EP1650520A2 - Heat exchange apparatus - Google Patents

Abstract

The apparatus includes two heat exchangers (1,2) that are arranged in a row. The heat exchangers have multiple pipes, in particular flat pipes. Well ribs (10) have a partition area (20) in transverse sections that are adjacent to the gas flow-through direction (12) towards intermediate spaces (17, 18), where no clamps are provided in the partition area. A bond bridge is provided between two through holes of the well rib.

Description

The invention relates to a heat exchanger assembly, in particular for a motor vehicle, with at least two in the air flow and successively arranged in Luftdurchströmungsrichtung heat exchangers, each having a plurality of tubes, in particular flat tubes, which are flowed through by a medium and leaving interstices to each other are aligned so that the heat exchangers common, extending along the tubes corrugated fins comprise each having a plurality of gills, which are bordered to the tubes by two continuous webs, respectively in the transverse to the air flow direction of the interstices adjacent sections at least have a pair of opposed through holes.

Such a heat exchanger assembly is known from German patent application DE 198 08 202 A1. In the known heat exchanger arrangement gills are provided in the transverse to the direction of air flow through the gaps adjacent sections between the webs, which serve to form turbulence and thus for improved heat transfer.

The object of the invention is to provide a heat exchanger arrangement, in particular for a motor vehicle, with at least two heat exchangers through which air flows and in the air flow direction one after the other. each having a plurality of tubes, in particular flat tubes, which are flowed through by a medium and are arranged in alignment with one another leaving gaps between them, so that the heat exchangers comprise common corrugated ribs extending along the tubes, each having a multiplicity of gills, which are bordered to the tubes by two respective continuous webs, which have at least one pair of opposite through holes in the transverse to the air flow direction adjacent to the interstices sections, which has a higher efficiency than conventional heat exchanger assemblies.

The object is in a heat exchanger assembly, in particular for a motor vehicle, with at least two in the operation of air flowed through and in Luftdurchströmungsrichtung successively arranged heat exchangers, each having a plurality of tubes, in particular flat tubes, which are flowed through by a medium and leaving gaps aligned with each other so that the heat exchangers comprise common, along the tubes extending corrugated fins, each having a plurality of gills, which are bordered to the tubes by two continuous webs, in the transverse to the direction of air flow through the spaces adjacent sections each having at least one pair of opposing through holes, achieved in that the corrugated fins in the transverse to the direction of air flow through the interstices adjacent sections between the webs have a separation region in which k a gills are provided. The through holes provide thermal separation between the tubes associated with different heat exchangers. By omitting the gills in the separation area, the pressure loss caused by the gills can be reduced. In addition, the stability of the corrugated fin is increased by the separation area without gills. The separation region may extend in the air flow direction over the entire length or only over a part of the sections adjacent to the interstices.

European Patent EP 0 431 917 B1 discloses a unified duplex heat exchanger having a first and a second heat exchanger unit. The two heat exchanger units operate at different temperatures and are equipped with common, corrugated cooling fins. The corrugated fins have at their middle portions in the width direction one or more slots for intercepting the heat conduction between the two heat exchanger units. The slots are configured to split the corrugated fins partially and alternately from one edge and from the other edge in opposite directions of the fin height. In the heat exchanger arrangement known from EP 0 431 917 B1, slots are formed between the webs instead of the gills in the sections adjacent to the spaces transverse to the air flow direction. A combination of the known from European Patent EP 0 413 917 B1 slots between the webs with the known from German Patent Application DE 198 08 202 A1 through holes in the webs would lead to a transection or at least to an unacceptable weakening of the corrugated fin.

A preferred embodiment of the heat exchanger assembly is characterized in that a bridge is formed between two through holes of a pair in the corrugated fin. The deliberate omission of gills and / or slots between two opposite through holes ensures adequate stability of the corrugated fins.

A further preferred embodiment of the heat exchanger arrangement is characterized in that gills are formed adjacent to the bridge in the corrugated fin. Preferably, gills are formed on both sides of the bridge. But it can also be formed only on one side in the immediate vicinity of the bridge gills.

A further preferred embodiment of the heat exchanger arrangement is characterized in that a pair of through holes at the ends of two opposite, a heat exchanger associated Pipes is arranged. Preferably, the through-holes are arranged in the ribbed arcs of the corrugated fins.

A further preferred exemplary embodiment of the heat exchanger arrangement is characterized in that slits are formed in the separating region and extend between two webs perpendicular to the webs. As a result, additional thermal separation points are created at low pressure loss. The slots are sized and arranged so that the corrugated fin is not weakened too much.

Another preferred embodiment of the heat exchanger assembly is characterized in that each one half of the gills of a corrugated fin are directed in a different direction than the other half of the gills of the corrugated fin. This avoids distortion of the corrugated fins during production.

Another preferred embodiment of the heat exchanger assembly is characterized in that the corrugated fins are each formed in one piece. This simplifies the manufacture and assembly of the heat exchanger assembly.

Figur 1

die Ansicht eines Querschnitts durch eine erfindungsgemäße Wärmetauscheranordnung mit einer zwischen vier Rohren angeordneten Wellrippe;

Figur 2

die Ansicht eines Längsschnitts durch die Wellrippe aus Figur 1 gemäß einem ersten Ausführungsbeispiel;

Figur 3

die gleiche Schnittansicht wie in Figur 2 gemäß einem weiteren Ausführungsbeispiel;

Figur 4

eine ähnliche Wärmetauscheranordnung wie in Figur 1 gemäß einem weiteren Ausführungsbeispiel;

Figur 5

eine ähnliche Wärmetauscheranordnung wie in Figur 1 mit zusätzlichen Schlitzen im Trennbereich;

Figur 6

eine ähnliche Wärmetauscheranordnung wie in Figur 1 mit vier Durchgangslöchern in den Stegen;

Figur 7

eine ähnliche Wärmetauscheranordnung wie in Figur 6 gemäß einem weiteren Ausführungsbeispiel;

Figuren 8 bis 11

jeweils die Ansicht eines Längsschnitts durch eine Wellrippe gemäß vier verschiedenen Ausführungsbeispielen;

Figur 12

eine schematische Darstellung eines Querschnitts durch eine Wärmetauscheranordnung und

Figur 13

verschiedene Schnittansichten von Einzelheiten aus Figur 12 gemäß weiteren Ausführungsbeispielen.

Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, various embodiments are described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination. Show it:

FIG. 1

the view of a cross section through a heat exchanger assembly according to the invention with a arranged between four tubes corrugated fin;

FIG. 2

the view of a longitudinal section through the corrugated fin of Figure 1 according to a first embodiment;

FIG. 3

the same sectional view as in Figure 2 according to another embodiment;

FIG. 4

a similar heat exchanger assembly as in Figure 1 according to another embodiment;

FIG. 5

a similar heat exchanger assembly as in Figure 1 with additional slots in the separation area;

FIG. 6

a similar heat exchanger assembly as in Figure 1 with four through-holes in the webs;

FIG. 7

a similar heat exchanger assembly as in Figure 6 according to another embodiment;

FIGS. 8 to 11

in each case the view of a longitudinal section through a corrugated fin according to four different embodiments;

FIG. 12

a schematic representation of a cross section through a heat exchanger assembly and

FIG. 13

various sectional views of details of Figure 12 according to further embodiments.

The heat exchanger arrangement according to the invention is also referred to as a monoblock. In the monobloc, two heat exchangers, for example a coolant cooler and a condenser, are integrated with a common, continuous outer rib in one unit. According to the present invention, the area between the two heat exchangers is not covered completely or not at all. The partially introduced Bekiemung can be varied. Ideally, to avoid distortion of the corrugated fin during manufacture, the change in gill orientation is positioned so that there are approximately equal numbers of gills in each direction.

In Figure 1, a heat exchanger assembly according to the invention is shown in section, comprising a first heat exchanger 1 and a second heat exchanger 2 in the first heat exchanger 1 is a capacitor. The first heat exchanger 1 comprises a plurality of flat tubes 4, 5, of which only two are shown in FIG. The second heat exchanger 2 comprises a plurality of flat tubes 7, 8, of which only two are shown in FIG. The tubes 4, 5; 7, 8 of the two heat exchangers 1; 2 open at their ends in each case (not shown) collection boxes. For reasons of strength, the tubes 4, 5; 7, 8 designed as multi-chamber profiles.

The tubes 4, 5; 7, 8 of the two heat exchangers 1; 2 are arranged in pairs opposite each other. Between the tubes 4, 5 of the first heat exchanger 1 and between the tubes 7, 8 of the second heat exchanger 2 extends a one-piece, continuous corrugated fin 10 which is connected to the tubes 4, 5; 7, 8 is connected to a unit. The corrugated fin 10 comprises a multiplicity of substantially plate-shaped sections 11, which are connected to one another in a zigzag shape and of which only one plate-shaped section 11 can be seen in the view shown in FIG. The corrugated fin 10 is traversed by air in the direction of an arrow 12, which is also referred to as Luftdurchströmungsrichtung. To form turbulence, the plate-shaped section 11 is provided with attached sections 14, 15, 16.

In the air flow direction 12, a gap 17 is provided between the tube 4 of the first heat exchanger 1 and the tube 7 of the second heat exchanger 2. In the same way, a gap 18 is provided between the tube 5 of the first heat exchanger 1 and the tube 8 of the second heat exchanger 2. The corrugated fin 10 has in the plate-shaped portion 11 between the interstices 17 and 18 on a separation region 20 which is unmarked, so having no gills. The unknown separation area 20 is arranged between the covered portion 14, which is provided between the tubes 4, 5 of the first heat exchanger 1, and the tight area 15, which is located between the tubes 7, 8 of the second heat exchanger 2 is provided. The bekiemte section 16 is also disposed between the tubes 7, 8 of the second heat exchanger 2. Between the bekiemten sections 15 and 16, a small unmarked portion 24 is formed, which is the center of the corrugated fin extension in the air flow direction 12.

The bekiemten sections 14, 15, 16 and the separation region 20 and the central region 24 are to the tubes 4; 7 and the tubes 5; 8 out of continuous webs 28, 29 edged. The webs 28, 29 extend parallel to each other in the air flow direction 12. In the air flow direction 12 at the end of bekiemten section 14, a through hole 31, 32 is formed in the webs 28, 29 respectively. The through hole 31, 32 is disposed in the immediate vicinity of the end of the cross section of the pipe 4, 5 of the first heat exchanger 1. Through the through holes 31, 32, the heat conduction between the tubes 4, 5 of the first heat exchanger 1 and the tubes 7, 8 of the second heat exchanger 2 is limited to the material of the corrugated fin 10 between the through holes 31, 32 and the bekiemten section 14.

In the sectional view of the corrugated fin 10 shown in Figure 2 it can be seen that the gills of the bekiemten sections 14 and 15 are aligned in the same direction. The gills of the bekiemten section 16 are offset by 90 ° aligned.

FIG. 3 shows an embodiment of a corrugated fin 10, in which the covered sections 15 and 16 of FIGS. 1 and 2 are combined in a covered section 35 whose gills are all aligned in the same direction.

In Figures 4 to 7 are similar Wärmetauschchsranordnungen as shown in Figure 1 The same reference numerals are used to designate the same parts. To avoid repetition, reference is made to the preceding description of FIG. In the following, only the differences between the individual embodiments will be discussed.

In the embodiment shown in Figure 1, the separation area extends almost over the entire extent of the intermediate spaces 17, 18 in Luftdurchströmungsrichtung 12. In the embodiment shown in Figure 4, the separation region 20 is slightly smaller, since the bekiemten sections 14 and 15 in the transversely to the air flow direction 12 the intermediate spaces 17, 18 extend into adjacent section. Moreover, in the exemplary embodiment illustrated in FIG. 4, two through-holes 41, 42 are arranged centrally in relation to the separating region 20.

In the embodiment shown in Figure 5, the separation region 20 is not formed continuously, but provided with slots 45 to 48. The slots 45 to 48 extend transversely to the air flow direction 12 between the webs 28 and 29. Through the slots 45 to 48, the thermal separation between the heat exchangers 1 and 2 can be improved.

In the exemplary embodiment illustrated in FIG. 6, the attached section 15 extends into the section between the intermediate spaces 17 and 18, so that the separation area 20 is smaller than in the exemplary embodiment illustrated in FIG. In addition, two further through-holes 61, 62 are provided in addition to the through-holes 31, 32 at the ends facing the separation region of the bekiemten portion 15 in the webs 28, 29.

In the exemplary embodiment illustrated in FIG. 7, two additional gills 65, 66 are arranged between the intermediate spaces 17, 18, following the end of the attached portion 15 facing the separation region 20. The additional gills 65, 66 are slightly flattened or aligned than in the gill sections 15 and 16.

The sectional views shown in FIGS. 8 to 11 are similar to the sectional views shown in FIGS. 2 and 3. To designate the same parts, the same reference numerals are used. To repetitions too In the following, only the differences between the individual exemplary embodiments will be discussed.

In the embodiment shown in Figure 8, the separation region 20 is formed slightly smaller than in the embodiment shown in Figure 2. In the embodiment shown in Figure 9, the gill alignment changes after the separation region 20. In the embodiment shown in Figure 10, the gill alignment changes so that in each case the same number gills each direction is present. In the embodiment shown in Figure 11, in addition to the bekiemten section 10 a bekiemter section 70 is provided, the gills are aligned as well as in the bekiemten section 10. The bekiemte section 70 is arranged between two bekiemten sections 71, whose gills are oriented differently the gills in the bekiemten sections 10 and 70. The bekiemte section 71 is disposed between the separation region 20 and the bekiemten section 70.

In Figure 12, two heat exchangers 1 and 2 with tubes 4, 5; 7, 8 shown schematically in section. Between the pipes 4 and 5; 7 and 8 of the heat exchanger 1 and 2, a continuous corrugated fin 10 is arranged with a plate-shaped portion 11.

The heat exchanger 1 preferably has a tube width B ₁ of 8 to 20 mm. The heat exchanger 2 preferably has a tube width B ₂ of 12 to 50 mm. The distance A between the two nets is preferably 1 to 10 mm. This results in a total depth of the heat exchanger assembly from 21 to 80 mm. The rib height H of the corrugated fin 10 is preferably 5 to 12 mm. The tube height of the tubes 4, 5; 7, 8 h is preferably 1.0 to 2.5 mm.

FIG. 13 shows a corrugated rib 73 with two plate-shaped sections 74, 75. The two plate-shaped sections 74, 75 are connected to each other by a rib bow 77. In the region of the fin arch 77, for example, a through hole 84 is formed with a substantially rectangular cross-section. In the region of the rib bow 77 can but also a through hole 86 may be formed with an undefined cross section. At 78, it is indicated that slots 78 may be disposed in the separation area. At 79 and 80 circular openings 79 and 80 are indicated in two opposite ribbed arches. At 82 it is indicated that a perforation line 82 can also be formed in the separation area.

Claims (7)

Heat exchanger arrangement, in particular for a motor vehicle, having at least two heat exchangers (1, 2), which are flowed through by a gas, in particular air and in gas flow direction, and which each have a multiplicity of tubes (4, 5, 7, 8), in particular flat tubes, which are flowed through by a medium and are arranged in alignment with each other leaving gaps (17, 18) such that the heat exchangers (1, 2) comprise common corrugated fins (10) extending along the tubes, each of which has a plurality of Gills, which are bordered to the tubes by two respective continuous webs (28,29), in the transverse to the gas flow direction (12) the intermediate spaces (17,18) adjacent portions each have at least one pair of opposed through holes (31,32 ), characterized in that the corrugated fins (10) in the transverse to the gas flow direction (12) the spaces (17,18) adjacent portions between the webs (28,29) have a separation area (20) in which no gills are provided. Heat exchanger arrangement according to claim 1, characterized in that between two through holes (31,32; 41,42) of a pair in the corrugated fin (10), a bridge is formed. Heat exchanger arrangement according to one of the preceding claims, characterized in that gills are formed adjacent to the bridge in the corrugated fin (10). Heat exchanger arrangement according to one of the preceding claims, characterized in that a pair of through holes (31,32) at the ends of two opposite, a heat exchanger (1) associated with tubes (4,5) is arranged. Heat exchanger arrangement according to one of the preceding claims, characterized in that in the separation region (20) slots (45-48) are formed, which extend between the webs (28,29) perpendicular to these. Heat exchanger assembly according to one of the preceding claims, characterized in that in each case about one half of the gills of a corrugated fin (10) are directed in a different direction than the other half of the gills. Heat exchanger arrangement according to one of the preceding claims, characterized in that the corrugated fins (10) are each formed in one piece.

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