Tube-nest heat exchanger with improved structure

Abstract

A heat exchanger includes a pressurized shell and a tube bundle with exchanging tubes between flexible tubesheets. The flexible tubesheets are reciprocally interconnected by tie rods in a central zone of the flexible tubesheets which is devoid of exchanging tubes. The exchanging tubes in the tube bundle are arranged around the tie rods. The heat exchanger may further include conveying diaphragms arranged along the tube bundle. The conveying diaphragms may be shaped, alternately, as discs and rings.

Claims

1. A heat exchanger comprising: a pressurized shell; and a tube bundle with exchanging tubes between flexible tubesheets, wherein the flexible tubesheets are reciprocally interconnected by a plurality of tie rods in a central zone of the flexible tubesheets which is devoid of exchanging tubes, and the exchanging tubes in the tube bundle are arranged around the plurality of tie rods, the plurality of tie rods being centrally positioned within the pressurized shell with the exchanging tubes surrounding all of the plurality of tie rods, and wherein each of the plurality of tie rods is a tube which: (i) has a structure corresponding to a structure of each of the exchanging tubes; and (ii) is sealed at both ends thereof.

2. The heat exchanger according to claim 1, wherein each of the exchanging tubes at a periphery of the tube bundle has a wall thickness which is less than a wall thickness of each of a remainder of the exchanging tubes in the tube bundle.

3. The heat exchanger according to claim 1, wherein each of the exchanging tubes at a periphery of the tube bundle has a diameter which is greater than a diameter of each of a remainder of the exchanging tubes in the tube bundle.

4. The heat exchanger according to claim 1, further comprising transverse diaphragms arranged along the tube bundle for conveying an exchanging fluid, wherein the transverse diaphragms alternate in shape between discs and rings along an axis of the tube bundle.

5. The heat exchanger according to claim 4, wherein one of the transverse diaphragms closest to one of the flexible tubesheets is ring-shaped.

6. The heat exchanger according to claim 4, wherein each of the transverse diaphragms shaped as rings has a central passageway which is crossed by the plurality of tie rods and is not crossed by the exchanging tubes.

7. The heat exchanger according to claim 1, wherein at least an inlet tubesheet of the flexible tubesheets has an insert protruding from a hot side of the inlet tubesheet in the central zone of the flexible tubesheets, in correspondence with the plurality of tie rods.

8. The heat exchanger according to claim 1, wherein at least an inlet tubesheet of the flexible tubesheets has a greater thickness in the central zone of the flexible tubesheets featuring interconnection with the plurality of tie rods than in a peripheral part of the inlet tubesheet.

9. A heat exchanger comprising: a pressurized shell; a tube bundle with exchanging tubes between flexible tubesheets; and radial channels for intake of an exchanging fluid or outlet of the exchanging fluid, wherein the flexible tubesheets are reciprocally interconnected by a plurality of tie rods in a central zone of the flexible tubesheets which is devoid of exchanging tubes, and the exchanging tubes in the tube bundle are arranged around the plurality of tie rods.

10. The heat exchanger according to claim 1, further comprising radial channels for intake of an exchanging fluid or outlet of the exchanging fluid.

11. The heat exchanger according to claim 9, wherein the radial channels are circumferentially evenly spaced.

12. The heat exchanger according to claim 9, wherein the radial channels are surrounded by and connected to a toroidal pipe for the intake of the exchanging fluid.

13. The heat exchanger according to claim 9, wherein the radial channels are adjacent to at least an inlet tubesheet of the flexible tubesheets.

14. The heat exchanger according to claim 10, wherein the radial channels are circumferentially evenly spaced.

15. The heat exchanger according to claim 10, wherein the radial channels are surrounded by and connected to a toroidal pipe for the outlet of the exchanging fluid.

16. The heat exchanger according to claim 10, wherein the radial channels are adjacent to at least an outlet tubesheet of the flexible tubesheets.

17. The heat exchanger according to claim 1, wherein: the tube bundle extends in an axial direction between a terminal upstream end and a terminal downstream end such that the tube bundle begins at the terminal upstream end and ends at the terminal downstream end; and the flexible tubesheets include a first flexible tubesheet at the terminal upstream end of the tube bundle and a second flexible tubesheet at the terminal downstream end of the tube bundle.

18. The heat exchanger according to claim 1, wherein at least one of: an inertia of each of the plurality of tie rods corresponds to an inertia of each of the exchanging tubes; and a section surface area of each of the plurality of tie rods corresponds to a section surface area of each of the exchanging tubes.

19. A heat exchanger comprising: a pressurized shell; and a tube bundle with exchanging tubes between flexible tubesheets, wherein the flexible tubesheets are reciprocally interconnected by a plurality of tie rods in a central zone of the flexible tubesheets which is devoid of exchanging tubes, and the exchanging tubes in the tube bundle are arranged around the plurality of tie rods, the plurality of tie rods being centrally positioned within the pressurized shell with the exchanging tubes surrounding all of the plurality of tie rods, and wherein each of the plurality of tie rods is filled with solid metal elements.

20. The heat exchanger according to claim 19, wherein at least one of: an inertia of each of the plurality of tie rods corresponds to an inertia of each of the exchanging tubes; and a section surface area of each of the plurality of tie rods corresponds to a section surface area of each of the exchanging tubes.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) To provide a clearer explanation of the innovative principles of the present invention and the advantages thereof with respect to the commonly known technique, an exemplifying embodiment in which the principles are applied will be described below, with the help of the accompanying drawings. In the drawings:

(2) FIG. 1 is a schematic, partially sectioned, side view of an exchanger according to the invention;

(3) FIG. 2 shows a schematic, cross-sectioned view of a first possible arrangement of the tube bundle in the exchanger shown in FIG. 1;

(4) FIG. 3 shows a schematic, cross-sectioned view of a second possible arrangement of the tube bundle in the exchanger shown in FIG. 1;

(5) FIG. 4 shows a schematic, cross-sectioned view according to line IV-IV in FIG. 1;

(6) FIG. 5 shows a schematic, cross-sectioned view according to line V-V in FIG. 1;

(7) FIG. 6 shows a schematic, cross-sectioned view (accordinggenerallyto line V-V in FIG. 1) of a possible embodiment of areas, in proximity to the tubesheets, for the inlet and outlet of the coolant within an exchanger according to the invention;

(8) FIG. 7 shows a partial schematic view of a section according to line VII-VII in FIG. 6; and

(9) FIG. 8 shows a schematic, partial, sectioned view of a possible variant of a central zone of the tubesheet in an exchanger according to the invention.

DETAILED DESCRIPTION OF THE INVENTION

(10) With reference to the figures, FIG. 1 shows an exchanger as a whole denoted by 10, produced according to principles of the present invention.

(11) The exchanger 10 comprises a pressurized shell 11, at the opposite ends of which there are conical diffusers or manifolds 12, 13, to which pipes 14, 15 are fitted for the inlet and outlet of the fluid to be cooled (for example, ethylene steam). A tube bundle 18 is arranged in the shell between the tubesheets 16 and 17 in order to be immersed in the exchanging fluid (e.g. water) which circulates in the exchanger via inlet and outlet pipes 19 and 20. The tubesheets are of the kind known as thin and are, therefore, flexible tubesheets, which means that the capacity to withstand flexion due to the internal pressure of the exchanger is ensured by the tube bundle welded between the tubesheets, and the tubesheets flex outwards also due to the thermal expansion of the bundle.

(12) According to the principles of the invention, the tube bundle advantageously comprises a central zone devoid of tubes and in such area the tubesheets are reciprocally interconnected by tie rods 21. The tubes, denoted as a whole with 18a and intended to be flowed through by the fluid to be cooled, are arranged around the central zone with the tie rods 21. As can be seen in the figures, the central zonedevoid of tubes but equipped with tie rodscomprises the center of the tubesheets.

(13) Essentially, the core of the bundle is composed solely of tie rods which do not take part in the circulation of the fluid to be cooled and the tubes are arranged in a torus around the tie rods.

(14) Advantageously, the area with solely tie rods can be, approximately, in correspondence with the section of the inlet pipe 14. The tie rods can be filled with solid metal elements or tubes similar to the tubes in the bundle but sealed at the ends. Generally, the inertia and section surface area thereof will be comparable to that of the exchanging tubes.

(15) FIG. 2 shows, by way of example, a possible arrangement of the bundle, showing the central tie rods (advantageously arranged in a crosswise fashion) and the tubes surrounding such tie rods.

(16) The tie rods between the tubesheets help to withstand the pressure thrust between the tubesheets. In other words, the tie rods can transfer the pressure thrust acting on the tubesheets from one tubesheet to the other.

(17) The innovative structure of the exchanger which features flexible tubesheets with the presence of tie rods in the central part of the bundle and exchanging tubes solely around the tie rods provides various advantages.

(18) First and foremost, the tie rods are immersed in the cooling fluid just like the tubes but, since such rods are not flowed through by the hot fluid, they have the same temperature as the cooling fluid (for example, in an exchanger for ethylene with exchanging water, such rods can befor exampleapproximately 10 C. colder than the exchanging tubes surrounding them).

(19) The arrangement is therefore advantageous because the buckling of the flexible tubesheets due to the pressure is mitigated in the central part by the different temperature profiles of the tubes and tie rods. Since the stresses are proportional to the deformations, the central part of the flexible tubesheets is less stressed than in the commonly known design solutions.

(20) At the same time, the tubes are also less stressed by an axial load, because the further away one moves from the center, proceeding outwards in a radial fashion, the more the axial stress decreases and the more the flexural stress increases due to the flexion (buckling due to pressure) of the tubesheet.

(21) Thanks to the decrease in the axial forces on the tubes and the improved diversion of the flow towards the peripheral tubes, the gas distribution in the tubes can be optimized.

(22) In fact, the gas flow is diverted to the tubes surrounding the tie rods and a more uniform distribution of the gas can be obtained in all the exchange tubes, in addition to a minimization of the formation of vortices and a reduced time of stay in the distribution cone for the flue gas (i.e. better yield from the rapid flue gas cooling reactions).

(23) The improved distribution of axial forces within the bundle also means that the wall of the outermost peripheral tubes (where the flexural stress component is greater than the axial stress) can be thinner, thereby increasing the internal aperture of the passageway. Alternatively, it is also possible to increase the diameter of the outer tubes as shown, by way of example, in FIG. 3.

(24) In any case, an increased passageway aperture at the periphery of the bundle results in the gas particleswhich have to travel freely along a route which is, on average, longer in order to reach the peripheral tubeshaving nevertheless the advantage of being exposed to a greater surface area and therefore lower losses of pressure.

(25) Incidentally, the thicker tubes in the inner part have a greater margin against potential catastrophic ruptures in the event of thinning due to corrosion (even though, with the solution described here, corrosion is either reduced or eliminated).

(26) Returning to FIG. 1, an insert 22 can also be featured, arranged in correspondence with the tie rods on the inlet tubesheet 16 on the hot side, in order to reduce the volume in the inlet conical diffuser.

(27) This allows the time of stay of the fluid in the conical diffuser to be reduced and improved protection of the hot tubesheet to be offered. Furthermore, diversion is the fluid towards the inlets of the tubes in the bundle is further improved.

(28) The insert 22, with a form which is generally tapered in the incoming flow direction, can be easily optimized by means of a computational fluid dynamics system, in order to better match the conformation of the conical diffuser. The insert can be made in one piece with the tubesheet or fitted thereonto in various ways, for example by keying. A removable fitting can be advantageous in order to be able to replace the insert when, possibly, worn, thereby constituting a sacrificial tubesheet for the protection of the thin tubesheet therebehind.

(29) As can be seen, again in FIG. 1, diaphragms can also be used in the exchanger according to the invention, arranged transversely along the bundle, to convey the exchanging fluid.

(30) Advantageously, such diaphragms have the form of discs 23 and rings 24, which alternate along the axis of the bundle in order to ensure circulation as shown by the arrows in FIG. 1, in other words, winding between a peripheral passageway and a central passageway. The exchanger (in particular a TLE) is, in fact, preferably vertical, with an ascending motion of the fluid (flue gases) to be cooled.

(31) As seen in FIG. 1, the first and the last diaphragm have, advantageously, a ring conformation. This is possible due to the fact that, in the central passageway of the ring-shaped diaphragm, where the flow of cooling fluid passes, solely the tie rods are, advantageously, present. In fact, in general, the central part of the tubesheet is exposed to a speed of approximately zero and therefore there is always a risk, in such central zone, of the accumulation of debris/deposits with consequent overheating locally, since the deposits and fouling in general are an additional thermal resistance which prevents removal of the heat from the tubesheet by the cooling fluid.

(32) If, according to the commonly known technique, there were no exchange tubes in such central zone, the use of ring-shaped diaphragms in proximity to the tubesheets would be impossible because such arrangement would involve an unacceptable increase in the tubesheet temperature due to the deposits, which would not allow correct removal of the heat conveyed into such zone by the exchange tubes.

(33) With the principles of the present invention, a possible accumulation of deposits in the central zone of the tubesheet does not, however, result in a rise in temperature locally because the central part of the bundle is not fed with hot fluid.

(34) In FIG. 4, there is a section of the exchanger shown which shows an advantageous embodiment of one of the ring-shaped diaphragms 24, with the central hole 25 whose perimeter follows the contour of the bundle of tie rods 21 (for example, advantageously arranged in a cross fashion) so that the solid crown part of the baffle is traversed by the exchange tubes and, preferably, supported thereby. The baffle may also have a minimum space between the peripheral edge thereof and the inner wall of the exchanger 26.

(35) In FIG. 5, however, there is a section of the exchanger shown which shows an advantageous embodiment of one of the disc-shaped diaphragms 23, with ample peripheral space 27 for circulation of the exchanging fluid between the two sides of the disc fluid.

(36) Advantageously, the possibility of using ring-shaped diaphragms in proximity to the internal faces of the tubesheets also allows improved inlet and outlet circulation of the cooling fluid.

(37) As shown in the embodiment in FIGS. 6 and 7, radial channels 28 can be advantageously featured on the edge of the tubesheet within the exchange chamber. The channels 28 are connected to the respective inlet pipes 19 through a connection pipe, for example, in the form of a torus 29 around the periphery of the exchanger. Advantageously, such channels are a plurality and are distributed evenly around the circumference of the tubesheet.

(38) The radial channels 28 face the interior of the exchanger in order to take in the flow of cooling fluid between the tubesheet and the facing ring-shaped baffle.

(39) Advantageously, the opposite end of the exchange chamber can also feature a similar structure of radial channels 28 for the outlet of exchanging fluid in proximity to the opposite tubesheet 17.

(40) The possibility of having multiple water inlets and at least one exchanging fluid outlet (which, at the outlet, can be a mixture of water plus steam), which is completely radial and allows a more uniform distribution of the fluid and overcomes various problems encountered with the commonly known systems.

(41) For example, with reference to a standard vertical TLE with ascending hot flue gases, the solution described above prevents a descending vertical two-phase flow, which would be unstable and/or pulsatile for certain operating points/surface speeds of the liquid and vapor phases.

(42) The described adduction and extraction arrangement for the exchanging fluid also allows a circular fluid flow symmetry and a configuration known as a No Tubes In The Window configuration, in which all the heat exchange tubes have the same Euler's critical load, regardless of the radial position thereof within the bundle.

(43) Moreover, by placing the outlet pipe of water/steam mixture flush with the upper tubesheet, the downflow area is eliminated. By creating a torus, with multiple access points, which collects the steam coming from all radial directions, pockets of steam are prevented from forming on the top of the exchanger.

(44) FIG. 8 shows a further advantageous embodiment, according to which the tubesheet has a local thickening 30 in the central part, in correspondence with the tie rods 21, which can be used as a corrosion/erosion allowance. This thickening is always possible thanks to the fact that, with the structure according to the invention, the central part of the tubesheet is always at approximately the same temperature as the exchanging fluid. The thickening can also implement or comprise the external flow diversion insert.

(45) At this point, it is clear how the intended aims are achieved. A tube bundle exchanger with flexible tubesheets produced according to the invention is prone to much fewer erosion and corrosion effects and also allows greater efficiency and flexibility of use. Also, it should be noted that, thanks to the principles of the invention, it is also possible to produce an exchanger which is symmetrical with respect to the transverse plane, i.e., which can be overturned, for example, to extend the working life thereof.

(46) Naturally, the description set out above of an embodiment applying the innovative principles of the present invention is given by way of example of such innovative principles and therefore must not be deemed a limitation of the patent right claimed here. For example, the proportions of the various parts of the exchanger may vary with respect to that shown in the drawings in order to adapt to specific requirements, as is easily imaginable by persons skilled in the art. Also the number of tubes, tie rods and any disc or ring-shaped internal diaphragms may vary depending on the embodiment and the specific requirements.

(47) Finally, there may be various techniques for fastening the tube bundle to the tubesheets, as is easily imaginable by persons skilled in the art. For example it may be advantageous to use Internal Bore Welding welds (IBW), as are known by persons skilled in the art and as shown schematically in FIG. 7, for the tube on the left.