EP1992898B1 - Heat exchanger for gaseous media - Google Patents

Abstract

The heat exchanger has a stack of first flow channels (5) extending in a first direction (3), second flow channels between them extending in a second direction (4) and inner and outer distance holders parallel to the first and second directions. It has corrugated profiles with lens-shaped nubs in flat sections and walls welded together in gas -tight manner to form a block (1) with the first and second flow channels.

Description

The invention relates to a heat exchanger of the type specified in the preamble of claim 1.

Known heat exchangers of this type are preferably used as condensers in tumble dryers (eg. EP 0 982 427 B1 . EP 1 106 729 B1 . DE 102 18 274 A1 . DE 103 56 417 A1 ). They are mainly characterized by the fact that the flow channels are limited by walls made of highly thermally conductive plastic or metal foils and z. B. by vacuum thermoforming, thermoforming or otherwise brought into their final form. A benefit obtained thereby is that the walls can be easily and in one piece provided with profiles that improve the heat exchange performance, as well as with spacers that keep the relatively flexible walls at a distance.

From the US 2,462,421 a heat exchanger is known, the individual superimposed planes of flow channels, which are welded together both at their side edges and on wavy profiles in the interior of the heat exchanger spacers welded together.

However, the previously known heat exchangers of this type are not free from defects.

Due to the thin-walled, z. B. 0.2 mm thick walls or films arise in spite of the known Proflierungen and spacers in particular problems with regard to the required compressive strength during operation of the heat exchanger. Higher temperatures can be mainly used for cost reasons, made of polypropylene or a copolymer such. B. ABS walls are soft with the result that they deform in the direction of the smallest pressure. In addition, high temperatures result in elongations resulting in distortions of the walls between their fixedly fixed in the frame ends. As a result, the structurally predetermined flow cross sections change during operation, which not only has an unfavorable influence on the performance of the heat exchangers, but also, in the case of tumble-dryer condensers, the formation of depressions in the process air Can cause flow channels. In these wells, condensed water can accumulate in an undesired manner (puddling), which affects the condensation performance and should actually drain into a collecting container provided for this purpose.

Not desired are still the relatively high production costs, the u. a. caused by the cumbersome, gas-tight fastening of the individual tubular flow channels in the frame by gluing.

Finally, although good heat exchange performance can be achieved even with heat exchangers made of plastic films of the type mentioned, but these are still lower than with appropriately sized, soldered, glued or folded coolers od. Like. Metal.

Based on this prior art, the present invention seeks to provide the heat exchanger of the type described above in such a way that they have increased performance and greater compressive strength despite reduction of manufacturing costs.

This problem is solved by the characterizing features of claim 1.

Due to the fact that according to the invention the profilings are additionally provided with knobs known per se, a noticeable increase in performance also occurs when walls made of film material are used. The inventive design and arrangement of the spacers allows the use of a sufficiently large number of spacers, without thereby increasing the pressure losses during operation excessively. Finally, a significant cost reduction is made possible by not only the first flow channels at their lateral edges, but also the second flow channels are connected at their front and rear end faces by welding. This results in a coherent block which can be used as a whole in the frames, which only has to be connected to the frame at its periphery by gluing. This leads to the saving of glue and laborious steps in the production.

Further advantageous features of the invention will become apparent from the dependent claims.

• Fig. 1 eine perspektivische Ansicht eines Wärmeaustauschers;
• Fig. 2 eine perspektivische Ansicht eines erfindungsgemäßen, ersten Strömungskanals, bestehend aus zwei an ihren Längsseiten verbundenen Wänden;
• Fig. 3 und 4 in je einem Schnitt längs der Linie III - III der Fig. 2 je eine obere und untere, einen ersten Strömungskanal begrenzende Wand;
• Fig. 5 die Wände nach Fig. 3 und 4 in einem Schnitt längs der Linie III - III der Fig. 2, jedoch in einem Zustand, in dem die beiden Wände fest miteinander verbunden sind;
• Fig. 6 in einer perspektivischen, vom geschnittenen Vorderansicht mehrere übereinander angeordnete, erfindungsgemäß ausgebildete, erste und zweite Strömungskanäle;
• Fig. 7 eine perspektivische Ansicht eines erfindungsgemäß ausgebildeten Blocks des Wärmeaustauschers nach Fig. 1; und
• Fig. 8 eine der Fig. 6 entsprechende Ansicht eines zweiten Ausführungsbeispiels der erfindungsgemäßen Strömungskanäle.

The invention will be explained in more detail below in connection with the accompanying drawings of an embodiment. Show it:

• Fig. 1 a perspective view of a heat exchanger;
• Fig. 2 a perspective view of a first flow channel according to the invention, consisting of two connected at their longitudinal sides walls;
• 3 and 4 in each case a section along the line III - III of Fig. 2 a respective upper and lower, a first flow channel limiting wall;
• Fig. 5 the walls after 3 and 4 in a section along the line III - III of Fig. 2 but in a state in which the two walls are firmly joined together;
• Fig. 6 in a perspective, from the cut front view a plurality of superimposed, according to the invention formed, the first and second flow channels;
• Fig. 7 a perspective view of an inventively designed block of the heat exchanger according to Fig. 1 ; and
• Fig. 8 one of the Fig. 6 corresponding view of a second embodiment of the flow channels according to the invention.

To Fig. 1 a heat exchanger comprises a block 1 provided with first and second flow channels, which is fastened to two longitudinal ends in a respective frame 2. The first flow channels are in a first, indicated by arrows 3 direction, the second flow channels, however, in a second, indicated by arrows 4 direction, which is preferably perpendicular to the first direction in the manner of a cross-flow heat exchanger, flows through each of a gas.

In the preferred exemplary embodiment described below, a heat exchanger suitable in particular as a condenser for a tumble dryer is described, through which the process air flows in the direction of the arrows 3 and the cooling air flows through in the direction of the arrows 4.

Fig. 2 shows a inventively designed, first flow channel 5, of two accordingly 3 and 4 trained walls 6 and 7 is limited, as in particular also from Fig. 5 is apparent. Fig. 6 shows a plurality of superimposed, first flow channels 5, which are arranged at preselected intervals and therefore form between them second flow channels 8, which according to FIG Fig. 1 in the direction of the arrows 4 z. B. are flowed through by cooling air.

The first flow channels 5 limiting, alternately superimposed plates or walls 6 and 7 are made of a film material, for. For example, a polypropylene or aluminum foil, prepared and have a useful consistently constant wall thickness, which is preferably 0.2 mm to 0.5 mm. In the plan view, the walls 6 and 7 have a substantially rectangular shape. The two walls 6 and 7 have, in particular Fig. 3 to 5 can recognize, parallel to the first direction and in the exemplary embodiment also parallel to their longitudinal sides extended side strips 6a and 7a, which are connected in a gas-tight manner by welding ( Fig. 5 ). This creates flow channels 5 in the form of laterally closed, open at their front and rear ends of pipes.

The first flow channels 5 are further provided with inner, ie inwardly projecting spacers 9 which are connected to the in Fig. 4 . 5 and 6 bottom walls 7 are formed, substantially perpendicularly rise from these and rest with their free ends to the overlying upper walls 6. Thereby, the walls 6 and 7 of the flow channels 5 are kept at a preselected distance. In addition, the in Fig. 3 . 5 and 6 overhead walls 6 are provided with outer spacers 10. These do not protrude into the first flow channels 5, but stand from their walls 6 substantially perpendicular to the outside. In the stacked Condition of walls 6 and 7 ( Fig. 6 ) lie the free ends of these outer spacers 10 on the undersides of the overlying walls 7 and therefore set the distances between the stacked flow channels 5 and the heights of the second flow channels 8 located between them.

Continue to show above all 3 and 4 in that the walls 6 and 7 are transverse to the first flow direction (arrows 3 in FIG Fig. 2 ) extended, wavy profiles have, which are formed substantially identical in both walls 6 and 7 and arranged parallel to each other.

Heat exchangers of the type described are essentially known from the publications mentioned above and therefore need not be explained in more detail to the person skilled in the art.

Profiles 11 are provided with at least partially planar sections according to the invention. Trapezoidal profilings 11 which are in accordance with cross section are particularly advantageous Fig. 2 to 4 in the second direction (arrows 4 in FIG Fig. 2 to 4 and 6 ) rising portions 11a, sloping portions 11b and these connecting portions 11c have. The profiles 11 have according to Fig. 5 Wavelengths 1 and heights h, which are preferably in a ratio 1 / h to each other, which is at least five, and preferably less than twenty.

The sections 11a, 11b are particularly flat while the sections 11c are preferably flat and parallel to the second direction. In addition, the sections 11a, 11b and 11c according to the invention are provided with preferably lenticular nubs 12, which lead to increased heat exchange performance and in particular lead to no significant increase in pressure losses, especially in the second direction for the cooling air when its depth is approximately between 0.2 and 0.8 times the distance between the upper and lower walls 6 and 7 is. The other dimensions and also the shapes of the nubs 12 are dependent on the performance increases desired in the individual case or to accept the maximum purchase losses to be accepted. In particular, instead of lenticular knobs, it is also possible to provide those with oval or angular bases as well as diamond-shaped or pyramid-shaped or otherwise suitably shaped studs 12.

The nubs 12 can, in particular 3 and 4 show, are formed by forms that protrude from opposite broad sides of the walls 6, 7, therefore optionally in the first or in the second flow channels 5 and 8 protrude and lead on their backs to corresponding recesses. If the heat exchangers are arranged in use such that the walls 6 each form an upper boundary and the walls 7 respectively form a lower boundary of the flow channels 5, then in the case of tumble-dryer condensers, the lower walls 7 are to face the flow channels 5 Inner sides only with raised projecting, in the flow channels 5 projecting nubs to provide. This avoids that on these inner sides of the walls 7, ie at the bottoms of the flow channels 5 depressions are present, which lead to the formation of puddles when condensing water from the process air and impede the desired flow of condensate. Such puddles, in which condensate accumulates instead of draining, are undesirable because of the deteriorated heat transfer at these locations. On the upper walls, on the other hand, inwardly projecting nubs are less critical, as forming condensate can drip off of them.

From Fig. 2 to 6 apparent spacers 9 and 10 are preferably elongate and flat oval or biconvex in plan view. They extend with their longitudinal axes expedient in the first flow channels 5 parallel to the first direction and in the second flow channels 8 parallel to the second direction. In particular, the leading edges of the spacers 9, 10 are preferably provided with small radii of curvature, which has favorable flow conditions and small pressure losses result.

It is also particularly advantageous if the number of spacers 9 and 10 remains within certain limits. If the number of spacers is too large, on the one hand the pressure losses increase, while on the other hand the area remaining for the attachment of the studs 12 is reduced. On the other hand, if the number of spacers is too low, then there is a risk that the walls 6, 7 will be deformed too much during operation because of the then prevailing pressure conditions due to the natural flexibility of the film material, as they will buckle and thus also lead to pressure losses. In the context of the present invention, it has been found that the number of spacers 9, 10 should not be less than four pieces per 100 cm ² wall area with a uniform distribution, wherein under such a wall surface preferably a substantially square area piece of approximately 10 cm. 10 cm is understood. In this case, the surface areas located between two support points are so small that the deformations still possible there are largely harmless. The upper limit for the number of spacers 9, 10 per 100 cm ² or preferably 10 cm × 10 cm wall surface largely depends on which pressure losses are tolerable. The cross-sectional areas of the spacers 9, 10 should also be as small as possible, in particular transversely to the respective flow direction. Since they contribute to the heat exchange little or nothing, it is sufficient if they are just so large that the spacers 9, 10 by the coming to use manufacturing processes such. B. thermoforming just be produced with the required stability. In addition, the spacers 9, 10 should come to lie alternately one above the other in the finished stack, so that from top to bottom continuous, preferably perpendicular to the two directions 3 and 4 extending support lines are obtained, as can be seen in particular Fig. 6 results. If the spacers 9 and 10 are arranged with an arbitrary lateral offset relative to one another, then there is a risk that pressure differences occurring during operation lead to moments, in particular in the area of individual support points, which could result in undesired deformations of the walls 6 and 7.

Further, it is considered advantageous for the purposes of the invention if the Walls 6 and 7 are arranged over the entire surface substantially parallel to each other and thus the flow channels 5 and 8 have a constant height, except of course, where the spacers 9, 10 arranged, provided in opposite directions nubs 12 and the walls , 7 are connected at their edges. As a result, almost uniform flow conditions are achieved throughout.

As wavy profilings 11 to achieve a good compressive strength has from Fig. 2 to 6 apparent trapezoidal shape with the preferably equally long, rising and falling sections 11a, 11b proved to be expedient. These have, inter alia, the advantage that the nubs 12 can be mounted in flat wall areas. However, it is recommended that the connection zones of the different regions 11a, 11b and 11c be slightly curved in order to obtain favorable flow conditions on the cooling air side, ie in the second flow channels 8, by rounded deflection zones. Alternatively, however, other, z. B. sinusoidal or zigzag waveforms applicable. Important in this context is a waveform that brings a high compressive strength without causing excessive pressure loss. To increase the performance of such waveforms contribute only slightly, which is why the nubs 12 are additionally provided according to the invention.

In particular Fig. 5 and 6 show, the two walls 6 and 7, each forming one of the first flow channels 5, each connected at their lateral edges firmly together. To make this possible, the trapezoidal walls 6 (see also Fig. 3 ) are provided at their sides with obliquely downwardly and outwardly curved or angled transition regions 6b, to which the side strips 6a adjoin outwardly. The walls 7, however, are provided at their edges with obliquely upwardly and outwardly curved or angled transition sections 7b, to which the side strips 7a connect. Both side strips 6a, 7a are preferably arranged substantially flat and both parallel to one another and parallel to imaginary center planes of the walls 6, 7. This preserves the walls 6, 7 a cup-shaped appearance, wherein in the embodiment, the walls 6, the ceilings and the walls 7, the bottoms of the flow channels 5 form. The position of the transition sections 6b, 7b is selected such that the walls 6, 7 automatically have the spacing also predetermined by the spacers 9 when the side strips 6a, 7a are placed one on top of the other.

Next, the invention provides, the walls 6, 7 also at their front and rear end faces by welding gas-tightly connected to each other, thereby sealing the second flow channels 8 laterally. In particular Fig. 2 and 7 For this purpose, the walls 6, 7 are provided at their front and rear ends with connecting strips 6c, 7c which, like the side strips 6a, 7a, are arranged substantially both parallel to each other and parallel to the imaginary center planes of the walls 6, 7 , Like the side strips 6a, 7a, the connecting strips 6c, 7c are also connected to the walls 6, 7 by means of short transition sections arranged at an angle to the middle planes. However, these non-illustrated transition sections are curved or angled in the opposite direction in each case compared to the attached to the same walls 6, 7 side strips 6a, 7a, ie, for example in the in Fig. 2 and 5 upper wall 6 upwards and at the in Fig. 2 and 5 bottom wall 7 down. Therefore, two flow channels 5, consisting of two walls 6 and 7, respectively Fig. 6 and 7 superimposed, then these two flow channels 5 are kept not only by the appropriately sized spacers 10, but also to form the lateral flow channels 8 through the coming to rest connection strips 6c, 7c at a distance. After the welding of the connecting strips 6c, 7c of all the flow channels 5 present in the stack, a coherent heat exchanger block 1 (FIG. Fig. 1 ), in which the first and second flow channels 5, 8 are already gas-tight and firmly connected to one another at their sides parallel to the respective flow directions 3, 4. For the completion of a heat exchanger, in particular a capacitor od. Like., It is then only necessary, the two end, provided with the connecting strips 6c, 7c ends of the block 1 according to Fig. 1 in the according to the outer circumference of the block 1 sized Insert frame 2 and connect with them by gluing.

A further advantage of the construction described is that the side and connecting strips 6a, 7a and 6c, 7c are connected to the walls 6, 7 by means of the additional transition sections 6b, 7b and therefore project beyond the actual flow channels 5, 8 , Thus, the side and connecting strips 6a, 7a and 6c, 7c for the welding tools are easily accessible, and there are no internal holders od. Like. Needed to perform the welding safely. This applies regardless of whether only the walls 6, 7 of the individual flow channels 5 laterally welded and the latter then stacked and welded to the front sides or conversely only all the walls 6, 7 stacked and then welded laterally and frontally.

Due to the described construction, the walls 6 and 7, which may also be referred to as plates or shells, not identical and arranged only rotated by 180 °. They differ rather by the position and direction of their side and connecting strips 6a, 6c and 7a and 7c, their spacers 9 and 10 and possibly their nubs 12th

Above and below the flow channels 5 are advantageously side parts 14 ( Fig. 1 ) arranged from a thick-walled, mechanically stable material. These preferably form at least with the end-side walls 6 a further flow channel 8 by resting on the spacers 10. On the opposite side, however, the side parts 14, for example, lie directly against the undersides of the walls 7. The front ends of the side parts 14 also project into the frame 2 and are firmly connected with these. As a result, the side parts 14 on the one hand serve the purpose of supporting the two frames 2 against each other and thereby relieving the stack formed by the walls 6, 7 of any occurring assembly and sealing forces. On the other hand, the side parts 14 serve to clamp the stack lying between them perpendicular to the directions 3 and 4 and thereby hold the spacers 9, 10 with the associated walls 6, 7 in abutment.

The example also a clothes dryer condenser illustrative embodiment Fig. 8 is different from that Fig. 2 to 7 especially in that the process air flows through the second flow channels 8 and the cooling air flows through the first flow channels 5 secured in the frame 2, as through the opposite Fig. 6 reversed arrows 3 and 4 is indicated. Therefore, the profilings 11 in this case are preferably extended in the direction of the first flow channels 5. Moreover, unlike Fig. 2 to 6 each of the inner spacers 9 and the outer spacers 10 is formed continuously, ie, over the entire length or at least approximately over the entire length of the first and second flow channels 5 and 8, respectively. Therefore, to achieve sufficient stability, not the number of spacers themselves, but the number of their crossing points should have a certain minimum value. The crossing points in this case are those areas (or rather their centers) at which the spacers 9, 10, which are perpendicular to each other and lie in different planes, intersect each other. It has proved to be expedient to provide at least four such crossing points per 100 cm ² or preferably per 10 cm × 10 cm wall surface. The location and arrangement of the remaining parts is opposite Fig. 2 to 7 unchanged.

Finally, in the case of Fig. 8 be expedient to embody the protruding into the flow channels 8 nubs 12 in the manner raised, as above with reference to 3 and 4 is explained in detail.

The invention is not limited to the described embodiment, which can be modified in many ways. This applies, as already mentioned, in particular for the waveform of the profilings 11 used in the individual case. Preference is given in particular to those waveforms which have the same wavelengths 1 throughout and in which the ascending and descending sections 11a, 11b are substantially the same length. Also, the size of the radii in the connecting zones between the sections 11a, 11b, 11c, and preferably also in the connecting zones between the transition sections 6b, 7b and the adjacent Wall parts or side and connecting strips 6a, 7a and 6c, 7c are provided, can be selected depending on the individual case. In addition, the spacers 9,10 other than the Fig. 6 and 8th have apparent lengths. Further, the heat exchangers described may be used for purposes other than those specified and gases other than air or steam. Depending on the purpose of use can also be contrary Fig. 1 the first flow channels 5 are shorter than the second flow channels 8. In addition, it is clear that the statements "above" and "below" with respect to the walls 6, 7 relate only to the described embodiment, in which the first flow channels 5 each bounded above by the walls 6 and below through the walls 7 while the reverse applies to the second flow channels 8. Instead, the heat exchanger can of course also z. B. in a slightly oblique position or in a rotated position by 90 ° are applied so that the flow channels 5 or 8 are arranged vertically. Finally, it is understood that the various features may be applied in combinations other than those described and illustrated.

Claims (15)

1. A heat exchanger for gaseous media, containing:

   a plurality of first flow channels (5) which extend in a first direction (3) and which are arranged in a stack and at a distance on top of one another, protrude with their ends into a respective holding frame (2) and form second flow channels (8) between themselves which extend in a second direction (4), with the first flow channels (5) being delimited by walls (6, 7) which are disposed above one another in an alternating fashion and consist of film material, and which are connected with each other in a gas-tight manner by welding by means of side strips (6a, 7a) arranged laterally and parallel to the first direction (3), and comprise undulating profile portions (11) and integrally attached inner spacers (9) protruding into the first flow channels (5) and outer spacers (10), which space the stacked first flow channels (5) from each other, with the walls (6, 7) comprising front and rear connecting strips (6c, 7c) which are arranged in parallel to the second direction, with the connecting strips (6c, 7c) of the walls (6, 7) of any first flow channel (5) respectively being connected in a gas-tight manner by welding with the connecting strips of the walls (6, 7) of a first flow channel (5) that are disposed above or below in the stack by forming a contiguous block (1) provided with the first and second flow channels (5, 8), and the spacers (9, 10) consists of elongated shaped portions, with the inner spacers (9) being arranged with their longitudinal axes parallel to the first direction (3) and the outer spacers (10) being arranged with their longitudinal axes parallel to the second direction (4),

   characterized in that undulating profiled portions (11) are provided with knobs (12) arranged at least partly in planar sections (11 a, 11 b, 11c), and that the walls (6) and (7) differ from one another by the position and the direction of their lateral and connecting strips (6a, 6c) and (7a and 7c) of their spacers (9) and (10), with the spacers (10) not protruding into the first flow channels (5), but protrude from their walls (6) substantially perpendicularly to the outside, and that the inner and outer spacers (9, 10) are arranged in such a way that they are situated above one another in the stack and form continuous supporting lines from top to bottom.
2. A heat exchanger according to claim 1, characterized in that the block (1) is fastened to the ends comprising the connecting strips (6c, 7c) by gluing in the frame (2).
3. A heat exchanger according to claim 1 or 2, characterized in that the profiled portions (11) are arranged in an undulating manner in the first or second direction.
4. A heat exchanger according to one of the claims 1 to 3, characterized in that the profiled portions (11) are arranged in a trapezoidal manner and the walls (6, 7) are arranged in parallel with respect to one another in such a way that the heights of the flow channels (5, 8) in the regions which are free from the spacers (9, 10) and knobs (12) are substantially continuously the same.
5. A heat exchanger according to one of the claims 1 to 4, characterized in that the profiled portions (1) have a length (I) measured in the second direction (4) and a height (h) measured perpendicularly to the walls (6, 7) and the ratio is 20 ≥ l/h ≥ 5.
6. A heat exchanger according to one of the claims 1 to 5, characterized in that the inner and outer spacers (9, 10) are distributed substantially evenly over the walls (6, 7) and at least four respective spacers (9, 10) are provided in surface sections of the walls of 100 cm², preferably square surface sections of 10 cm · 10 cm.
7. A heat exchanger according to one of the claims 1 to 6, characterized in that the walls (6, 7) have a thickness which is substantially constant at 0.1 mm to 0.5 mm.
8. A heat exchanger according to one of the claims 1 to 7, characterized in that the knobs (12) are arranged in an elevated and/or depressed manner in the walls (6, 7).
9. A heat exchanger according to claim 8, characterized in that the knobs (12) are provided with an elevated configuration at least on the walls (7) which in operation form a bottom boundary of the flow channels (5).
10. A heat exchanger according to claim 9, characterized in that the knobs (12) are elevated in walls (7) of the first flow channels (5) which are the bottom ones in operation, and are arranged in such a way that they protrude into the first flow channels (5).
11. A heat exchanger according to one of the claims 1 to 10, characterized in that the side strips (6a, 7a) and the connecting strips (6c, 7c) are provided in regions protruding outwardly beyond the flow channels (5, 8) and are connected to the walls (6, 7) by sections curved upwardly or downwardly.
12. A heat exchanger according to claim 11, characterized in that in each wall (6, 7) the sections leading to the side strips (6a, 7a) and the sections leading to the connecting strips (6c, 7c) are respectively curved towards opposite sides.
13. A heat exchanger according to one of the claims 1 to 12, characterized in that the side and connecting strips (6a, 7a and 6c, 7c) are arranged substantially parallel among each other.
14. A heat exchanger according to one of the claims 1 to 13, characterized in that the spacers (9, 10) extend approximately over the entire length of the associated flow channels (5, 8).
15. A heat exchanger according to claim 14, characterized in that in surface sections of the walls (6, 7) of 100 cm², preferably square surface sections of 10 cm · 10 cm, at least four respective crossing points are provided between the inner and outer spacers (9, 10).

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