EP0726441A2 - Laminated heat exchanger, more particularly heating radiator with profiled tube sections - Google Patents

Abstract

The profile tube components (2-4) comprises at least one fluid channel (13) and at least one side provided with ribs (12). The at least one fluid channel has a slot-type cross-section, the width of which amounts to a max. of 5 mm. The length of the slot-type cross-section is at least five times as long as its width. The profile tube components has a flat side of a structured surface. At least one side of the profile tube components provided with ribs has at least one slightly acute-angled end rib (14,15), which on the angle inner side has a convex surface (16,17), in order to be connectable via a slotted casing (18) with a further end rib.

Description

The invention relates to a sectional heat exchanger made of an extruded profile, in particular for space heaters with profile tubular members, the sectional tubular members having at least one fluid channel and at least one side provided with ribs.

With sectional heat exchangers of this type, the individual profiled tube members are arranged next to one another in register-like fashion and connected by end strips. This creates heating panels that are used both horizontally and vertically. The links each have at least one fluid channel in which the heat exchange fluid is guided with the better heat transfer. For radiators that are intended to heat room air, water or thermal oil, for example, is suitable as the heat exchange fluid. The fluid is fed to and discharged from the end of the individual profile tube members through a suitable distribution tube arrangement.

Sectional heat exchangers are fundamentally different from integrally manufactured plate radiators. The individual links of sectional heat exchangers make it possible, in contrast to plate heat exchangers, to arrange the individual heat exchange surfaces of a heat-conducting ribbing more efficiently, e.g. B. to form more appropriate sized convection shafts.

Profile tube members for sectional heat exchangers are usually used as extruded parts, for. B. made of aluminum or an aluminum alloy.

In the case of the customary profile tube members for sectional heat exchangers, a conduit tube for the heat exchange fluid is provided, which is provided in a rib arrangement which is considered to be optimal in each case with a web arrangement which enlarges the heat exchange surface and forms convection shafts. The ribs form a particularly large surface, since the heat transfer from the liquid to the heat exchanger material can be up to 25 times better than the heat transfer from the heat exchanger material to the ambient air with free convection flow. In addition, the aim should be that the pipes run as close as possible to the fins, since the heat conduction lengths in link profiles determine the mean heating surface temperature and are therefore a parameter for the heat output transferred.

Since, on the one hand, many, long webs are required for optimal heat transfer from the profile tube members to the air and, on the other hand, the heat conduction lengths should be as short as possible in order to achieve a high, medium heating surface temperature, it was proposed to use several fluid channels in one profile tube member. However, this has the disadvantage that this makes the distribution tube arrangement more complex and each fluid channel must be sealed individually against the distribution tube arrangement.

The invention is therefore based on the object of developing a sectional heat exchanger of the type described at the outset in such a way that the heat conduction lengths can be kept short for a given heat exchange surface.

This task is carried out in a generic. Link heat exchanger solved in that at least one fluid channel has an essentially slot-like cross section.

The slot-like cross-section increases the heat transfer area on the inner walls of the slot while the cross-sectional area remains the same.

However, since the heat transfer area in the slot is defined by the heat transfer area on the ribs, the cross-sectional area through which the slot flows can be reduced. As a result, the fluid content of the radiator can be kept low with the slot-like shape of the channel. This is a particular advantage, since the fluid content of a radiator increases the controllability of the radiator. A low fluid volume shortens the dead time when the setpoint changes in the room temperature and thus enables the mean heating surface temperature to be changed more quickly.

In addition, the slot-like channel has the advantage that the ribs of the profile tube members can be arranged closer to the fluid channel. As a result, the heat conduction lengths in the link profiles are kept short, with the result that the average heating surface temperature is not reduced too much by the thermal gradient within the link profile.

In addition, flat heating panels can be produced by the slot-like design of the fluid channels. This is advantageous since flat heating panels can be equipped with particularly narrow end profiles, which only minimally hinder free convection of the air when the profile tube members are arranged vertically. The dead zones on the upper or lower end profile are therefore particularly small. If the profile tube elements with low fins are arranged horizontally, flat heating panels have the advantage that the unilateral transverse flow against the fins and cavity walls does not lead to any noticeable loss in performance.

For the person skilled in the art, from the problem solved by the invention, that the channel cross-section does not necessarily have to be exactly one slot, but that, for example, a dumbbell-shaped or kidney-shaped cross-section or even a cross-section of several star-shaped slots also fulfills the task at hand.

For conventional space heaters, it has been found that a slot-like cross section with a width of up to 5 mm is quite sufficient and a favorable ratio of the length to the width of the slot-like cross section is achieved in that the length of the slot-shaped cross section is at least five times as long as its length Width is selected. By reducing the cross-sectional width and increasing the cross-sectional length, the heat transfer area to the profiled tube members can be increased while the fluid content of the radiator remains the same, and it also makes it easier to arrange more fins in the vicinity of the fluid channel.

It is optically and technically advantageous if the profiled tube members have an essentially flat side with a structured surface. A structure on an essentially flat side of the sectional heat exchanger increases the area required for the heat transfer and forces a swirling of the free convection flow, whereby the heat transfer is improved. In addition, special structures can save material while maintaining the strength values of the tubular sections and contribute to a more pleasing appearance of the sectional heat exchanger. For example, we refer to circular arc segments or trapezoidal grooves.

It is particularly advantageous if at least one side of the profiled tube member provided with ribs has at least one end rib arranged at a slightly acute angle has, which preferably has a convex surface on the inside of the angle, in order to be connectable to a further end rib via a slotted sleeve. If the profiled tubular members thus shaped with end ribs abutting one another are arranged in a slightly arcuate manner next to one another, a slotted sleeve can easily be pushed over the end ribs of two profiled tubular members in order to connect them to one another. The individual profile tube elements are firmly connected to one another by the subsequent alignment of the profile tube elements on a straight line and the clamping of the elements in the end profile strip. Another type of fastening the profile tube members to one another is therefore unnecessary. With this special type of fastening, the sleeves stretch by widening their inner diameter and they align the link profiles via the end rib shape through mutual contact.

It has proven to be particularly practical here if the end rib is chamfered at an angle of approximately 5 to 6 ° and the convex surface has a semicircle in cross section with a diameter of approximately 5 mm. Two adjacent tubular sections thus show a circle of approximately 5 mm in diameter with a free triangular segment of 10 to 12 ° and a bevel length of approximately 6 mm. Alignment, joining and cover elements can be attached to the end ribs that are not required for the mutual fastening of the profile tubular members.

The profile tube members can be held in end profile strips, at least one end of the fluid channel being sealed against the end profile with an O-ring seal inserted in the end profile strip. Commercially available O-ring seals, which are usually made to seal circular cross-sectional areas, are also suitable for slot-like ones Sealing cross-sectional areas when the seal is compressed into a slot. This pressure can be achieved by holding the O-ring seal in the end profile strip, advantageously in a milled slot. Such a cord-ring seal is advantageously round, but it can also have a U-shaped or rectangular cross-section, for example. The ratio of the cord-ring diameter to the cord diameter is important for holding the cord-ring seal in the intended concave longitudinal groove, since the cord-ring seal should advantageously only be held on the end profile strip by frictional adhesion.

It is also advantageous if the profile tube members are held in end profile strips, which are provided with profile webs, to which fittings and / or convectors can be fastened via clamping sleeves. Profile bars on end profile strips allow in conjunction with further profile webs on fittings and / or convectors are fastened by means of clamping sleeves which hold the webs together by widening their thigh slot. This type of fastening enables radiator parts made of different materials to be firmly connected to one another. This is particularly important when inserting and attaching convectors to heated panels. A suitable shape of the profile webs on the end profile strips and on the flange of the fitting to be fastened can make the sleeve guidance easier when the sleeve is pushed on.

In addition, at least two profiled tube members can be arranged opposite one another, ie two surfaces made of profiled tube members can also be parallel to each other. Such parallel heating panels can be mounted vertically or horizontally. By laying the fins of heating panels facing each other in parallel, sectional heat exchangers with smooth outer surfaces can be produced, which have different thicknesses depending on the fin height and the type of profile tube elements put together.

Built-in or add-on convectors can be arranged between the opposing profile tube members. These convectors increase the heating power and the profile tube elements serve at the same time to increase the heating power and as a heated cover for the convectors. It is advantageous to connect the profile pipe sections to the built-in or add-on convectors in the fluid guide, so that low contact temperatures occur on the heating panels serving as covers and to achieve a higher heating output compared to connecting all elements in parallel.

Due to the shape of the profile tubular members, at least one side of the sectional heat exchanger is designed with an essentially flat side. In order to also provide the other sides with a flat surface, either middle profiled tube link plates can be arranged opposite one another or in a closed form, or at least one side of the link heat exchanger can be covered with a tensioning strap. For this purpose, sheets can be attached to the end profile strips opposite the side cover as leaf springs, between which a tensioning strap can be hung.

A tensioning strap is understood to mean a thin stainless steel sheet or a fabric with end angles attached to it on both sides. The sheet thickness is preferably 0.035 to 0.1 mm. Such straps improve the look of the radiator, force the air flow and can be easily replaced. When rolled up, these tapes can also be transported and stored well.

The invention is explained in more detail below with the aid of schematic drawings in several exemplary embodiments.

Fig. 1

einen Schnitt durch einen Doppeltafelheizkörper mit eingesetzten Lamellenkonvektoren,

Fig. 2

einen Schnitt durch den Doppeltafelheizkörper gem. Fig. 1 längs der Linie II - II,

Fig. 3

einen Längsschnitt durch einen Doppeltafelheizkörper mit einem eingesetzten Doppellamellenkonvektor,

Fig. 4

einen Querschnitt durch einen Doppeltafelheizkörper nach Fig. 3,

Fig. 5

ein Schaltbild für den Strömungsverlaufs des Fluids in einem Heizkörper gem. den Fig. 3 und 4,

Fig. 6

einen Schnitt durch einen Verbindungsknotenpunkt,

Fig. 7

einen Schnitt durch die Armatur in Fig. 6 längs der Linie VII - VII,

Fig. 8

eine elastische Abstützung der Konvektoren,

Fig. 9

eine Draufsicht auf einen Doppeltafelheizkörper mit hohen Rippen,

Fig. 10

einen Schnitt durch eine Endprofilleiste mit eingesetztem Profilrohrglied,

Fig. 11

einen Querschnitt durch die Endprofilleiste gem. Fig. 10 längs der Linie XI - XI,

Fig. 12

eine Draufsicht auf einen Eintafelheizkörper mit angebautem Lamellenkonvektor,

Fig. 13

eine alternative Ausführungsform eines Strangpreßprofils mit beidseitig angeordneten Rippen,

Fig. 14

einen Schnitt durch einen Heizkörper mit einem Strangpreßprofil nach Fig. 13,

Fig. 15

eine Seitenansicht eines Heizkörpers mit Strangpreßprofilen nach Fig. 13 und

Fig. 16

schematisch verschiedene Heizkörpervarianten.

It shows:

Fig. 1

a section through a double panel radiator with inserted slat convectors,

Fig. 2

a section through the double panel radiator acc. 1 along the line II - II,

Fig. 3

a longitudinal section through a double panel radiator with an inserted double lamella convector,

Fig. 4

3 shows a cross section through a double panel heating element according to FIG. 3,

Fig. 5

a circuit diagram for the flow of the fluid in a radiator acc. 3 and 4,

Fig. 6

a section through a connection node,

Fig. 7

6 shows a section through the fitting in FIG. 6 along the line VII-VII,

Fig. 8

elastic support of the convectors,

Fig. 9

a plan view of a double panel radiator with high fins,

Fig. 10

a section through an end profile strip with inserted profile tube member,

Fig. 11

a cross section through the end profile bar acc. 10 along the line XI - XI,

Fig. 12

a plan view of a single panel radiator with attached lamella convector,

Fig. 13

an alternative embodiment of an extruded profile with ribs arranged on both sides,

Fig. 14

13 shows a section through a radiator with an extruded profile according to FIG. 13,

Fig. 15

a side view of a radiator with extruded profiles according to FIGS. 13 and

Fig. 16

schematically different radiator variants.

In Fig. 1, a double-panel radiator is shown as a sectional heat exchanger 1, which essentially consists of several profile tube members 2, 3, 4, end profile strips 5, 6, a fitting 7, which is used as a panel connector, and a cover profile 8. A lamella convector 9, which serves as a heating power amplifier, is arranged between the oppositely arranged, parallel panels made of a plurality of profile tube members 2, 3, 4.

The profile tube members 2, 3, 4 consist of a surface which is substantially flat on one side 10 and on its other side 11 has ribs 12 rising perpendicularly from the surface. The essentially flat side can be structured in various ways. As examples of this, trapezoidal grooves are drawn in FIG. 1 in the upper section of the profiled tube member 2, circular arc and in the lower region of the profiled tube member 2. The profile tube members are extruded profiles and the ribs on the side 11 of the surface extend in the extrusion direction evenly distributed over the surface. In the middle of the surface, a fluid channel 13 is provided in the extruded profile on the side 11 between the ribs 12. The fluid channel 13 has an oval cross section and runs parallel to the ribs 12, so that the flat side of the oval rests on the surface of the profile tube member. In the present exemplary embodiment, the width of the oval cross section is approximately 5 mm and its length is 33 mm.

The last rib 14, 15 on both sides of the profile tube member 2, 3, 4 is in each case slightly acute-angled, ie beveled at an angle of 5 to 6 ° to the side 11 of the profile tube member. On the inside of the angle, the end ribs 14, 15 have a convex surface 16, 17 which is formed by a semicircular elevation running in the direction of extrusion. This semicircle has preferably a diameter of 5 mm. The special design of the end ribs 14 and 15 makes it possible to connect a plurality of profiled tube members 2, 3 to one another by means of a slotted sleeve 18, which is in each case pushed over two end ribs. On the other hand, the rib 14 on the end side of the radiator can also be used to fasten a cover profile 8 with a clip 19 to the end rib 14.

The attachment of a profile tube member 4 to the end profile bar 5 is shown schematically in Fig. 2. The end profile strip 5 consists of a tubular part 20, on the sides of which two flanges 21 and 22 extend parallel to one another. One side 23 of the flange 21 partially covers the flat side 10 of the profile tube member 4 and the profile tube member 4 is inserted between this side 23 of the flange 21 and a projection 24 at the foot of the flange 22 and spot welded. The other side 25 of the flange 21 has ribs 26, 27 protruding at right angles in the flange 21, between which a cover plate 28 can be held.

The other flange 22 is used to attach a fitting 29 to the end profile bar 5, which is held on the end profile bar 5 by means of clamping sleeves 30, 31. The flange 22 is thickened in the pressing direction of the extruded profile end strip 5 in such a way that the clamping sleeves 30 and 31 are guided through the flange 22. Arrows 32, 33 show the fluid flow from the fitting 29 through the end profile bar 5 into the profile tube member 4 and in the opposite direction.

The profile tube members 2, 3, 4 are inserted into the receiving groove between the shoulder 24 and the flange side 23. Via the flange side 23 there is additionally a spot weld to the profile tube member 4. The clamping sleeves 30 and 31 for the attachment of the fitting 29 consist of a slit pipe section along the longitudinal axis, which is pressed over the flange 22 of the end profile strip 5 and a flange of the fitting 29. When pressed on, the slot of the sleeve widens and cuts into the flange of the valve to be assembled. In this way, different materials can be easily joined together.

Because of its relatively short ribs 12, the double panel heating element shown in FIGS. 1 and 2 can be used both in a vertical and in a horizontal position.

In Fig. 3, the double panel radiator is shown in longitudinal section. The panels each consist of four profile tube members 2, 3. These profile tube members are aligned via clamping sleeves 18 and held in end profile strips 5. The convector 9 is arranged between the sheets of profile tube members 2, 3, 4 and flows through the fluid in front of the profile tube members 2, 3, 4.

The fluid flows into the convector at the fluid inlet fitting 34 at "E". This fitting 34 is the solder receptacle for the uppermost convector tube and also forms a connection between the panels made of profiled tube members. The convector 9 is fastened to the end profile strips 5 via clamping sleeves without a fluid connection being established between the fluid inlet fitting and the end profile strip 5. The convector 9 is also fastened to the end strip profiles 5 by means of pipe elbow connectors 35 by means of expansion-compensating metal bands 36 with clamping sleeves. Via the fluid outlet fitting 37, the fluid passes in two partial flows via the end profile strips 5 into the opposite panels made of profile tube members 2, 3, 4. The Fluid outlet fitting 37 is the soldering receptacle for the lowermost convector tube and, moreover, a connector between the opposing profile tube link panels via clamping sleeves.

In Fig. 3, "E" denotes the entry of the fluid into the radiator and "Ü" the transition of the fluid from the convector to the heating panels, and "A" denotes the exit of the fluid from the radiator. "L" denotes a vent connection as an insert in a connection fitting and "S" denotes a plug for the fluid guidance in the end profile strip 5 as a potential isolator.

The connection of the convector 9 in front of the profile tube members 2, 3, 4 significantly improves the heating power and lowers the contact temperature on the essentially flat side 10 of the profile tube members.

Fig. 4 shows a section through the double panel radiator, in which the lamella convectors 9 between the panels of profile tube members 2, 3, 4 are clearly shown again. In addition, the fluid inlet fitting 34, the fluid outlet fitting from the convector 37, the vent fitting 38 and the fluid outlet fitting 39 from the radiator 1 can be seen.

In Fig. 5 the fluid flow in the double panel radiator is shown again. The fluid flows at E into the convector 9 and flows through it in a meandering shape from top to bottom to the outlet U, where the amount of fluid is divided and distributed into the opposite panels of profiled tube members. The profile tube members lying above the potential point Ü are flowed through in parallel by distributing the fluid in the end profile strip 5 with the stopper S. The end profile strip 5 opposite the entrance area collects the fluid and directs it through the two opposite lowest profile tube sections back to exit A.

The difference in fluid temperature between the entry potential E and the exit potential A is the temperature spread. It can be seen that the double convector 9 has a higher, average fluid temperature to the air temperature in the radiator (excess temperature) than the downstream heated plates made of profile tube members.

Fig. 6 shows the sealing of a profile tube member 2 on an end profile strip 5. Between the two flanges 21 and 22, an oval bead 40 is provided in the end profile strip 5, into which a cord-ring seal 41 fits exactly. The oval concave longitudinal groove 40 has rounded edges so that a commercially available O-ring seal can be easily pressed into the end profile strip 5 at the intended location and is held there by the tension created by the deformation of the seal 41. The profile tube members 2 are connected to the end profile strip 5 by spot welding.

Also at the connection point between the end profile strip 5 and a fitting 29, a seal 42 is provided, which is incorporated into the end piece of the fitting 29 and is pressed together by means of the clamping rings 30 and 31 when the fitting 29 is attached to the end profile strip 5.

Fig. 7 shows the flange of the fitting 29 with its square outline. This allows the position of the valve 29 to the end profile 5 in 90 ° steps to be changed. This ensures universal use of prefabricated fittings for different types of radiators.

8 shows the connection of a pipe bend connector 35 to the end profile strip via an expansion-compensating metal strip 36. The expansion-compensating metal band 36 is corrugated in a serpentine manner and carries the elbow connector 35 of the lamella convector 9 in a trough. The other side of the metal band 36 is fastened to the flange 22 of the end profile strip via a clamping sleeve 43. The waveform of the metal strip 36 ensures elastic support of the lamella convector 9 on the end profile strip 5, which can compensate for thermal changes in length between profile tube members and convectors, which are caused by different temperatures and materials.

As a further exemplary embodiment, FIG. 9 shows a double panel heating element 50 with high fins 51, which has no convector, but is otherwise constructed like the double panel heating element 1 with short fins. Profile tube sections with high fins considerably increase the heating surface for heat exchange. Accordingly, the fluid channel 13, on which the heat transfer of a fluid to the profile tube member takes place, must be enlarged. Profile tube sections with high fins are only suitable for vertical installation, since otherwise they form too large dead zones with little heat transfer between the fins. However, the ratio of heating power to the mass of the material used improves considerably. So that profile tube members with high ribs 51 can also be installed in the end profile strips 5 described, the ribs 51 in the end region of the profile tube members must be shortened. By the ratio of the circumference of a profile tube member to the circumference of the fluid channel 52 under 25 to 1 to keep, and to keep the heat flow paths in the profile short, two fluid channels 52 and 53 are provided per profile tube member 54 in the embodiment with the long ribs 51. This measure primarily reduces the temperature drop at the end of the fins 51.

10 and 11, the attachment of a profile tube member 54 with high ribs 51 to an end profile strip is shown via a seal 55 clamped in the end profile strip 5, which essentially corresponds to the type of attachment according to FIG. 6. However, it should be pointed out that in the case of profile tube members with high ribs 54, the ribs in the region of the end profile strip 5 and the fittings must be removed. A high rib is understood to be a rib with a rib height H in which the rib height relative to the mean rib thickness d _{m is} greater than 30 to 1.

FIG. 12 shows a plan view of a so-called single-panel heating element 60, which serves as a third exemplary embodiment. The panel heating element 60 consists essentially of a panel 61 made of profiled tubular members, two end profile strips 62 and 63, a lamella convector 64 and a tensioning band 67 held between two leaf springs 65 and 66. The end profile strips 62 and 63 hold at their ends between two webs 68 and 69 a leaf spring 66 which has a continuous bead 71 in the area of the clamping sleeve 70. The leaf springs 66 are installed in such a way that they are prestressed against the clamping sleeve in the direction of the arrows 72 and 73 and cover the radiators laterally. At the end of the leaf springs 66, a further bead 74 is formed, into which an angle bracket 75 of the tensioning band 67 can be hung. As a result, the tensioning band 67, which is fastened to the leaf springs 66 with the angle tabs 75, is stretched over the pretensioning of the leaf springs 65, 66. As a tightening strap, which can also be divided into strips, the finest sheet is the smallest thickness (0.035 to 0.1 mm) or textile tape material. These straps can also be used as a radiation shield. The tensioning straps can also be designed as decorative tensioning straps and, if they are not required, they can be rolled up and secured without problems.

An overview of exemplary embodiments of sectional heat exchangers with ribs arranged on one side is shown in FIG. 16. While a) shows a simple stringing together of a plurality of profile tube members in the form of a plate, this plate is connected in b) to one convector and in c) to two convectors. In d) two opposing panels of profile tube members are shown, between which, as shown under e) and f), either one or two convectors can be accommodated. Finally, g) shows a panel made of profiled tubular members with high fins and under h) a combination of a panel made of profiled tubular members with short fins and a panel made of profiled tubular members with high fins. Finally, i) shows two panels of profiled tubular members with high fins arranged opposite one another. These are just a few examples of combinations that can be put together from the universally applicable elements described above.

The extruded profile 80 in FIG. 13 is intended as a further variant. In this example, ribs 76 and 77 are arranged on both sides of a central axis. The resulting large heat transfer area also requires a larger heat transfer area in the fluid channel and therefore two fluid channels 78 and 79 are provided in profile on the central axis.

14, this profile 80 is shown installed between two end profile strips 81 and 82. For egg building, ribs 76 and 77 must be in the area of End profile strips are partially notched to enable attachment. The outer edges of the ribs are rounded and covered with a strip or cap 83.

The assembly of several profiles to form a radiator 84 is shown in FIG. 15. Heating fluid is supplied and discharged via the fitting 85, which is passed through the extruded profiles 80 via the end profile strips 81 and 82.

Claims (12)

Sectional heat exchanger (1) made of an extruded profile, in particular for space heaters with profile tube members (2, 3, 4), the profile tube members (2, 3, 4) having at least one fluid channel (13) and at least one side provided with ribs (12, 51) characterized in that at least one fluid channel (13, 52, 53) has an essentially slit-like cross section. Sectional heat exchanger according to claim 1, characterized in that the width of the slot-like cross-section is max. Is 5 mm. Sectional heat exchanger according to one of the preceding claims, characterized in that the length of the slot-like cross section is at least 5 times as long as its width. Sectional heat exchanger according to one of the preceding claims, characterized in that the profile tube sections (2, 3, 4) have an essentially flat side (10) of a structured surface. Sectional heat exchanger according to one of the preceding claims, characterized in that at least one side of the profiled tube member (2, 3, 4) provided with ribs (12) has at least one end rib (14, 15) which is arranged at a slightly acute angle and which has a convex surface on the inside of the angle ( 16, 17) in order to be connectable to a further end rib (14, 15) via a slotted sleeve (18). Sectional heat exchanger according to one of the preceding claims, characterized in that the end rib (14, 15) is chamfered at an angle of approximately 5 to 6 ° and the convex surface (16, 17) has a semicircular cross section with a diameter of approximately 5 mm . Link heat exchanger according to one of the preceding claims, characterized in that the profile tube members (3, 4) are held in end profile strips (5) and at least one end of the fluid channel (13, 52, 53) with a cord ring clamped in the end profile strip (5) -Seal is sealed against the end profile strip (5). Sectional heat exchanger according to claim 7, characterized in that the end profile strips (5) are provided with profile webs (22) to which fittings (29) and / or convectors (9) can be fastened via clamping sleeves (30, 31). Sectional heat exchanger according to one of the preceding claims, characterized in that at least two profile tube sections (2, 3, 4) are arranged opposite one another. Sectional heat exchanger according to claim 9, characterized in that built-in or add-on convectors are arranged between the profile tube members (2, 3, 4). Sectional heat exchanger according to claim 10, characterized in that the profile tube sections (2, 3, 4) are connected downstream of the built-in or add-on convectors in the fluid guide. Sectional heat exchanger according to one of the preceding claims, characterized in that at least one side of the sectional heat exchanger is covered with a tensioning band (67).

Images