BR112017017684B1 - HULL AND TUBE HEAT EXCHANGER, TUBE BEAM AND USES OF A HULL AND TUBE HEAT EXCHANGER - Google Patents

Abstract

shell and tube heat exchanger. The present invention relates to a shell-and-tube heat exchanger wherein, to allow for a uniform distribution of gas in the flow around the tube bundle, a tube bundle comprising a plurality of tubes with at least one base of tube, which is bounded on the outside by a hull surface and has a longitudinal axis extending centrally in the hull space, is disposed in a hull space, wherein the arrangement of the tubes in the tube bundle defines an area of tube, which has an inner channel around the longitudinal axis that is free of tubes and an outer channel between the outer edge of the tube bundle and the hull surface that is free of tubes, wherein, according to the invention, the The tube area has at least one connection zone between the inner and outer channel through which fluid enters into and/or exits the shell space during operation of the shell and tube heat exchanger.

Description

[001] The invention relates to a shell and tube heat exchanger according to claim 1.

[002] Shell and tube heat exchangers are also referred to as shell and tube heat exchangers and are the most frequently used heat exchangers in industry. In the case of the shell and tube heat exchanger the heat transfer area separates a hot fluid compartment from a cold fluid compartment. One fluid flows through the tubes (on the tube side), while the other fluid flows around the tubes (on the hull side). Bundles of tubes are placed in the hull and in this case it is attached to a tube base so that it forms a barrier in order to prevent mixing of both different temperature controlled fluids. To generate a higher velocity in the hull or to raise the contact frequency of the medium in the hull space with the heat transfer area, bypass segments are used. The fluid in the hull has a longer run between the inlet and outlet pipe for passage.

[003] A heat exchanger of this type according to the state of the art is shown in figure 1. The figure above shows a longitudinal section through a shell and tube heat exchanger operated in countercurrent. The figure below shows an open perspective illustration of the hull space with tube bundle and deflection segments.

[004] On the hull side the tube split has a great influence on the fluid velocity and, therefore, on the heat transfer as well as on the pressure loss. Conventional countercurrent heat exchangers have non-uniform flow lines on the side. hull and thus a higher mechanical load. Furthermore, the pressure losses in the case of these heat exchangers are very large.

[005] The next step in the development of the shell and tube heat exchanger was a so-called radial flow apparatus. A heat exchanger of this type is illustrated in Figure 2 in a longitudinal section. In the figure above, a longitudinal section is illustrated through a hull and tube heat exchanger operated in countercurrent. The figure below shows an open perspective illustration of the hull space with tube bundle and diversion segments, the respective top space for the supply and discharge of fluid on the tube side and on the hull side is not shown.

[006] With a shell and tube heat exchanger with radial flow, spots and weakening of the conventional shell and tube heat exchanger can be reduced. By uniformly circulating the central channel outwards in the radial direction or from the space between the heat exchanger hull around the tube bundle to the central channel, both minimal mechanical loads and also smaller pressure losses in the hull space are obtained. heat exchanger. This not only provides freedom in the selection of the device on the hull side of the inlet and outlet pipes, but also a more compact design of the tube bundle.

[007] As a disadvantage of the radial hull and tube heat exchanger, it is considered the fact that it builds a complicated end and top dome in which both the inlet and the outlet tubes for tubes on the hull side as well as on the side tube for fluid circulation are integrated through the tube bundle. Or the pipes for fluid inlet and outlet on the hull side need to be placed directly over the hull which leads to uniformly flowing loads in the corresponding inlet or outlet chamber.

[008] It is the task of the invention to enable uniform circulation from the central channel outwards to the hull area or from the space between the heat exchanger hull around the tube bundle to the central channel and simultaneously a fluid supply to inside and a simple fluid discharge in terms of design out of the hull space. It is primarily the task of the invention to provide the pressure loss on the shell side of a shell and tube heat exchanger relative to one with comparable heat transfer performance. Furthermore, it is a task of the invention to be able to reduce in the case of comparable heat transfer performance the frame size of a shell and tube heat exchanger.

[009] These tasks are solved in a surprisingly simple way through a shell and tube heat exchanger according to claim 1. Advantageous improvements are the subject of the claims.

[0010] The invention provides a shell-and-tube heat exchanger in which a bundle of tubes composed of several tubes with at least one tube base, which is delimited outward by a shell area and has a tube bundle, is arranged in a shell space. a longitudinal axis that runs centrally in the hull space and the arrangement of tubes in the tube bundle defines a tubular sheet having an inner tube-free channel around the longitudinal axis and an outer tube-free channel between the outer edge of the bundle of tubes and the hull area, according to the invention, the tubular sheet presents between the inner channel and the outer channel a connection zone through which, during the operation of the shell and tube heat exchanger, the fluid enters the space of hull and/or exits the hull space.

[0011] In the example of the basic form of a radial shell and tube heat exchanger, the mode of operation of the solution according to the invention is explained in more detail below. In the case of a cylindrical heat exchanger, the tubes are arranged radially to a tubular sheet with a circular cross section at first. The tube bundle in this case is configured in such a way that it does not form a complete annular bundle, but by means of the connection zone a segment and any kind of circular cross section of the tube sheet are omitted by the tube occupation. Thereby the advantages of a classic shell and tube heat exchanger, especially of the aforementioned countercurrents, is combined with a radial shell and tube heat exchanger. The invention thus enables better heat transfer with reduced pressure loss in the hull space. By means of the heat exchanger according to the invention, lower mechanical loads of the heat exchanger during operation are realized compared to the conventional shell and tube heat exchanger without the need for a top dome and end of complicated construction. Before, it is possible to dispense with a dome in the conventional direction subsequent to the tube bases in the longitudinal direction of the heat exchanger at first. In this way it is possible with the aid of the invention more compact and therefore also smaller.

[0012] Briefly speaking through the shell and tube heat exchanger according to the invention a "semiradial circulation" is realized. A heat exchanger according to the invention is therefore referred to also as "Semi RF Heat Exchanger". In this case, the expression "semi" can be understood by the fact that only a part - not necessarily the half - of the tubular sheet is equipped with tubes.

[0013] The hull space is externally delimited basically parallel to the surrounding curves around the tube bundle by the hull area. Within the scope of the invention, the tube bundle can in this case initially have a random external shape.

[0014] Mainly the external delimitation of the bundle of tubes seen in the cross section can be surrounded by a circle, a polygon, for example by a rectangle, preferably a square or an ellipse.

[0015] The tube bundle tubes are mainly individually insulated by the hull area in a direction perpendicular to its longitudinal axis or relative to the longitudinal axis of the hull heat exchanger and tubes so that during operation of the hull heat exchanger and tubes the complete tube bundle can be freely circulated between the inner channel and the outer channel. The tube bundle is generally coupled to its first tube base in a feed chamber for feeding a tubular space medium that circulates during operation of the shell and tube heat exchanger through the tubes and its second tube base. tube in a discharge chamber for the discharge of a medium and tubular space which circulates during operation of the shell heat exchanger and tubes through the tubes so that the tubes open in the supply or discharge chamber. In a special embodiment the tubes of the tube bundles can also be held by just a single tube base and in this case they present a deviation between their two passages through the tube bases, for example which can be a curved U-shaped deviation . Therefore, the feed and discharge chambers can be housed adjacent to each other in a single end dome.

[0016] The "connection zone" of the shell and tube heat exchanger according to the invention is the area in which the flow resistance for the hull space fluid is reduced relative to the flow resistance for the radial circulation of the tube bundle. In this area the packing density of the tubes in the tube bundle is reduced.

[0017] Mainly, the connection area can be free of tubes in the tubular sheet. The number of tube passes through an area perpendicular to the longitudinal axis is smaller in the connection zone than in the area placed outside the connection zone of the tubular sheet.

[0018] The formulation that through the connection zone during operation the fluid enters the hull space "and/or" leaves the hull space, refers to a constructive form within the scope of the invention according to which the heat exchanger can present several chambers so that in a first chamber through the connection zone fluid can be fed from the hull space and in a last chamber through the connection zone fluid can be discharged from the hull space out of the heat exchanger. If the heat exchanger has a single chamber, the first and last chambers will be the same and the hull space fluid circulates individually through these said chambers.

[0019] In a simple embodiment in terms of design the tubes of the tube bundle are arranged by their longitudinal extension in parallel direction. Parallel alignment of the tubes is not necessarily necessary, for example the tubes can each also pass over a spiral track around the longitudinal axis in the hull space.

[0020] According to an advantageous development of the invention, the shell and tube heat exchanger has a single chamber.

[0021] Mainly, the shell and tube heat exchanger is designed with a chamber as a module for a multi-piece shell and tube heat exchanger in which the outlet out of the discharge chamber is formed for connection to the inlet into the feed chamber. Thereby, a union of several shell and tube heat exchangers is made possible forming a type of tower or stack in which during operation the shell space fluid after leaving one heat exchanger module enters the next module.

[0022] In order to be able to make longer circulation paths in the case of the highest possible impeller gradient for heat transfer, the shell and tube heat exchanger is arranged in a further development of the invention two or more chambers, preferably up to twenty chambers around a single bundle of tubes, whereby between chambers adjacent to each other there is arranged at least one deflection element for the hull space fluid.

[0023] During operation of the hull and tube heat exchanger, the hull space fluid enters the first chamber which is externally delimited by the hull area and the edge of the connection zone between outer channel and inner channel of the tubular sheet of a base of tube and an offset segment. The deviation segment is composed of a disk with an area perpendicular to the longitudinal axis that corresponds inversely to the tubular sheet, from which an inner area is cut or an outer area is sectioned. Mainly, the inner area in its cross section practically corresponds to that of the inner channel and the outer area in its cross section practically corresponds to that of the outer channel.

[0024] A simple connection in constructive terms to apparatus arranged upstream or downstream is made possible in accordance with the invention by the fact that the shell and tube heat exchanger has a supply device for fluid from the shell space into the channel internal and into the external channel and a discharge device for hull space fluid out of the internal channel or out of the external channel, the connection zone between the external channel and the internal channel being an integral component of the feeding device or of the discharge device.

[0025] In the case of an odd number of chambers with respect to the longitudinal axis the direction of flow of the hull space fluid through the feed device and through the discharge device is the same. That is, through the feeding and through the discharge the fluid circulates in the longitudinal axis inwards or circulates outwards from it.

[0026] In the case of an even number of chambers with respect to the longitudinal axis the direction of flow of the hull space fluid through the feed device is opposed to the direction of flow through the discharge device. That is, through the feed the hull space fluid circulates to the longitudinal axis (leaves the longitudinal axis), and through the discharge the hull space fluid circulates outside the longitudinal axis (goes to the longitudinal axis).

[0027] Within the scope of the invention, the bundle of tubes can mainly have a circular cross-section so that, in a simple way in terms of construction, an internal structure of the heat exchanger can be obtained that ensures, during operation, an especially uniform circulation of the fluid. of hull space.

[0028] The bundle of tubes, in this case, can be arranged concentrically with respect to the longitudinal axis. In a further development of the invention, the tube bundle is arranged eccentrically with respect to the longitudinal axis on which an additional possibility of influencing circulation in the hull space is created by positioning the tube bundle.

[0029] The connection zone presents in an advantageously simple configuration a first area and a second penetration area as well as two lateral boundaries, the first penetration area being the passage between the outer channel and the connection zone, the second area of penetration is the passage between the connection zone and the inner channel, the first lateral boundary extends from an edge that passes longitudinally of the hull space of the first penetration area to the corresponding edge that passes longitudinally of the space of hull of the second penetration area and the second lateral boundary extends from the other longitudinally passing edge of the hull space of the first penetration area to the corresponding longitudinally passing edge of the hull space of the second penetration area.

[0030] The two lateral boundaries of the connection zone basically run parallel to each other when the connection zone must make the shortest way between the inner channel and the outer channel. Within the scope of the invention, the lateral boundaries of the connection zone can create in a direction perpendicular to the longitudinal axis or parallel to the longitudinal axis also by some segments different cross-sectional shapes of the connection zone. The cross-section of the connection zone is the area through which the hull space fluid flows as it flows between the inner channel and the outer channel.

[0031] The invention creates a plurality of possibilities to create, through the configuration of the geometry of the connection zone, the desired circulation profile during the operation of the hull space fluid and therefore also adjust the heat transfer kinetics. Examples for the configuration of the connection zone geometry will be described in more detail based on the attached figures.

[0032] In another advantageous embodiment of the invention the tube bundle is composed of at least two, preferably three or four or five tube bundle modules. Thus, a structure of a desired tube bundle is made possible by realizing the connection zone according to the invention with prefabricated modules according to the modular principle.

[0033] The tube bundle modules can be in this case of the same type.

[0034] Mainly n-1 (for example I will give) tube bundle modules with internal burr of tube basically circular shape 1/n (for example of semicircle shape) in cross section perpendicularly to the longitudinal axis can be connected together, being that the connection zone is formed through the n-te module (for example fourth) that is missing for the complete circle. The connection of the tube bundle modules is preferably made simply by insertion into at least one tube base.

[0035] In another embodiment of the invention, at least one tube bundle module of different type is designed in relation to at least one other tube bundle module. Mainly according to the embodiment, a tube bundle module comprises a cutout from the tubular sheet with the connection zone and adjacent tubes, while one or the other tube bundle modules contribute with the other tubes in relation to the full tubular blade.

[0036] The invention also provides a bundle of tubes for a shell and tube heat exchanger described above. Such a bundle of tubes can be manufactured and distributed separately. The final assembly of the total heat exchanger can be done for example firstly at the place of use by mounting in the hull and placing the supply and discharge lines in the connections to the connection zone.

[0037] The shell and tube heat exchanger according to the invention can be used basically for liquid and gaseous media as well as for fluids, which contain liquid and gaseous components such as aerosols or wet steam. Due to the relatively large heat exchanger area obtainable with the invention, the shell and tube heat exchanger can be advantageously employed as a gas-gas heat exchanger, also for the exchange of heat between two gaseous fluids basically. For example, the shell and tube heat exchanger can be used for heat recovery from hot exhaust gas streams. A special area of application results from the use in the context of processes for the synthesis of sulfuric acid (H2S04).

[0038] The invention will be clarified in more detail below with reference to the attached drawings based on examples of embodiment. In this case, the same or different components are marked with the same reference signs and the characteristics of the different examples of embodiment can be combined with each other where:

[0039] Figure 1 shows a schematic illustration of a longitudinal section through a hull and tube heat exchanger operated in countercurrent according to the state of the art (above) as well as a schematic open perspective illustration of the corresponding hull space with tube bundle and bypass segments (below),

[0040] Figure 2 shows a schematic illustration of a longitudinal section through a hull and tube heat exchanger operated in radial countercurrent according to the prior art (above) as well as a schematic open perspective illustration of the corresponding hull space with bundle of tubes and diversion segments (below), with the respective top space for the supply and discharge of fluid on the tube side and on the hull side not shown,

[0041] Figure 3 shows an open schematic perspective illustration of a shell and tube heat exchanger according to the invention with a chamber,

[0042] Figure 4 shows an open schematic perspective illustration of a shell and tube heat exchanger according to the invention with two chambers,

[0043] Figure 5 shows an open schematic perspective illustration of a shell and tube heat exchanger according to the invention with three chambers,

[0044] Figure 6 shows an open schematic perspective illustration of a shell and tube heat exchanger according to the invention with four chambers,

[0045] Figure 7 shows an external schematic perspective view of the hull space with feeding and discharging devices of the hull and tube heat exchanger 1 shown in Figure 6,

[0046] Figure 8 shows a schematic illustration of a longitudinal section of another embodiment of the shell and tube heat exchanger 1 according to the invention,

[0047] Figure 9 shows a schematic illustration of a longitudinal section of another embodiment of the shell and tube heat exchanger 1 according to the invention,

[0048] Figure 10 shows a schematic illustration of a longitudinal section of another embodiment of the shell and tube heat exchanger 1 according to the invention,

[0049] Figure 11 shows a schematic illustration of a cross section through a bundle of tubes according to another embodiment of the shell and tube heat exchanger 1 according to the invention,

[0050] Figures 12 to 30 show a schematic illustration respectively of a cross section through a bundle of tubes according to respectively another embodiment of the shell and tube heat exchanger 1 according to the invention,

[0051] Figure 31 shows an open schematic perspective illustration of a shell and tube heat exchanger according to the invention with an (open) chamber, in which the shell is disposed eccentrically to the bundle of tubes, and the view corresponding in cross section (below).

[0052] In the figures, it is suggested to partially facilitate the understanding of the flow direction of the hull space fluid and the tube space fluid through arrows as it is done during operation of the hull and tube heat exchanger according to invention.

[0053] The tubular sheet can present according to the invention in the simplest case, a radial shape, that is, it can be circular in shape, however, tubes are not arranged along the entire perimeter of the circle. Through a groove independent of the connection zone the hull space fluid can circulate into the central channel of the heat exchanger. From there, the fluid circulates radially around the tubes in the direction of the heat exchanger shell. In the case of a multi-chamber shell and tube heat exchanger the fluid flows from there parallel to the shell wall to the next chamber where it can again flow radially through the tube bundle to the central channel of the heat exchanger. In this way, the fluid is routed to the central channel of the next chamber. The position of the manifolds as a supply and discharge device for the hull space fluid as well as the dome follows the same principle as that of a conventional hull and tube heat exchanger with the difference that the tubular sheet is constructed accordingly. with the principle of a radial shell and tube heat exchanger.

[0054] Figures 3 to 10 illustrate the operating mode explained above in principle of the shell and tube heat exchanger according to the invention based on the different examples.

[0055] In figure 3 a heat exchanger with a chamber is illustrated. The fluid on the side of the tube enters through the dome which opens in the flat reproduction of the perspective illustration from the left to the bottom, is divided into the tubes and exits again through the dome which opens from the right to the top. The hull space fluid is led through an opening which is below in the flat reproduction of the perspective illustration into the connection zone and exits after its passage from the hull space through the opening I is above, out of the heat exchanger . The geometry of the connection zone is determined in addition to the length of the hull space of the chamber, which is in connection with the supply or discharge device for the hull fluid, through the width of this chamber and the measurement and positioning of both boundaries sides illustrated in matte black of the connection zone.

[0056] In figure 4 is shown another embodiment of the shell and tube heat exchanger according to the invention, which has two chambers that are separated by a baffle in the tubular sheet. The hull space fluid is led through an opening which is located below right in the flat reproduction of the perspective illustration into the connection zone and from there into the inner channel. After its passage from the first chamber of the hull space it enters through the outer channel released by the deflector into the second chamber and there it circulates through the tubular sheet from the outside to the inner channel. From there the hull space fluid leaves the inner channel in the connection zone and exits through the opening below left in the perspective illustration out of the heat exchanger.

[0057] Between the two chambers of the embodiment illustrated in figure 4 other chambers can be arranged in order to increase the heat exchange area. In figure 5 a corresponding heat exchanger with such an additional chamber is illustrated. In figure 6 a corresponding heat exchanger with two additional chambers of this type is shown.

[0058] Figure 7 shows an external view of the hull space of the embodiment illustrated in Figure 6. A supply device and a discharge device for the hull space fluid is respectively seated in the form of a dome over the space of hull whose hull area has corresponding cavities in order to allow penetration of the hull space fluid out of the feed device into the connection zone of the first chamber and out of the connection zone of the last chamber into the discharge device .

[0059] In figure 8 a longitudinal section is made through a shell and tube heat exchanger with two chambers. In the case of this embodiment, the hull space fluid is fed in the direction in the paper plane to the inner channel of the first chamber, which is located below in the illustration in figure 8. After the passage of the tube bundle to the first chamber the hull space fluid circulates in the outer channel around the deflector and passes from the outside to the inside the second chamber tube bundle which is situated above in the illustration in figure 8. The discharge of the hull space fluid is made through the connection zone to the discharge device in the direction from the paper plane exiting the inner channel of the second chamber. Through end domes above and below reproduced in the illustration in figure 8 schematically the fluid on the tube side is introduced into and withdrawn from the heat exchanger.

[0060] In the variant shown in figure 9 of a heat exchanger according to the invention the discharge of the hull space fluid is made directly out of the inner channel of the second chamber through a centrally arranged discharge device.

[0061] In the case of the embodiment illustrated in figure 10 of the heat exchanger according to the invention the flow direction of the hull space fluid is inverse to the illustration shown in figure 9; the conduction of fluid from the hull space directly into the inner channel of the chamber through which it first passed through a centrally disposed feeding device. Discharge of the hull space fluid is in the direction, out of the paper plane, out of the inner channel of the chamber through which it second passes through the connection zone to the discharge device.

[0062] The tubular sheet can initially have a radially arranged shape or reproduce with the help of several segments a radial shape. The number of segments can be random.

[0063] Inside the tubular sheet the tubes can be arranged aligned in relation to one another or displaced from each other. Another possibility for arranging the tubes relative to one another within the scope of the invention is a special variant of the offset arrangement, namely the arrangement of series of tubes positioned - viewed from the longitudinal axis - consecutively so that the tubes are arranged over a curved track. This arrangement is achieved when a composite wall is constructed with tubes, whose central points are positioned on concentric circles around the longitudinal axis. In the figures curved lanes 28 are marked as dotted lines.

[0064] The bundle of tubes according to the invention presents in a corresponding preferred embodiment at least one segment in which tubes are arranged with their central points on concentric circles, at least three, in relation to the longitudinal axis so that the line connecting the center points of a tube relative to a tube of the next larger diameter circle while routing to an adjacent tube of a nearby larger diameter circle results in a curved track 28. With this the invention creates the possibility of compressing the tubes in circles adjacent to each other since the distance of the circles, over which the center points of the tubes are arranged, can be selected in the case of properly dimensioned tube distance also to be smaller than the tube radius. Tube arrangements of this type are embodied in the tube bundle, which are illustrated in the figures.

[0065] The fluid inlet groove and the fluid outlet groove of the connection zone, which are formed by the absence of tubes on the tubular sheet, can adopt a random geometry such as radial, axial, spiral, rectangle, triangle with the tip pointing towards the center or outwards.

[0066] Geometries of this type will be clarified in more detail below based on figures 11 to 31. In figures 11 to 16 are additionally drawn flow arrows that illustrate, the flow of the hull space fluid in operation.

[0067] In figures 11 and 12 is shown a tubular blade according to an embodiment of the invention, in which the connection zone has cross-sectional area in the direction of the longitudinal axis in relation to a constant cross section; the lateral boundary areas of the connection zone are parallel to each other. Figure 17 shows an alternative tubular sheet in the case of the same area with another arrangement of tubes and also parallel walls of the connection zone. Also in Fig. 27, lateral boundaries of the connection zone are arranged parallel to each other on the tubular sheet, the connection zone carrying the hull space fluid in this case tangentially to the inner channel (see below).

[0068] In figures 13 bis 16, 18, 19, 21, 25, 26, 28, 29 and 30 are shown tubular blades in which the connection zone thins towards the longitudinal axis at an angle CC (alpha). In figure 20, a tubular sheet is illustrated, in which the connection zone widens towards the longitudinal axis at an angle CC. In this case, the first or second lateral delimitation of the connection zone passes through at least segments radially seen from the longitudinal axis. Also, both lateral boundaries of the connection zone can pass at least through segments radially seen from the longitudinal axis.

[0069] The two lateral boundaries of the connection zone may include within the scope of the invention viewed from the longitudinal axis or in the direction from the outer channel to the inner channel between them an angle in the range of approximately 180° to approximately 10°.

[0070] The vertex of the angle CC must be located in this case not necessarily on the axis in the longitudinal direction, before its position can be selected with respect to the configuration of the hull space fluid flow profile.

[0071] Mainly in the case of at least one lateral boundary conducted tangentially on the edge of the inner channel of the connection zone, the vertex of angle CC is not located in the longitudinal axis, but mainly in the area of the inner channel outside the longitudinal axis or in the area provided of tubular sheet tubes.

[0072] According to another embodiment of the invention, the first or second lateral boundary or both lateral boundaries of the connection zone pass in cross section perpendicularly to the longitudinal axis at least in segments basically tangentially to the inner channel edge.

[0073] Figure 26 illustrates a variant of this form of realization in which both lateral boundaries pass tangentially to the edge of the inner channel. In the case of the embodiment illustrated in Fig. 28, one lateral boundary runs tangentially to the edge of the inner channel, the other lateral boundary of the connection zone runs radially to the longitudinal axis.

[0074] In the case of the embodiment illustrated in Figure 29, one side boundary passes tangentially to the edge of the inner channel, the other side boundary of the connection zone passes over a spiral track that wraps from the outer channel to the inner channel. The center of the spirals is located in the tube-tubed area of the tubular sheet outside the connection zone.

[0075] Within the scope of the invention, depending on how the flow of the hull space fluid is to be conducted in the connection zone, the first or second lateral boundary or both lateral boundaries of the connection zone may pass in cross section perpendicularly to the longitudinal axis by less by curved segments wherein the first or second lateral boundary or both at least segmented lateral boundaries primarily define a segment of circular arc or a segment of a spiral.

[0076] The radius of the circular arc segment of both boundaries can in this case be the same or different. The spiral has a center in the compartment between the outer channel and the inner channel. In figure 22 a tubular blade is shown according to another embodiment of the invention in which both lateral boundaries pass according to a spiral track.

[0077] The illustrations in figures 24 and 25 show embodiments, in which in a first segment the lateral boundaries pass in a spiral shape to the inner channel, and in a second segment the lateral boundaries pass adjacent to the outer channel to the outer channel. in relation to the longitudinal axis.

[0078] The number of tubes per cross-sectional area perpendicular to the longitudinal axis in the connection zone can be varied within the scope of the invention. In a further development of the invention, the number of tubes per cross-sectional area perpendicular to the longitudinal axis in the connection zone is smaller than outside the connection zone, in particular the connection zone can be free of tubes.

[0079] In figures 13, 14, 18, 19 and 23 to 25 are shown embodiments in which tubes are arranged in the connection area, but less than in the remaining area of the tubular sheet outside the inner channel and the outer channel. In the case of the embodiment, whose tubular lamina is shown in cross section in Figure 23, the tubes are arranged in the connection zone in such a way that a double spiral track is formed for transporting the hull space fluid through the zone of connection. At least one tube, preferably several tubes, can or can be arranged or arranged according to the invention in the connection zone, so that the connection zone of multiple threads is realized.

[0080] Within the scope of the invention, the first or second lateral boundary or both lateral boundaries of the connection zone can be covered in at least segments. In figures 12 to 21 and 26 to 30 embodiments appear with such coatings in the lateral area of the connection zone.

[0081] A metallic sheet is preferably installed as a coating for separating the connection zone in the area of the lateral boundary or lateral boundaries in the tubular sheet. The sheet metal is mainly formed according to the shape of the lateral fencing or lateral fences in question, in flat or curved shape.

[0082] In an advantageous development of the invention, the shell and tube heat exchanger has at least two, mainly three or four or five connection zones that are preferably evenly distributed in the tubular sheet. A tubular blade of such an embodiment is shown in figure 30 with four connection zones. These are evenly distributed around the perimeter of the tubular sheet.

[0083] The connection zones are separated from each other by areas occupied with tubes. Several connection zones can converge in the outer hull so that only respectively a supply and discharge device for the hull space fluid can be connected to the shell and tube heat exchanger. Within the scope of the invention, however, depending on the application case, even more supply and/or discharge devices can be placed, up to the number of connection zones in the shell and tube heat exchanger.

[0084] In figure 31 is shown another embodiment of the invention according to which the fluid circulation of the hull space is further improved with respect to a uniform gas distribution in the tube bundle. As can be seen in the perspective view reproduced in figure 31 above, an inlet opening in the outer channel is provided with an extension in the direction parallel to the longitudinal axis which is greater than in the perpendicular direction. The outlet opening, which connects to the connection zone, compared to the inlet opening has a shorter extension in the direction parallel to the longitudinal axis and a wider extension in the direction perpendicular to it, especially the outlet opening is shaped Circular. In the case of the embodiment shown, the discharge of the fluid from the hull space through the connection zone is carried out separately. For comparison purposes: In the case of the embodiment shown in figure 1, the hull space fluid is fed separately through the connection zone.

[0085] In addition - and in this case it is a constructive measure independent of the selection of cross-sectional dimensions of inlet opening and outlet opening for the hull space fluid - the tubular blade is positioned eccentrically in relation to the space of hull on this one (see figure below in figure 31). The longitudinal axis of the tube bundle is arranged offset relative to the longitudinal axis of the hull. The direction of displacement widens the outer channel on the opposite side, in the example shown the tube bundle is shifted downward so that the outer channel is widened upward. In this way, the hull space fluid that circulates there can be entertained before passing through the tubes in a larger area. Also the eccentric arrangement of the tube bundle can contribute to an even gas distribution in the tube bundle.

[0086] The fluid inlet and fluid outlet pipes of the hull space fluid may, within the scope of the invention, assume in principle a random configuration, for example with a rectangular, oval or circular cross section. The working temperature range of the shell and tube heat exchanger according to the invention can be between -270 to 2000 °C Liége. A working circle between 0 to 700°C is preferred.

[0087] The tube bundles described here can be used as shell and tube heat exchanger or separately as part of another apparatus, as soon as heat transport occurs as a main function or secondary function.

[0088] In the following examples the performance of two heat exchangers of a so-called "semiradial heat exchanger" according to the invention and the performance of a conventional "radial heat exchanger" are compared to each other. In each example both heat exchangers have the same tube length as well as the same inner and outer tube diameter as well as the same tube division. The heat exchangers compared differ in terms of the number of tubes. Embodiment example 1

[0089] A semi-radial heat exchanger with 76.1 mm outer diameter tubes with a total heat transport area of 573.78 to square meters is used for heat transfer between gas streams in a sulfuric acid plant with the following parameters reproduced below.

[0090] The amount of heat transferred is 607 kW.

[0091] In the case of a radial heat exchanger with the same tube division and tube diameter as well as the same tube length with a heat transfer area of 577 square meters the power is only 560 kW.

Exemplo de concretização 3[0092] In the case of using the same radial and semiradial heat exchanger as in Embodiment Example 1 in another process with the following gas composition, the radial heat exchanger has only a power of 634 kW, while the heat exchanger according to the invention has a power of 677 kW.

Implementation example 3

[0093] In this example the semi-radial heat exchanger according to the invention has the same power as that of the radial heat exchanger from Embodiment Example 2 under the same process conditions, that is, a power of 634 kW. Tube diameter, tube length as well as tube split remain the same for both heat exchangers, but the number of tubes is reduced for the semi-radial heat exchanger. In this case it is then necessary for the indicated power of the semi-radial heat exchanger only a heat transfer area of 474 square meters while the radial heat exchanger has a transfer area of 577 square meters.

[0094] It will be evident to the person skilled in the art that the invention is not restricted to the examples described above, but rather can be varied in multiple ways. Especially, the characteristics of the individually illustrated examples are also combined with each other or mutually exchanged.Reference Listing1 Shell and tube heat exchanger11 chamber, first chamber12 last chamber13 Supply line for hull space fluid, supply device14 Discharge line for hull space fluid,discharge device2 tube bundle20 tube21 inner channel23 outer channel24 tube bundle outer edge28 curved track200 tube bundle module29 first tube base30 second tube base250 feed chamber260 discharge chamberR middle tube spaceM middle of hull space3 hull space 31 hull area32 deflector, deflection segment for hull space fluid 33 longitudinal axis4 connection zone41 first penetration area45 edge of first penetration area42 second penetration area46 edge between second penetration area43, 44 side fences430, 440 cladding, border plate side angle (0C = alpha)

Claims (23)

1. Shell and tube heat exchanger (1), in which, in a shell space (3), a tube bundle (2) consisting of a plurality of tubes (20) with at least one tube base is arranged (25; 26), which to the outside is delimited by a hull surface (31) and which has a longitudinal axis (33) that extends centrally into the hull space, with the arrangement of the tubes (20) in the tube bundle (2) defines a tube plate, which has an inner channel (21) free of tubes around the longitudinal axis (33) and an outer channel (23) free of tubes between the outer edge (24) of the tube bundle and the hull surface (31), the tube plate between the inner channel (21) and the outer channel (23) having at least one connection area (4), through which during the operation of the hull and tube heat exchanger (1) enters fluid (M) into the hull space (3) and/or leaves the hull space (3), the connection zone being formed by a segment of circular cross section of the tube arrangement where the tubes are shortened, characterized by the fact that the tubes (20) of the tube bundle (2) are surrounded only by a hull surface (31) in the direction perpendicular to its longitudinal axis so that during operation of the shell and tube heat exchanger, the medium can flow freely around the entire bundle of tubes (2) between the inner channel (21) and the outer channel (23). 2. Shell and tube heat exchanger (1) according to claim 1, characterized in that the shell and tube heat exchanger has a single chamber (11). 3. Shell and tube heat exchanger according to claim 1 or 2, characterized in that the shell and tube heat exchanger has two or more chambers (11,12) preferably up to twenty, around one a single bundle of tubes (2), a diversion segment (32) for the hull space fluid (M) being arranged between chambers adjacent to each other. 4. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the shell and tube heat exchanger has a supply line (13) for hull space fluid ( M) in the inner channel (21) or in the outer channel (23) and a discharge line (14) for the hull space fluid (M) of the outer channel (23) or the inner channel (21) where the connection (4) is an integral component of the supply line (13) and/or discharge line (14). 5. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the bundle of tubes (2) has a circular cross-section. 6. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the bundle of tubes (2) is arranged concentrically or eccentrically in relation to the longitudinal axis (33). 7. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the connection zone (4) has a first and a second penetration area (41, 42) as well as two lateral boundaries (43, 44), the first penetration area (41) being the passage between the outer channel (23) and the connection zone (4), the second penetration area (42) being the passage between the connection zone (4) and the inner channel (21), the first lateral boundary (43) extends from an edge (45) that runs in the longitudinal direction of the hull space (3) from the first penetration area (41) to the corresponding edge (46) which runs longitudinally through the hull space of the second penetration area (42) and the second lateral boundary (44) extends from the other edge (45) which runs longitudinally through the hull space ( 3) from the first penetration area (41) to the corresponding edge (46) which passes in the longitudinal direction of the space of c. ascus (3) of the second penetration area (42). 8. Shell and tube heat exchanger (1), according to claim 7, characterized in that the two lateral boundaries (43, 44) of the connection zone (44) pass through at least some segments basically in the direction parallel to each other. 9. Shell and tube heat exchanger (1) according to claim 7 or 8, characterized in that the two lateral boundaries (43,44), seen from the longitudinal axis (33), include at least by segments from each other, an angle (α) in the range of approximately 180° to about 10°. 10. Shell and tube heat exchanger (1) according to any one of claims 7 to 9, characterized in that the two lateral boundaries (43,44) include in the direction from the outer channel (23) to the channel internal (21), at least by segments to each other, an angle (α) in the range of approximately 180° to approximately 10°. 11. Shell and tube heat exchanger (1) according to any one of claims 7 to 10, characterized in that the first or second side enclosure or both side enclosures (43, 44) of the connection zone (4 ) at least by segments pass or pass radially seen from the longitudinal axis (33). 12. Shell and tube heat exchanger (1) according to any one of claims 7 to 11, characterized in that the first or second side enclosure or both side enclosures (43,44) of the connection zone (4 ) passes or passes in cross section perpendicularly seen from the longitudinal axis (33) at least by segments basically tangentially to the edge of the inner channel (21). 13. Shell and tube heat exchanger (1) according to any one of claims 7 to 12, characterized in that the first or second side enclosure or both side enclosures (43, 44) of the connection zone (4 ) in the cross section passes or passes curved/curved perpendicularly seen from the longitudinal axis (33) at least in segments, with the first or second lateral boundary or both lateral boundaries defining or defining at least by segments mainly a segment of circular arc or a segment of a spiral. 14. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the number of tubes (20) per cross-sectional area perpendicular to the longitudinal axis (33) in the connection zone ( 4) is smaller than outside the connection zone or that the connection zone is free of pipes. 15. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the shell and tube heat exchanger has at least two, mainly three or four or five connection zones (4 ) which are preferably evenly distributed on the tube plate. 16. Shell and tube heat exchanger (1) according to any one of claims 7 to 15, characterized in that the first or second side enclosure or both side enclosures (43, 44) of the connection zone (4 ) at least by segments is or are covered. 17. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that on the tube plate are arranged at least by areas, tubes (20) with their center points in at least three circles concentric with respect to the longitudinal axis (33) so that the connecting line from the center points of a tube of one circuit to a tube of the circuit with the next largest diameter while driving to an adjacent tube of the next circuit with the largest diameter results on a curved path (28). 18. Shell and tube heat exchanger (1) according to any one of the preceding claims, characterized in that the tube bundle is composed of at least two, preferably three or four or five tube bundle modules (200 ). 19. Shell and tube heat exchanger (1) according to claim 18, characterized in that the tube bundle modules (200) are of the same type. 20. Shell and tube heat exchanger (1) according to claim 18, characterized in that at least one tube bundle module is designed of a different type in relation to at least one other tube bundle module. 21. Tube bundle (2) for a shell and tube heat exchanger as defined in any one of claims 1 to 20 in which, in a shell space (3), a tube bundle (2) consisting of a plurality of tubes (20) with at least one tube base (25; 26), which to the outside is delimited by a hull surface (31) and which has a longitudinal axis (33) extending centrally in the hull space, the arrangement of the tubes (20) in the tube bundle (2) defining a tube plate, which has an inner channel (21) free of tubes around the longitudinal axis (33) and an outer channel (23) free of tubes between the outer edge (24) of the tube bundle and the hull surface (31) so that during the operation of the shell and tube heat exchanger, the medium can flow freely around the entire the bundle of tubes (2) between the inner channel (21) and the outer channel (23) characterized by the fact that the tube plate between the inner channel (21) and the outer channel (23) it has at least one connection zone (4), through which, during operation of the shell-and-tube heat exchanger (1), fluid (M) enters the hull space (3) and/or exits the hull space (3 ), where the connection zone is formed by a circular cross-sectional segment of the pipe arrangement where the pipes are missing. 22. Use of a shell and tube heat exchanger (1) as defined in any one of claims 1 to 20, characterized in that it is a Gas-Gas heat exchanger, mainly for heat recovery purposes. 23. Use of shell and tube heat exchanger (1) as defined in any one of claims 1 to 20, characterized in that it is a gas-gas heat exchanger, mainly for heat recovery purposes. Gas-gas heat is employed in a process for the synthesis of sulfuric acid.

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