52 layout with longitudinal baffle plates 56, 58 and end plates 54.
- FIG. 10 shows the resultant connection between two adjacent segments 50, welded in situ in the field to provide a "double plate” arrangement of a pair of parallel plates intermittently welded, one to the other, at at least one end thereof.
- the plates are so spaced apart as to provide a gap "g" between a plate 56, 56A, 58, 58A and its adjacent row of tubes, as to allow gas flow between each of the tubes and the plates, while preventing gas bypass between the adjacent row of tubes of adjacent bundles.
- FIG. 11 shows generally in end view 80, the angles ⁇ for both the segments and the offset arcs.
- Dimension "f” is the offset distance between the center of shell 82 and the center of the "petal” arcs 84.
- Dimension "m” denotes a maximum deviation between centered arc 86 and petal arc 84. This figure also shows adjacent arcs 88 and non-adjacent arcs 90.
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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
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI0506668A BRPI0506668A8 (en) | 2005-07-27 | 2005-10-14 | HEAT EXCHANGER, SULFURIC ACID MANUFACTURING PLANT, METHOD OF MANUFACTURING A HEAT EXCHANGER, AND, HEAT EXCHANGER SEGMENT |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2,513,989 | 2005-07-27 | ||
CA002513989A CA2513989C (en) | 2005-07-27 | 2005-07-27 | Improved heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007012171A1 true WO2007012171A1 (en) | 2007-02-01 |
Family
ID=36577239
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CA2005/001592 WO2007012171A1 (en) | 2005-07-27 | 2005-10-14 | Improved heat exchanger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20070023173A1 (en) |
AU (1) | AU2005256114B2 (en) |
BR (1) | BRPI0506668A8 (en) |
CA (1) | CA2513989C (en) |
WO (1) | WO2007012171A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007060291B4 (en) * | 2007-12-12 | 2011-04-28 | Sartorius Stedim Biotech Gmbh | Container arrangement with a container with flexible wall |
JP2009222360A (en) * | 2008-03-18 | 2009-10-01 | Daikin Ind Ltd | Heat exchanger |
EP2246109A1 (en) | 2009-04-29 | 2010-11-03 | Methanol Casale S.A. | Isothermal tube reactor |
DE102014201908A1 (en) * | 2014-02-03 | 2015-08-06 | Duerr Cyplan Ltd. | Method for guiding a fluid flow, flow apparatus and its use |
DE102015102312A1 (en) * | 2015-02-18 | 2016-08-18 | HUGO PETERSEN GmbH | Tube bundle heat exchanger with sequentially arranged tube bundle components |
CN109312987B (en) * | 2016-01-22 | 2021-10-15 | 杭州富尔顿热能设备有限公司 | Heat exchanger tube assembly, heat exchanger and fluid heating system |
SE544878C2 (en) * | 2021-01-20 | 2022-12-20 | Marinnovation Hb | Tube heat exchanger |
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US1790828A (en) * | 1931-02-03 | Heating apparatus | ||
US4357991A (en) * | 1979-11-23 | 1982-11-09 | C-I-L Inc. | Heat exchanger having improved tube layout |
US5291944A (en) * | 1993-11-25 | 1994-03-08 | Delio Sanz | Heat exchanger |
Family Cites Families (14)
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US1672650A (en) * | 1927-07-27 | 1928-06-05 | Foster Wheeler Corp | Heat exchanger |
US2676651A (en) * | 1944-05-25 | 1954-04-27 | Lavigne Jean Loumiet Et | Evaporating apparatus |
US2655346A (en) * | 1949-07-25 | 1953-10-13 | Rolls Royce | Heat exchanger with tube matrix |
US2729433A (en) * | 1952-01-07 | 1956-01-03 | Smith Corp A O | Heat exchanger with removable tube banks |
US2729432A (en) * | 1952-09-17 | 1956-01-03 | Smith Corp A O | Large capacity heat exchanger |
GB968598A (en) * | 1961-03-10 | 1964-09-02 | Parsons C A & Co Ltd | Improvements in and relating to feed heaters for steam turbine plant |
GB1101773A (en) * | 1964-05-25 | 1968-01-31 | Babcock & Wilcox Ltd | Improvements in or relating to heat exchangers |
GB1280662A (en) * | 1969-01-28 | 1972-07-05 | Atomic Energy Authority Uk | Improvements in or relating to tubular heat exchangers |
US3827484A (en) * | 1970-02-04 | 1974-08-06 | W Wolowodiuk | Liquid metal heat exchanger |
US3955620A (en) * | 1974-04-26 | 1976-05-11 | Artemov Lev N | Heat exchanger |
FR2293684A2 (en) * | 1974-12-05 | 1976-07-02 | Trepaud Georges | TUBULAR BEAM HEAT EXCHANGER |
CH629586A5 (en) * | 1977-09-14 | 1982-04-30 | Sulzer Ag | HEAT EXCHANGER. |
CA1323363C (en) * | 1989-08-24 | 1993-10-19 | Gordon M. Cameron | Tube layout for heat exchanger |
US6167951B1 (en) * | 1999-01-26 | 2001-01-02 | Harold Thompson Couch | Heat exchanger and method of purifying and detoxifying water |
-
2005
- 2005-07-27 CA CA002513989A patent/CA2513989C/en active Active
- 2005-10-14 BR BRPI0506668A patent/BRPI0506668A8/en not_active Application Discontinuation
- 2005-10-14 WO PCT/CA2005/001592 patent/WO2007012171A1/en active Application Filing
- 2005-10-14 AU AU2005256114A patent/AU2005256114B2/en not_active Ceased
-
2006
- 2006-01-10 US US11/328,146 patent/US20070023173A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1790828A (en) * | 1931-02-03 | Heating apparatus | ||
US4357991A (en) * | 1979-11-23 | 1982-11-09 | C-I-L Inc. | Heat exchanger having improved tube layout |
US5291944A (en) * | 1993-11-25 | 1994-03-08 | Delio Sanz | Heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
AU2005256114A1 (en) | 2007-02-15 |
AU2005256114B8 (en) | 2007-02-15 |
AU2005256114B2 (en) | 2008-01-03 |
US20070023173A1 (en) | 2007-02-01 |
CA2513989A1 (en) | 2006-06-06 |
BRPI0506668A (en) | 2007-06-12 |
CA2513989C (en) | 2007-02-06 |
BRPI0506668A8 (en) | 2016-04-26 |
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