Heat Exchanger

Abstract

A heat exchanger (1), particularly for motor vehicles, comprises flat tubes (2) whose interior can be flowed through by first fluids and whose exterior can be subjected to the action of a second fluid. The flat tubes (2) are situated essentially transversal to the flowing direction of the second fluid while being parallel to one another and are interspaced in such a manner as to form flow paths for the second fluid that pass through the heat exchanger (1). Cooling ribs (3) extending between adjacent flat tubes (2) are situated in the flow paths. A number of corrugated ribs are provided, which are located one behind the other in the flowing direction of the second fluid and which are offset with regard to one another in the flowing direction of the first fluid.

Description

The invention relates to a heat exchanger, especially one for motor vehicles, having the features of the preamble to claim 1.

Such a heat exchanger may be designed, for example, as an integrated heat exchanger having a condenser of an air-conditioning system and a coolant radiator for motor vehicles. The heat exchanger usually has a number of flat tubes arranged side by side and running parallel to one another in a plurality of rows. First fluids, in the above example a refrigerant and a coolant, flow in these rows of flat tubes. The flat tubes are connected to manifolds or collecting pipes and exposed to the flow of a second fluid, for example ambient air, in order to produce a transfer of heat between the fluids. Flow paths for the second fluid are formed between the spaced individual flat tubes.

In order to improve the heat transfer between the fluids, cooling fins are arranged between the flat tubes and fixed to the latter. In the heat exchanger disclosed by DE 198 13 989 A1, the surfaces of the cooling areas are fundamentally situated transversely to the direction of flow of the second fluid. This means that there is a flow resistance to the second fluid. Designing the cooling fins to obstruct the flow is purposely intended to reduce the rate of flow of the second fluid. This, on the one hand, increases the time which the second fluid spends flowing through the heat exchanger, that is to say the time in which the second fluid can absorb heat from a first fluid or transmit heat to this. On the other hand, however, the low rate of flow of the second fluid limits the amount of heat transferable between the first and the second fluid, that is to say the efficiency of the heat exchanger.

A further heat exchanger with cooling fins is disclosed, for example, by U.S. Pat. No. 4,676,304. In this heat exchanger the cooling fins lie fundamentally parallel to the direction of flow of the second fluid (in this case, air). Despite the formation of baffle louvers on the individual cooling fins, it is nevertheless impossible to prevent some of the second fluid that flows through the heat exchanger from flowing between adjacent cooling fins without absorbing significant amounts of energy from these or giving off energy to these fins. This problem is particularly important when the heat exchanger has small dimensions in the direction of flow of the second fluid. In this case a high mass flow of the second fluid does not necessarily result in a high heat transfer coefficient. Only a relative small proportion of the available temperature difference between the first and second fluid is utilized.

With integrated heat exchangers, the problem often arises that heat passes from one individual heat exchanger to the other via a common corrugated fin, i.e. via integrally formed corrugated fins of the individual heat exchangers. To reduce this undesirable heat transfer, it has been proposed, for example in EP 0 773 419 A2, to provide the integrated corrugated fin of a heat exchanger of this type with slots in a region between the two individual heat exchangers. However, this has the drawback that the air is swirled up in the region of the slot, thereby increasing the flow resistance and therefore the pressure drop for the air.

The object of the invention is to specify a heat exchanger of the type mentioned in the introduction having cooling fins which are designed to promote flow and which at the same time reduce thermal coupling between a plurality of first fluids.

According to the invention, this object is achieved by a heat exchanger having the features of claim 1. Here the heat exchanger has flat tubes through which first fluids can flow and which can be externally exposed to a second fluid, and which are arranged fundamentally parallel to one another and transversely to the direction of flow of the second fluid, in such a way that flow paths for the second fluid are formed, in which cooling fins are arranged, which in each case extend between adjacent flat tubes. The cooling fins here take the form of corrugated fins, multiple corrugated fins being arranged in series in the direction of flow of the second fluid and laterally offset in relation to one another, that is offset in the direction of flow of the first fluids. Successively offsetting the corrugated fins means that a very high proportion of the second fluid flowing through the heat exchanger is used for heat transfer. In the case of corrugated fins with gills, a greater overall mass flow of the second fluid may possibly flow through gills that are arranged in the area of that side of a fin on the downstream side for the second fluid than is the case without an offset between the corrugated fins. This may give rise to an increased heat transfer coefficient in this area. In addition, this has an influence on a thermal boundary layer, which may form at a tube wall, so that any heat transfer from the tube wall to the second fluid or vice-versa may be increased. The offset arrangement of the corrugated fins simultaneously reduces undesirable heat transfer between different rows of tubes via the corrugated fins, even though the fins are formed from one common strip. This in turn has manufacturing technology advantages, since a plurality of corrugated fins which are arranged in series and are formed from a common strip, i.e. as a single piece, can easily be inserted between the rows of tubes of the heat exchanger. The corrugated fins, including the gills, can be produced in particular by rolling from a metal strip.

A flow-enhancing design for the corrugated fins is preferably achieved in that their surfaces lie fundamentally parallel to the direction of flow of the second fluid, that is to say the normals to the surfaces of the corrugated fins fundamentally enclose a right angle with the direction of flow of the second fluid. This flow-enhancing design of the corrugated fins notwithstanding, the lateral offsetting of corrugated fins arranged in series ensures that only a smaller proportion of the second fluid flows between the flat tubes unused, that is to say without significant heat transfer, than is the case without such an offset. This advantage is all the more manifest the greater the spacing b between two fins. Two or three similarly shaped corrugated fins are preferably successively offset in relation to one another. In order to ensure a high heat transfer coefficient, the individual corrugated fins are preferably arranged directly adjoining one another, that is to say without any spacing in the direction of flow of the second fluid. This gives a large heat exchanger surface. Alternatively, a spaced arrangement of in this case narrower corrugated fins may be provided in order to reduce the flow resistance.

According to a preferred development, the corrugated fins have gills to direct the second fluid. A so-called swelling flow developing at the gills, which has a high temperature gradient in one area of the corrugated fin, ensures a better heat transfer between the second fluid and the corrugated fins.

All gills of a corrugated fin section enclosed between two flat tubes are preferably angled in the same direction in relation to the direction of flow of the second fluid. A uniform angling of the gills within a fin section has the advantage that, where necessary, the flow can thereby be purposely directed towards a downstream fin section.

The gills of successively offset fin sections are preferably angled in opposite directions, so as to define a longer flow path for the second fluid flowing through the heat exchanger. The gills of two adjacent gilled panels may also be angled in the same direction, it then possibly being advantageous for the gills of a gilled panel arranged upstream or downstream of the two adjacent gilled panels to be angled in the opposite direction to the gills of the two adjacent gilled panels.

A uniform coverage of the flow cross-section through which the second fluid passes is preferably achieved in that successively offset fin sections run parallel to one another. In this case the offset fin sections are preferably perpendicular to the flat tubes. If the fin surfaces deviate somewhat (up to approximately 6 degrees) from parallel, these surfaces in the context of the invention still being regarded as substantially parallel, this has scarcely any adverse effect on the thermodynamic advantages of the offset fins. The use of so-called V-fins or fins with any degree of rounding is equally feasible. The fin geometry according to the invention can be used, in particular, in motor vehicle heat exchangers such as radiators, heating elements, condensers and evaporators.

According to an advantageous development of the invention a gill depth LP in the range from 0.7 to 3 mm at a gill angle of 20 to 30 degrees improves efficiency, because this increases the flow angle, that is to say the deflection of the second fluid from one channel into the adjacent channel, in turn producing a longer flow path for the second fluid. The fin height for such a system advantageously lies in the range from 4 to 12 mm. The fin density for this system advantageously lies in the range from 40 to 85 fins/dm, corresponding to a fin interval or fin spacing of 1.18 to 2.5 mm.

Examples of embodiments of the invention will be explained in more detail below with reference to a drawing, in which:

FIG. 1a, b shows a heat exchanger having two successively offset corrugated fins as cooling fins between each two adjacent flat tubes in a row of tubes,

FIG. 2a, b shows a heat exchanger having three successively offset corrugated fins as cooling fins between each two adjacent flat tubes in a row of tubes,

FIG. 3 shows two corrugated fins formed from a single strip,

FIG. 4 shows three corrugated fins formed from a single strip,

FIG. 5a shows a cross-section of a corrugated fin without offset having two gilled panels,

FIG. 5b shows a cross-section of a corrugated fin without offset having two gilled panels,

FIG. 5c shows a cross-section of a corrugated fin from one strip having 2 rows,

FIG. 5d shows a cross-section of a corrugated fin from one strip having 3 rows,

FIG. 5e shows a cross-section of a corrugated fin from one strip having 4 rows,

FIG. 5f shows a cross-section of a corrugated fin from one strip having 5 rows,

FIG. 5g shows a cross-section of a corrugated fin from one strip having 5 rows,

FIG. 5h shows a cross-section of a corrugated fin from one strip having 5 rows,

FIG. 5i shows a cross-section of a corrugated fin from one strip having 3 rows,

FIG. 5j shows a cross-section of a corrugated fin from one strip having 3 rows,

FIG. 5k shows a cross-section of a corrugated fin from one strip having 3 rows,

FIG. 5l shows a cross-section of a corrugated fin from one strip having 5 rows,

FIG. 6 shows a snapshot of a simulated air flow through corrugated fins without offset,

FIG. 7 shows a snapshot of a simulated air flow through corrugated fins with offset,

FIG. 8 shows a graph plotting an air mass flow flowing through a louvered opening as a proportion of a total air mass flow against the depth of the tubes for a low air flow rate,

FIG. 9 shows a graph plotting an air mass flow flowing through a louvered opening as a proportion of a total air mass flow against the depth of the tubes for a high air flow rate,

FIG. 10a, b show a heat exchanger having two corrugated fins arranged offset in series as cooling fins between in each case two adjacent flat tubes of two rows of tubes, and

FIG. 11a, b show a heat exchanger with three corregated fins arranged offset in series, as cooling fins between in each case two adjacent flat tubes of two rows of tubes.

Corresponding parts are provided with the same reference numerals in all figures.

FIGS. 1a, 1b and 2a, 2b show sections from a heat exchanger 1 with flat tubes 2 which are arranged parallel to one another and through which a first fluid FL1a flows in a first direction of flow S1. The flat tubes 2 are fitted with flow baffle elements 2a and are connected to manifolds or collecting pipes (not shown). The fluid FL1a is a coolant, for example, or a refrigerant condensing in the heat exchanger 1.

Two (FIG. 1a, 1b) or three (FIG. 2a, 2b) corrugated fins 3 are arranged as cooling fins between each two adjacent flat tubes 2. Embodiments with a greater number of corrugated fins 3 are also feasible. The corrugated fins 3 are bent in a square-wave shape from a sheet, a fin section 4a adjoining a flat tube 2 in each case alternating with a fin section 4b connecting two adjacent flat tubes 2. The fin sections 4a adjoining the flat tubes 2 are connected to the flat tubes 2 by a heat-conducting method, in particular by brazing. The fin sections 4b connecting two adjacent flat tubes 2 are perpendicular to the flat tubes 2 and form flow paths for a second fluid FL2, for example air, which flows through the heat exchanger 1 in the direction of flow S2. The second fluid FL2 flows largely parallel to the surface 5 of the corrugated fins 3, that is to say as it flows into the heat exchanger 1 the second fluid FL2 is initially only incident upon the narrow end faces 6 of the corrugated fins 3. The second fluid FL2 can thereby flow through the heat exchanger 1 at high speed and with a correspondingly high mass flow.

Gills 7, which extend transversely to the direction of flow S2 of the second Fluid FL2 and transversely to the direction of flow S1 of the first fluid FL1 are formed out of the fin sections 4b, as can be seen in particular from FIGS. 3, 4. The gills 7 within a fin section 4b on the one hand produce an especially good heat transfer between the second fluid FL2 and this fin section 4b, and on the other purposely direct the second fluid FL2 to the fin section 4b arranged obliquely behind in the direction of flow S2. In this way virtually full use is made of the mass flow of the second fluid FL2 passing through the heat exchanger 1, efficiently exploiting the temperature difference between the first fluid FL1a and the second fluid FL2 for the transfer of heat.

Two corrugated fins 3 arranged in series between two flat tubes 2 are offset in relation to one another by half the width b between two adjacent fin sections 4b. In the case of three corrugated fins 3 arranged in series, as shown in FIGS. 2 and 4, an offset of b/3 may also be selected for preference, other offset values also being feasible.

Two or three adjacent corrugated fins 3, which extend over the depth T of the heat exchanger 1, are produced by rolling from one sheet 8. In rolling, the sheet 8 is cut in the area of the respective offset between the two (FIG. 1a, 1b, FIG. 3) or three (FIG. 2a, 2b, FIG. 4) corrugated fins 3 and the gills 7 are cut into the corrugated fins 3. A single (FIG. 1a, 1b, FIG. 3, FIG. 5c) or double (FIG. 2a, 2b, FIG. 4, FIG. 5d) offset or offset of a higher order (FIG. 5e, 5f, 5g) of the corrugated fins 3 can alternatively be produced by arranging similar, separate corrugated fins 3 with an offset of between 0.1 mm and b/2, b being the distance between two adjacent flat tubes 2.

The fin sections 4a of the corrugated fins 3 adjoining the flat tubes 2 do not have any gills. In this area therefore a laminar flow of the fluid FL2 tends to form more readily than in the fin sections 4b that are provided with gills 7 and which connect the adjacent flat tubes 2. Over a longer distance the laminar flow may lead to the formation of a boundary layer with falling temperature gradient at the flat tube 2. This effect is limited to an insignificant amount in that the flow of the second fluid FL2 forming between two adjacent fin sections 4b of a corrugated fin 3 is already disrupted even after the short distance T/2 (FIG. 1a, 1b, FIG. 3, FIG. 5c) or T/4 (FIG. 2a, 2b, FIG. 4, FIG. 5d) by the succeeding corrugated fin 3 in the direction of flow S2, so that an increase in the temperature gradient is generated, which causes an increase in the heat transfer. In this way a highly efficient heat transfer is achieved between the second fluid FL2 and the first fluid FL1a even in a heat exchanger 1 with a low depth T of 12 to 20 mm, for example.

FIG. 5 shows cross-sections of corrugated fins 10a, b . . . l each with multiple gilled panels. In cooling fins of prior art with baffle louvers (gills) in the individual fins, a fin between two tubes in the main direction of flow of the second fluid usually lies solely in one plane without offset (FIG. 5a, 5b). These cooling fins have at least two so-called gilled panels 11, 12, and 13, 14 respectively, which are separated from one another by a web of varying design. The baffle louvers (gills) of adjacent gilled panels are in this case usually aligned in opposite directions.

According to the present invention two, three or even more similarly shaped corrugated fins (cooling fins) are preferably successively offset in relation to one another, that is to say the one corrugated fin with baffle louvers (gills) may be offset in multiple planes. At the same time the number of corrugated fins which are arranged in series, viewed in the direction of flow of the second fluid, may be chosen as a function of the depth of the heat exchanger and/or the depth of the corrugated fins. For example, 2, 3 or more rows may be used for an overall depth of 12 to 18 mm, 2, 3, 4 or more rows for an overall depth of up to 24 mm, 2, 3, 4, 5 or more rows for an overall depth of up to 30 mm, 2, 3, 4, 5, 6 or more rows for an overall depth of up to 36 mm, 2, 3, 4, 5, 6, 7 or more rows for an overall depth of up to 42 mm, 2, 3, 4, 5, 6, 7, 8 or more rows for an overall depth of up to 48 mm, 2, 3, 4, 5, 6 7, 8, 9 or more rows for an overall depth of up to 54 mm, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more rows for an overall depth of up to 60 mm, and 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or more rows for an overall depth of up to 66 mm.

FIG. 5c shows a cross-sectional view of an example of an embodiment for 2 rows 15 and 16.

FIG. 5d shows a cross-sectional view of an example of an embodiment for 3 rows 17, 18 and 19.

FIG. 5e shows a cross-sectional view of an example of an embodiment for 4 rows 20, 21, 22 and 23.

FIG. 5f shows a cross-sectional view of an example of an embodiment for 5 rows 24, 25, 26, 27 and 28.

FIG. 5g shows a cross-sectional view of an example of an embodiment for 5 rows 29, 30, 31, 32, and 33.

FIG. 5h shows a cross-sectional view of an example of an embodiment for 5 rows 34, 35, 36, 37 and 38.

More than two offset rows can preferably be distributed on a total of two planes offset in relation to one another, as in the embodiments in FIGS. 5d, 5e and 5g. However, they can also be distributed on three or more different planes as in the embodiments in FIGS. 5f and 5h, the intervals between each two respective planes being either identical or different.

Alternatively, just the area 41 or 44 between two gilled panels 39, 40 and 42, 43 lying in one plane can be offset in relation to the gilled panels 39, 30 and 42, 43 (FIGS. 5i and 5j). In the area 41 or 44 the corrugated fin 10i and 10j respectively has no gills. This development, too, has an influence on the thermal boundary layer at the tube walls and/or improves the flow through the louvers.

The gilled panels 45, 46, 47 of the corrugated fin 10k may also be of different sizes (FIG. 5k). In this case, by way of example, it is advantageous to assign the gilled panels 45, 46 to a first row of tubes and the gilled panel 47 to a second row of tubes, since the offset 49 between the gilled panels 46 and 47 prevents a thermal connection between the rows of tubes.

A combination of differently sized gilled panels 65, 66, 67, 68, 69 in different planes is also possible, as for the corrugated fin 101 (FIG. 5l).

The number of gills per row is between 2 and 30 gills, for example, depending on the number of rows and the depth of the heat exchanger. For production engineering reasons the number of gills per gill panel is preferably not identical in the case of an odd number of rows, that is 3, 5, 7, 9, or 11 rows. With an even number of rows, the number of gills per gilled panel may be identical, although this is not essential.

A simulation of an air flow through a heat exchanger having three different corrugated fin configurations is explained below (FIG. 6 to 9).

The simulation is performed under the following conditions: tube temperature=60°; air inlet temperature=45° C.; air density=1.097 kg/m³; air inlet velocity vL=1 and 3 m/s, fin height=8 mm, fin depth=16 mm. The simulation is partly based on a consideration of one corrugated fin in a row, that is without offset, consisting of a row with two gilled panels separated from one another by a roof-shaped web (prior art). In addition, one corrugated fin with 2 rows and one corrugated fin with 3 rows are considered. In addition to the air-side pressure drop, the simulation also determines the mass flow through the individual louvered openings and the radiated output from the tube to the cooling air.

FIG. 6 shows the flow field of the air at an air inlet velocity v_Luft of 3 m/s into a heat exchanger 51 having corrugated fins 52, 53 under the aforementioned boundary conditions in the area between two gilled panels 54, 55 and 56, 57 respectively. The webs 58 and 59 between each two gilled panels are in this case roof-shaped. The arrows 60 indicate the main flow path of the air particles, which flow through the last louvered opening 61 in front of the web 59, then experience a flow deflection before flowing through the louvered openings 62 and 63 in the adjacent gilled panel 57. It can be seen from the figure that it is not until the second louvered opening 62 of the gilled panel 57 that a higher number of air particles again flows through, and that it is only through the third louvered opening 63 that the velocity field again starts to approximate to the velocity pattern in the previous gilled panel 56.

FIG. 7 shows the flow field of the air at an air inlet velocity v_Luft of 3 m/s into a heat exchanger 71 having corrugated fins 72, 73 under the aforementioned boundary conditions in the area of an offset 74 and 75, in each case between two gilled panels 76, 77 and 78, 79 respectively. The arrows 80 indicate the main flow path of the air particles in front of the offset 75, firstly through the last louvered opening 81 in front of the offset and secondly through the offset opening 75. After flowing through the offset opening 75, the air particles experience a flow deflection, the air particles that flow through the offset opening then flowing primarily through first and second louvered opening 82, 83 of the adjacent gilled panel 79. After likewise experiencing a flow deflection, the air particles which flow through the last louvered opening 81 in front of the offset flow primarily through the third louvered opening 84 of the following gilled penal 79.

FIGS. 8 and 9 show a graph of the ratio of the mass flow m_Kieme through the respective gilled opening (louvered opening) to half the total mass flow ½ m_ges of the air as fluid FL2 for the three different corrugated fin configurations at an air flow velocity of V_Luft=1 m/s (FIG. 8) and V_Luft=3 m/s (FIG. 9) under the boundary conditions described above, plotted against the depth of the tubes and the depth of the heat exchanger respectively, The percentage mass flow through the opening at the offset is not shown.

As can be seen from FIG. 8, the percentage air mass flow in the two corrugated fin configurations with two or three rows (one or two offsets) is always in excess of 9%, whereas in the case of corrugated fins in one plane/row the air mass flow in the two louvered openings adjoining the web area drops to less than 8% with a minimum of about 4%. Whilst the air mass flow in the case of the corrugated fin comprising one plane drops from approximately 12% to about 10% in the louvered opening in front of the web area, in the case of the corrugated fin comprising two planes/rows the mass flow through the last louvered opening in front of the offset here increases from approximately 12 to about 13%. This is again here followed after the offset by a re-orientation of the air flow and the first louvered opening is exposed only to a partial air mass flow of approximately 10%. In the case of the corrugated fin comprising three rows the mass flow through the last louvered opening in front of the offset likewise increases to approximately 13%. This is again here followed after the offsets by a re-orientation of the air flow and the first louvered opening is in each case exposed only to a partial air mass flow of approximately 10-11%.

As can be seen from FIG. 9, the percentage air mass flow in the two corrugated fin configurations with two or three rows (one or two offsets) is always in excess of 12%, whereas in the case of corrugated fins in one plane/row the air mass flow in the two louvered openings adjoining the web area drops to less than 11% with a minimum of about 4.5%. Whilst the air mass flow in the case of the corrugated fin comprising one plane drops from approximately 16.5% to about 15% in the louvered opening in front of the web area, in the case of the corrugated fin comprising two planes/rows the mass flow through the last louvered opening in front of the offset here increases from approximately 16.5 to about 18%. This is again here followed after the offset by a re-orientation of the air flow and the first louvered opening is exposed only to a partial air mass flow of approximately 14%. In the case of the corrugated fin comprising three rows the mass flow through the last louvered opening in front of the offset likewise increases to approximately 18-19%. This is again here followed after the offsets by a re-orientation of the air flow and the first louvered opening is in each case exposed only to a partial air mass flow of approximately 14%.

FIGS. 10a,b and 11a,b in each case show excerpts from a heat exchanger 1 with flat tubes 2 which are arranged parallel to one another in two rows la,b and have first fluids FL1a,b flowing through them in a first direction of flow S1. Flow in the opposite direction is also conceivable. The flat tubes 2 are connected to manifolds or collecting pipes (not shown). The fluids FL1a,b are, for example, a cooling liquid and a refrigerant which condenses in the heat exchanger 1. There may equally be two identical fluids within a heat exchanger 1 comprising two or more rows.

Two (FIG. 10a,b) or three (FIG. 11a,b) corrugated fins 3 are arranged as cooling fins between two respectively adjacent flat tubes 2. Embodiments with a greater number of corrugated fins 3 can likewise be implemented. The corrugated fins 3 are bent in meandering form from a metal sheet, with a fin section 4a which bears against one flat tube 2 in each case alternating with a fin section 4b which connects two adjacent flat tubes 2. The fin sections 4a which bear against the flat tubes 2 are connected to the flat tubes 2 in a heat-conducting manner, in particular by brazing. The fin sections 4b connecting two adjacent flat tubes 2 are perpendicular to the flat tubes 2 and form flow paths for a second fluid FL2, for example air, which flows through the heat exchanger 1 in the direction of flow S2. The second fluid FL2 flows largely parallel to the surface of the corrugated fins 3, that is to say as it flows into the heat exchanger 1 the second fluid FL2 is initially only incident upon the narrow end faces 6 of the corrugated fins 3. The second fluid FL2 can thereby flow through the heat exchanger 1 at high speed and with a correspondingly high mass flow.

Gills 7, which extend transversely to the direction of flow S2 of the second fluid FL2 and transversely to the direction of flow S1 of the first fluid FL1a,b are formed out of the fin sections 4b. The gills 7 within a fin section 4b on the one hand produce an especially good heat transfer between the second fluid FL2 and this fin section 4b, and on the other purposely direct the second fluid FL2 to the fin section 4b arranged obliquely behind in the direction of flow S2. In this way virtually full use is made of the mass flow of the second fluid FL2 passing through the heat exchanger 1, efficiently exploiting the temperature difference between the first fluids FL1a,b and the second fluid FL2 for the transfer of heat.

Two corrugated fins 3 arranged in series between two flat tubes 2 are offset in relation to one another. These offset, integrally formed corrugated fins are produced, for example, as explained in connection with FIG. 1a,b.

In the intermediate region 9 between the flat-tube rows 1a,b illustrated on a larger scale in FIG. 10b, 11b, the corrugated fins 3 are offset with respect to one another. On account of the integral formation, the corrugated fins 3 of different tube rows are connected to one another via narrow webs 9a in the region of the fin sections 4a bearing against the flat tubes 2. Since these webs 9a form the only heat-conducting connection between the tube rows 1a,b, heat transfer from one row of tubes to the other is effectively suppressed.

Claims

1. A heat exchanger, especially for motor vehicles, having flat tubes through which first fluids can flow and which can be externally exposed to a second fluid and which are arranged fundamentally parallel to one another and transversely to the direction of flow of the second fluid in at least two rows, each first fluid being assigned at least one row of tubes, with the flat tubes in a row of tubes being spaced apart forming flow paths for the second fluid passing through the heat exchanger, cooling fins being arranged in the flow paths, which in each case extend between adjacent flat tubes, wherein multiple corrugated fins, which are arranged in series in the direction of flow of the second fluid and laterally offset in relation to one another, are provided as cooling fins and in that multiple corrugated fins arranged in series are formed from a common strip.

2. The heat exchanger as claimed in claim 1, wherein the surfaces of the corrugated fins are arranged fundamentally parallel to the direction of flow of the second fluid.

3. The heat exchanger as claimed in claim 1, wherein multiple offset corrugated fins (3) are similarly shaped.

4. The heat exchanger as claimed in claim 1, wherein at least one of the corrugated fins (3) has gills (7) for directing the second fluid (FL2).

5. The heat exchanger as claimed in claim 4, wherein all gills of a fin section bounded by two flat tubes are angled in the same direction relative to the direction of flow of the second fluid.

6. The heat exchanger as claimed in claim 5, wherein the gills of two successively offset fin sections are angled in the same direction.

7. The heat exchanger as claimed in claim 5, wherein the gills of two successively offset fin sections are angled in opposite directions.

8. The heat exchanger as claimed in claim 1, wherein two successively offset fin sections are fundamentally parallel to one another.

9. The heat exchanger as claimed in claim 8, wherein the fin sections e are arranged fundamentally perpendicular to the flat tubes.

10. The heat exchanger as claimed in claim 1, wherein the corrugated fins (3) extend for an equal or similar distance in the main direction of flow of the second fluid.

11. The heat exchanger as claimed in claim 1, wherein different rows of tubes have different fluids flowing through them.

12. The heat exchanger as claimed in claim 1, wherein one fluid flows through different rows of tubes.