US3117559A - Heat exchanger - Google Patents

Description

Jan. 14, 1964 1 .Fouc1-1 3,117,559 HEAT EXCHANGER Fil'ed Sept. 20, 1961 2 Sheets-Sheet 1 FOUCHE HEAT *EXCHANGER I Jan. 14, 1964 2 Sheets-Sheet 2 Filed Sept 20, 1961 i I I 9 i u United States Patent 01 3,117,559 I-EAT EXQHANGER Lucien l ouch, Sevres, Seine-et-Gise, France, assignor to Fives-Penhet, Paris, France, a corporation of France Filed Sept. 29, E61, Ser. No. 139,555 Claims priority, application France Sept. 21, 1960 9 Claims. Ii. 122-32) The present invention has for its principal object a method of laying-out two-fluid heat exchanger elements, and a heat exchanger device for performing said method.

The principle of heat transfer using jets is well known. The method according to the invention is of the type wherein one of the two fluids, termed the primary fluid, is directed towards the peripheral surface of a tubular wall which separates it from the other fluid, termed the secondary fluid, in the form of multiple continuous jets distributed in the form of cylindrical clusters, said jets being produced for example by passage of said primary fluid through orifices or nozzles, and notably through holes in a perforated wall forming a cylindrical enclosure round the heat exchanger surface.

This method is notably remarkable in that it consists in disposing, in the interior of a common enclosure formed by an external cylindrical envelope, firstly, a certain number of tubular conduits which are distributed in one or more spaced coaxial and cylindrical clusters and through which the secondary fluid is caused to circulate, preferably in the direction opposite to that in which the primary fluid flows and, secondly, primary fluid jet producers distributed in the form of a preferably even number of spaced coaxial and cylindrical clusters, said jet clusters being concentric with the tube clusters and arranged so that each cluster of tubes is placed between two successive clusters of jets, the jets being projected radially towards said tubes.

According to another characteristic of the invention, said coaxial jet clusters are arranged in one or more successive tiers in extension of each other.

According to a further characteristic of the invention, said tube clusters consist of straight tubes arranged paral lel to the axis of the apparatus.

in accordance with yet another characteristic of the invention, one end of each annular space bounded by the jet clusters is tightly obturated in such a way that the obturated ends of successive annular spaces alternate in opposition to each other' According to another characterr do of the invention, the primary fluid jet producers are uniformly distributed along the generating lines and the parallels of said coaxial jet clusters, the jet producers of any given cluster being disposed symmetrically in relation to the common axis.

The invention also has for its object a heat exchanger device for performing the aforementioned method. The device according to the invention is of the tubular heat exchanger type with jets. This device is notably remarkable in that it comprises, inside its casing, firstly, a number of tubes which convey the secondary fluid and are arranged in one or more spaced coaxial cylindrical clusters and secondly, a certain number of perforated coaxial cylindrical ferrules or the like, preferably bodies of revolution. These ferrules, of which there is preferably an even number, are arranged in one or more successive tiers in extension of one another and they define between themselves and the outer casing, annular spaces or intervals through which pass the prhnary fluid and said secondary fluid tubes.

In accordance with a further characteristic of the invention, said tube clusters consist of straight tubes arranged parallel to the axis of the apparatus.

3,1175% Patented Jan. 14, 1984 According to another characteristic of the invention, the annular space formed between each distinct pair of successive coaxial ferrules, or successive cylindrical clusters of tiered ferrules, comprises a cluster of said tubes which-is coaxial with the apparatus and preferably extends through all the aforementioned coaxial tiers of ferrules.

In accordance with yet another characteristic of the invention, each of said ferrules comprises orifices producing jets of primary fluid, and these orifices are uniformly distributed along generating lines and parallels that are symmetrical in relation to the common axis.

According to still another characteristic of the invention, the two ferrules of each distinct pair of concentric successive ferrules comprise orifices located in common meridian planes and parallel planes.

An embodiment of a heat exchanger according to the invention will be described hereinafter solely by way of example, and it is illustrated somewhat schematically in the accompanying drawings.

In these drawings,

FIGURE 1 is a partly sectional schematic illustration of an embodiment of a heat exchanger according to the invention;

FIGURE 2 is a section taken along the line HII in FIGURE 1;

FIGURE 3 is a schematic longitudinal section view of a heat-exchanger; and

FIGURE 4 is an alternative embodiment of the exchanger, in an illustration similar to FIGURE 1.

In the embodiment shown in FIGURE 1, which shows an exchanger of the vertical type, the reference numeral 1 designates the outer casing or shell of the exchanger. This casing consists of a preferably cylindrical barrel-plate 2 closed at both ends by plates 3 and 4 the shapes of which will be dictated by considerations of pressure, by the size of the apertures they must accommodate, and by the nature of the component parts that may have to be contained within the exchanger. A cylindrical shape is in most cases the optimum one, however, as it is well suited to withstand pressure variations and is economical to manufacture. The arrangement in accordance with the invention is designed to make best use of the space offered by the cylindrical barrel-plate 2 forming the side of the heat exchanger. The end plates 3, 4 shown in F1- URE 1 are substantially elliptical. The upper plate .3 comprises a primary fluid inlet 5 and secondary fluid discharge tubes 6. The lower plate 4 comprises a pri mary fluid outlet tube 7 and secondary fluid inlet tubes 8.

Although the arrangement illustrated is the preferred one from the standpoints of both convenience of con struction and efliciency of fluid flow, the foregoing tubes 58 may be placed in different ways to suit specific requirements, notably requirements arising from the posi tion of the exchanger in relation to the various fluid-conveying incoming and outgoing pipes. In some cases, for example, certain of the aforementioned tubes may be placed on the cylindrical barrel-plate 2 forming the casing.

Furthermore, the shape of said end plates 3, 4 may likewise vary. As an example, FIGURE 4 shows that an upper plate or head 3' is provided which is spherical to permit accommodation of a flask device 19 which will be described hereinafter.

In addition, discharge of the secondary fluid may be caused to take place inside the primary fluid inlet tube, This arrangement, to be explained in more detail with reference to FIGURE 4, is advantageous when, in rela tion to the direction of flow of the primary fluid, the exchanger under consideration is preceded by another exchanger operating with the sarne two fluids. This obviates the need for secondary fluid exit and re-entry.

Inside the barrel-plate 2 and coaxial therewith are disposed a number of perforated cylindrical ferrules or guide casings 9-11, 9'41" etc. These ferrules may be arranged concentrically and in one or more superimposed tiers, in such a way that homologous ferrules form extensions of iohe another along concentric cylindrical clusters. Thus, FIGURE .1 shows an arrangement of perforated ferrules 9, 9', 9", 9', 9"", 10, 10, 10 etc., 11, 11, 11" etc.

The ferrules designated 9, ill and 11; 9', 10', and 11'; 9", 1%" and 11", etc, respectively, form extensions of one another and may be interconnected if necessary by suitable linking members, in which case the latter must leave large unoccupied feed spaces located at the levels A- -A' and BB', as will be seen hereinafter.

In what follows, the ferrules 9, 9', 9 etc. will conventionally be referred to as the first or top tier of the exchanger, the ferrules 10, 10', 16" etc as the second or intermediate tier, and the ferrules ll, 11, 11" etc. as the third or bottom tier. This number of tiers is by no means limited and depends essentially upon the nature of the duty assigned to the exchanger and also upon its positioning. These cylindrical ferrules thus determine coaxial annular spaces which, for clarity purposes, will be numbered in inward succession, starting from the barrel plat'e 2. Tubes or pipes such as 12, 12', 12" are di posed parallel to the axis of the apparatus, in coaxial cylindrical clusters for conveying the secondary fluid; each cluster of tubes is accommodated in the annular space determined by a pair of successive concentric ferrules or of successive cylindrical clusters of tiered fer- All the ferrules 9-11, 9'-11' etc. are pierced with small holes which are aligned along a certain number of preferably uniformly spaced generating lines. These holes are designed to produce jets of primary fluid directed against the tubes 12 etc. conveying the secondary fluid. The annular spaces of same parity bounded by the ferrules and the barrel-plate 2 all fulfill the same function, to wit the function either of distributing primary fluid to the ferrule holes, or of discharging the primary fluid, which these spaces contain, round the tubes disposed parallel to the exchanger axis.

The ferrule holes are so pierced as to ensure that each tube receives, on two diametrically opposed generating lines, the primary fluid jets distributed by two annular spaces of identical parity, numbered n and n+2, the jets from the ferrule external to the cluster of tubes concerned being directed radially inwards, and those of the inside ferrule outwards. The various tiers of ferrules are similar to each other, but the lengths of the tiers and the diameters, number and longitudinal pitches of the holes may vary from one tier to another. Similarly, the radial spacing between ferrules or tiered clusters .of ferrules, namely the cross-section of the annular spaces for a given type of exchanger, will depend on specific requirements arising from the nature of the duty involved. The distributing annular spaces are closed at their lower or downstream ends (in the direction of flow of the primary fluid), while the annular discharging spaces are closed at their upper or upstream ends (in the same direction).

The description will be more clearly understood if reference is had to FIGURE 3 which shows the second or intermediate tier of ferrules 10, 1t), it)" etc. The two ferrules in each distinct pair of successive concentric ferrules comprise jet-producing holes disposed in common meridian planes and parallel planes. Thus, to each perforation generating line of the ferrule 10, there corresponds a perforation generating line on the ferrule 10', located in the same meridian plane. Between the two ferrules of any pair of successive concentric ferrules, as 10 and 10, 1d" and 10', etc.,. of the same tier and parallel to the exchanger axis run the secondary fluid tubes 12 the axes of which lie in the same meridian planes .as the pe foration generating aines. The tubes 12, 12,

4 etc. each pass, in leakproof manner, through whole or divided plates 13, 13 or the like, which are preferably annular and coaxial with the exchanger and to which the tubes are respectively fixed by welding or by any other leakproof joining method in order to avoid leaking of the primary fluid.

Each of the odd annular spaces, namely those which are devoid of tubes and which distribute the primary fluid to the holes in the foregoing ferrules, is closed at its lower or downstream end by at least one coaxial ring such as 14, 14', 14 which is preferably similar to a cone frustrum, that is to say slightly inclined downwardly towards the lowermost ferrule holes in order to allow drainage of said annular spaces.

Each of the even annular spaces, namely those containing the tubes and designed to discharge the primary fluid, is closed at its upper or upstream end by at least one coaxial ring such as 15, 15, 15" pierced with holes or orifices to provide passage for the secondary fluid tubes 12, 12' etc., the integrally united plates 13, 13' etc. of which are applied against said rings 15, 15 etc. in order to form a joint. The rings furthermore fulfill the function of bracing means for the tubes, the correct position of which in relation to the ferrules is thereby ensured. In the embodiment under consideration, the tubes 12, 12' etc. are continuous throughout the length of the three tiers of the exchanger. Should balancing considerations make it necessary, intermediate manifolds or the like may be disposed to this end in the spaces close to the A-A' or BB' levels, since no appreciable heat transfer takes place in these spaces.

FIGURES 1 and 2 show an arrangement for collecting the secondary fluid. The tubes 12, 12' etc. are tapped on to ring manifolds 16, 1 6, respectively and these manifolds are connected via pipes 17 and 17 17 and 17 to manifolds 18, 18 leading into the discharge tubes 6. A similar arrangement is provided at the bottom for the secondary fluid intake.

Other arrangements may also be used. As an example, the ring manifolds may be divided. Alternatively, they may be replaced by straight manifolds, in which case the tappings will be facilitated by bending the tubes at their ends.

FIGURE 4 illustrates a different arrangement specifically intended for the case where the heat exchanger is used to evaporate the secondary fluid. In this case, the pipes 17, 17', 17 of the first or top tier are connected to at least one separating balloon flask 19, drum or the like, contained within the exchanger, and placed, for example, near the top thereof. At least one liquid return pipe or duct 20, preferably arranged at the center of the exchanger, connects the drain of the flask 19 to the bottom inlet of the secondary fluid tubes in the last or bottom tier. In addition, the secondary-fluid vapor discharges through at least one pipe 21 located inside the primary fluid inlet pipe 5.

The manner of operation of a tier of heat exchanger elements such as the second or intermediate tier is as follows: The primary fluid arrives from the proceeding upper tier, in this case the first or top tier, by flowing along the secondary fluid tubes, at the level AA'. This draining process is blocked by the plates 13, 13 etc. and the primary fluid enters the aforementioned odd annular feed spaces devoid of tubes. The primary fluid thus finds itself in the annular spaces comprised between the barrel-plate '2 and the ferrules 10, 10 and 10" etc. and is projected in the form of jets against the secondary fluid tubes as it passes through the holes in said ferrules. The bottom parts of the annular spaces defined by the ferrules 10 and 10, 10" and 10" etc. are open at the B-B level, and the primary fluid then escapes through these bottom parts and is conveyed towards the next or bottom tier.

In the case of the first tier, the primary fluid comes directly from the top of the exchanger, while in the case of the last tier it escapes towards the bottom of the exchanger.

t is to be noted that the perforated ferrules may be replaced by any other convenient jet-producing means arranged in coaxial cylindrical clusters.

It is to be understood that the invention is not limited to 11.16 embodiments disclosed in the foregoing description and the drawings, as variations of the preferred forms may be adopted Within the scope of our invention.

What I claim is:

1. A jet counter-flow heat exchanger comprising a substantially cylindrical vertical shell having a top end and a bottom end, at least two fluids of differing temperatures being adapted to be conducted through said shell for effecting heat transfer therebetween, inlet means and outlet means for a first one of said fluids provided at said top and said bottom ends respectively, inlet means and outlet means for a second one of said fluids provided at said bottom and said top ends respectively, a plurality of nests of spaced-apart pipes within said shell interconnecting said inlet means and said outlet means for the second fluid, extending longitudinally within said shell and arranged in radially spaced substantially circular concentric rows, a plurality of separate sets of cylindrical annular guide casings, said sets being disposed in successive spaced tiers substantailly in coaxial extension of each other lengthways within said shell, said guide casings of each set being arranged in concentric radially spaced elationship and having each one a closed top end directed towards said inlet means for the first fluid and an open bottom end, each guide casing having two concentric radially spaced continuous side walls formed with perforations and an annular flat top end wall formed with orifices and rigidly interconnecting said side walls substantially at the top end thereof which is thereby closed, whereby said side walls define substantially along their whole lengths a continuous annular space therebetween through which extends a respective one of said rows of pipes entering said guide casing from said open bottom end and passing in fitting relationship through said orifices, said guide casings of each set defining further continuous annular spaces between and substantially along the whole length of the confronting side walls of respective adjacent guide casings and between and along the radially outer side Walls of the outermost ones of said guide casings and the inner wall of said shell, annular bottom closure means integral with said open bottom ends of the guide casings outside thereof and interconnecting said confronting side walls of each successive pair of adjacent guide casings in each set and said outer side walls of the outermost guide casings of each set with said inner wall of the shell, whereby said further annular spaces are closed at their bottom ends and remain open at their top ends, said pipes being traversed by said second fluid and bathed externally by said first fluid which enters said further annular spaces from said top ends and sprays said pipes with jets upon passing through said perforations in said side walls of the guide casings, so that heat transfer is effected between said first fluid in the region of said guide casings and said second fluid flowing through said pipes within said region.

2. A heat exchanger according to claim 1, wherein said closed top ends of the guide casings in each set substantially register with said open bottom ends of the guide casings in the adjacent overlying set, said rows of pipes consist of substantially straight longitudinal ducts arranged parallel to, symmetrical with the axis of said shell and extending through all of said sets of guide casings, and said perforations are substantially uniformly distributed along generating lines and parallels of said side walls of the guide casings.

3. A heat exchanger according to claim 2, wherein said perforations are disposed in common axial meridian planes and in parallel planes perpendicular to said axis, said pipes of each of the rows having their axes respectively disposed in said meridian planes containing said generating lines, so that said pipes are sprayed along two opposite faces thereof by said jets issuing from said perforations.

4. A heat exchanger according to claim 1, wherein said bottom closure means consist of coaxial ring plate members of substantially frustoconical shape tapering toward the lowermost perforations near said open bottom ends of the guide casings.

5. A heat exchanger according to claim 1, further comprising substantially flat ring plate elements applied under and against said top end walls of and inside the respective guide casings, the pipes of the same row, surrounded by the afore-mentioned guide casings, passing through and being tightly secured to a respective one of said ring plate elements, thereby forming a leakproof seal for said second fluid.

6. A heat exchanger according to claim 1, further comprising at least one torus-shaped manifold provided at both ends of said sheets of pipes which open therein and respectively communicate with said inlet means and said outlet means for the first fluid.

7. A heat exchanger according to claim 6, further comprising torus-shaped headers located in at least some of the intervals between successive ones of said rows of guide casings, each of said rows of pipes opening into one of said headers.

8. A heat exchanger according to claim 6, wherein at least said outlet means for the second fluid is located inside said inlet means for the first fluid.

9. A heat exchanger according to claim 8, further comprising a dished top head for said shell, at least one phase separator drum means housed within the inner space of said top head and communicating with the exit ends of said pipes and with said outlet means for the first fluid, and at least one drain duct extending longitudinally within said shell for liquid condensate and connecting the outlet of said drum means to the entry ends of said pipes, whereby evaporation of the ascending second fluid is achieved in the region of said inlet means for the first fluid.

References Cited in the file of this patent UNITED STATES PATENTS 1,884,778 Lucke et al Sept. 25, 1932 2,699,184 Frenkel Sept. 2, 1952 FOREIGN PATENTS 1,043,623 France June 17, 1953 823,904 Great Britain Nov. 18, 1959

Claims (1)

1. A JET COUNTER-FLOW HEAT EXCHANGER COMPRISING A SUBSTANTIALLY CYLINDRICAL VERTICAL SHELL HAVING A TOP END AND A BOTTOM END, AT LEAST TWO FLUIDS OF DIFFERING TEMPERATURES BEING ADAPTED TO BE CONDUCTED THROUGH SAID SHELL FOR EFFECTING HEAT TRANSFER THEREBETWEEN, INLET MEANS AND OUTLET MEANS FOR A FIRST ONE OF SAID FLUIDS PROVIDED AT SAID TOP AND SAID BOTTOM ENDS RESPECTIVELY, INLET MEANS AND OUTLET MEANS FOR A SECOND ONE OF SAID FLUIDS PROVIDED AT SAID BOTTOM AND SAID TOP ENDS RESPECTIVELY, A PLURALITY OF NESTS OF SPACED-APART PIPES WITHIN SAID SHELL INTERCONNECTING SAID INLET MEANS AND SAID OUTLET MEANS FOR THE SECOND FLUID, EXTENDING LONGITUDINALLY WITHIN SAID SHELL AND ARRANGED IN RADIALLY SPACED SUBSTANTIALLY CIRCULAR CONCENTRIC ROWS, A PLURALITY OF SEPARATE SETS OF CYLINDRICAL ANNULAR GUIDE CASINGS, SAID SETS BEING DISPOSED IN SUCCESSIVE SPACED TIERS SUBSTANTIALLY IN COAXIAL EXTENSION OF EACH OTHER LENGTHWAYS WITHIN SAID SHELL, SAID GUIDE CASINGS OF EACH SET BEING ARRANGED IN CONCENTRIC RADIALLY SPACED RELATIONSHIP AND HAVING EACH ONE A CLOSED TOP END DIRECTED TOWARDS SAID INLET MEANS FOR THE FIRST FLUID AND AN OPEN BOTTOM END, EACH GUIDE CASING HAVING TWO CONCENTRIC RADIALLY SPACED CONTINUOUS SIDE WALLS FORMED WITH PERFORATIONS AND AN ANNULAR FLAT TOP END WALL FORMED WITH ORIFICES AND RIGIDLY INTERCONNECTING SAID SIDE WALLS SUBSTANTIALLY AT THE TOP END THEREOF WHICH IS THEREBY CLOSED, WHEREBY SAID SIDE WALLS DEFINE SUBSTANTIALLY ALONG THEIR WHOLE LENGTHS A CONTINUOUS ANNULAR SPACE THEREBETWEEN THROUGH WHICH EXTENDS A RESPECTIVE ONE OF SAID ROWS OF PIPES ENTERING SAID GUIDE CASING FROM SAID OPEN BOTTOM END AND PASSING IN FITTING RELATIONSHIP THROUGH SAID ORIFICES, SAID GUIDE CASINGS OF EACH SET DEFINING FURTHER CONTINUOUS

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