JP2007505282A - Heat exchanger - Google Patents

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 present invention is a heat exchanger for automobiles in particular, and has a flat tube through which a first fluid can be circulated. The flat tube can be added to the outside with a second fluid, and the flat tube is a second fluid. At least two rows substantially transverse to each other and parallel to each other, at least one tube row is attached to each first fluid, the flat tubes of one tube row are spaced apart from each other, and The present invention relates to a heat exchanger in which a flow path penetrating a heat exchanger for two fluids is formed, and cooling fins respectively extending between adjacent flat tubes are arranged in the flow path.

  Such a heat exchanger can be configured as an integrated heat exchanger having, for example, a condenser and a refrigerant cooler of an automotive air conditioner. A heat exchanger typically has a number of flat tubes in multiple rows that are juxtaposed and extend parallel to each other. The first fluid, that is, the refrigerant and the coolant in the above example, flow in these flat tube rows. The flat tube is connected to a collecting conduit or collecting tube and is exposed to a flow of a second fluid, such as ambient air, to cause heat transfer between the fluids. A second fluid flow path is formed between the flat tubes spaced apart from each other.

  In order to improve heat transfer between fluids, cooling fins are disposed between the flat tubes and are fixed to the flat tubes. In the heat exchanger known from Patent Document 1, the surface of the cooling surface substantially crosses the flow direction of the second fluid. This counteracts flow resistance against the second fluid. By configuring the cooling fin as a flow obstruction, the flow velocity of the second fluid is appropriately reduced. Thereby, on the other hand, the residence time of the second fluid during circulation of the heat exchanger, that is, the time during which the second fluid can absorb or transfer heat from the first fluid is lengthened. On the other hand, however, the amount of heat that can be transferred between the first fluid and the second fluid, that is, the heat exchange performance is limited by the small flow rate of the second fluid.

  Another heat exchanger with cooling fins is known, for example, from US Pat. In this heat exchanger, the cooling fins are substantially parallel to the flow direction of the second fluid (here, air). However, despite the fact that the flow-inducing plates are configured on individual cooling fins, a part of the second fluid flowing through the heat exchanger is absorbed or released into the adjacent cooling fins by a significant amount of energy. It is impossible to exclude passing between them without doing. This problem is particularly serious when the heat exchanger has a small dimension in the flow direction of the second fluid. In that case, the high mass throughput of the second fluid does not necessarily result in high heat transfer performance. Only a relatively small portion of the available temperature difference between the first fluid and the second fluid is utilized.

A problem that often arises in integrated heat exchangers is that one individual heat exchanger can provide another individual heat exchanger through one common corrugated fin of the individual heat exchanger, i.e. through an integrally constructed corrugated fin. Heat is transferred to the exchanger. In order to reduce this undesired heat transfer, for example, US Pat. No. 6,057,077 proposes providing a groove in the integral corrugated fin of such a heat exchanger in the region between both individual heat exchangers. However, this has the disadvantage that the air is swirled in the region of the grooves, which increases the flow resistance and thus the pressure drop for the air.
German Patent Application Publication No. 19813989 US Pat. No. 4,676,304 European Patent Application No. 0773419

  It is an object of the present invention to provide a heat exchanger having cooling fins that are hydrodynamically shaped and that simultaneously reduce thermal coupling between a plurality of first fluids.

  According to the present invention, according to the present invention, a plurality of corrugated fins arranged in the front-rear direction in the flow direction of the second fluid are provided as cooling fins shifted in the lateral direction, and a plurality of corrugated fins arranged in the front-rear direction Is solved by a heat exchanger characterized in that it is formed from one common strip. In that case, the heat exchanger has a flat tube through which the first fluid can be circulated, and the flat tube can be added with the second fluid on the outside and arranged parallel to each other substantially across the flow direction of the second fluid. Thus, a flow path is configured for the second fluid, and the cooling fins disposed in the flow path are respectively extended between adjacent flat tubes. In that case, the cooling fins are configured as corrugated fins, and a plurality of corrugated fins are arranged in the front-rear direction in the flow direction of the second fluid, and are shifted from each other in the lateral direction, that is, in the flow direction of the first fluid. Due to the corrugated fins that are shifted back and forth, most of the second fluid flowing through the heat exchanger is utilized for heat transfer. In the corrugated fin having the casing, in some cases, the first core having a mass flow rate higher than that when there is no deviation between the corrugated fins in the casing disposed in the fin side region downstream of the second fluid. Two fluids flow. This in some cases results in increased heat exchange performance in this region. Furthermore, in some cases, the temperature boundary layer generated at the tube wall is affected, and in some circumstances heat transfer from the tube wall to the second fluid or vice versa is enhanced. Despite the fact that the fins are formed from one common strip, the undesired heat transfer between the various tube rows is reduced through the corrugated fins at the same time by staggering the wave fins. This is advantageous from a manufacturing engineering point of view. This is because a plurality of integral corrugated fins formed of one common strip and arranged in the front-rear direction can be easily fitted between the tube rows of the heat exchanger. The corrugated fins including the casing can be produced in particular from one metal strip by rolling.

BEST MODE FOR CARRYING OUT THE INVENTION

  The hydrodynamic shaping of the corrugated fin is preferably accomplished by having its surface substantially parallel to the flow direction of the second fluid, i.e. the surface normal of the corrugated fin being substantially perpendicular to the flow direction of the second fluid. Is done. Despite this hydrodynamic configuration of the corrugated fins, the corrugated fins that are shifted laterally back and forth leave only a fraction of the second fluid unused, i.e., without such misalignment, i.e. Passing between the flat tubes is ensured without undue heat transfer. This advantage becomes more prominent as the fin interval b between the two fins increases. Mainly two or three similarly shaped corrugated fins are arranged one behind the other while being offset from each other. In order to ensure high heat transfer performance, the individual corrugated fins are arranged mainly directly next to each other, i.e. without any spacing in the flow direction of the second fluid. This provides a large heat exchange surface. As an alternative to this, in order to reduce the flow resistance, a thinner corrugated fin can be arranged in this case.

  According to one preferred configuration, the corrugated fin has a housing for guiding the second fluid. The so-called starting flow generated in the enclosure has a high temperature gradient in the area of the corrugated fins, ensuring improved heat transfer between the second fluid and the corrugated fins.

  All the fins in the fin area confined between two flat tubes of one corrugated fin are preferably tilted in the same direction with respect to the flow direction of the second fluid. A similar tilting of the enclosure within one fin section can have the advantage that in some cases the flow can be properly directed to the downstream fin section.

  The fin section housings that are displaced back and forth are tilted primarily in the opposite direction so that a longer flow path is provided in the second fluid flowing through the heat exchanger. The housings of two adjacent housing zones can be tilted in the same direction, and depending on the circumstances, one housing zone arranged upstream or downstream of both adjacent housing zones It is advantageous if the housings are tilted in opposite directions with respect to the housings of both adjacent housing zones.

  A uniform cover of the flow cross section through which the second fluid is circulated is preferably achieved by the fin sections that are offset and arranged in front and back extending parallel to each other. In that case, the fin sections offset from one another are preferably perpendicular to the flat tube. When the fin face deviates somewhat (up to about 6 degrees) from parallelism, in which case it can still be considered substantially parallel within the framework of the invention, the thermodynamic advantages of the offset fins are It is hardly damaged by things. The use of so-called V-shaped fins or optionally rounded fins is conceivable as well. The fin geometry according to the present invention is particularly applicable in automotive heat exchangers such as refrigerant coolers, heaters, condensers and evaporators.

  According to one advantageous development of the invention, a housing depth LP in the range of 0.7 to 3 mm at a housing angle of 20 to 30 degrees improves the performance. This is because this increases the flow angle, i.e. direction change, of the second fluid from one passage to the adjacent passage, thereby making the flow path longer for the second fluid. The fin height for such a system is preferably in the range of 4-12 mm. The fin density for such a system is preferably in the range of 40 to 85 fins per decimeter, which corresponds to a fin spacing or fin pitch of 1.18 to 2.5 mm.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  Corresponding parts are given the same reference numerals in all figures.

  1a, 1b and FIGS. 2a, 2b, part of which includes a flat tube 2 arranged in parallel to each other, and the flat tube distributes the first fluid FL1a in the first flow direction S1. . The flat tube 2 includes a flow guide element 2a and is connected to a collecting pipe (not shown) or a collecting pipe. The fluid FL1a is, for example, a coolant or a refrigerant condensed in the heat exchanger 1.

  Two (Figs. 1a and 1b) or three (Figs. 2a and 2b) corrugated fins 3 are arranged as cooling fins between two adjacent flat tubes 2. Embodiments having a larger number of corrugated fins 3 are also feasible. The corrugated fins 3 are bent in a meandering manner from one thin plate, and each one fin section 4 a that abuts one flat tube 2 alternates with one fin section 4 b that joins two adjacent flat tubes 2. ing. The fin area 4a that abuts the flat tube 2 is heat transfer coupled to the flat tube 2 and is particularly brazed. A fin section 4b connecting two adjacent flat tubes 2 is perpendicular to the flat tube 2 and forms a flow path for the second fluid FL2, for example air, which flows through the heat exchanger 1 in the flow direction S2. The second fluid FL2 flows substantially parallel to the surface 5 of the corrugated fin 3. That is, when the second fluid FL2 flows into the heat exchanger 1, it first collides only with the thin front surface 6 of the corrugated fins 3. This allows the second fluid FL2 to flow through the heat exchanger 1 at a high speed and a correspondingly high mass throughput.

  3 and 4, the casing 7 formed from the fin section 4b extends across the flow direction S2 of the second fluid FL2 and across the flow direction S1 of the first fluid FL1a. Has been. The housing 7 inside one fin section 4b provides on the one hand a particularly good heat transfer between the second fluid FL2 and this fin section 4b, and on the other hand a fin section arranged obliquely behind it in the flow direction S2. This leads to an appropriate induction of the second fluid FL2 with respect to 4b. Thus, the mass flow rate of the second fluid FL2 flowing through the heat exchanger 1 is utilized for heat exchange substantially completely by fully utilizing the temperature difference between the first fluid FL1a and the second fluid FL2.

  The two corrugated fins 3 arranged in the front-rear direction between the two flat tubes 2 are offset from each other by a half of the width b between the adjacent fin sections 4b. Alternatively, when three corrugated fins 3 are arranged at the front and rear as shown in FIG. 2 and FIG. 4, a deviation of b / 3 can be mainly selected, and other values for the deviation are also conceivable.

  Two or three adjacent corrugated fins 3 extending over the depth T of the heat exchanger 1 are manufactured from one strip 8 by rolling. At the time of rolling, the strip 8 is cut at each shift region between two (FIGS. 1a, 1b, and 3) or three (FIGs. 2a, 2b, and 4) corrugated fins 3 to form corrugated fins 3 A housing 7 is provided. Corrugated fin 3 single (FIGS. 1a, 1b, 3, 5c) or double (FIGS. 2a, 2b, 4, 5d) or higher order deviations (FIGS. 5e, 5f, 5g) ) Can optionally be realized by arranging similar individual corrugated fins 3 with a deviation of 0.1 mm to b / 2, where b is the spacing between two adjacent flat tubes 2.

  The fin area 4a of the corrugated fin 3 that contacts the flat tube 2 does not have a housing. Therefore, in this region, a laminar flow of the fluid FL2 is produced rather than in the fin section 4b which is provided with the housing 7 and connects the adjacent flat tubes 2. The laminar flow may lead to the formation of a boundary layer as the temperature gradient in the flat tube 2 decreases as the travel length increases. However, this effect is limited to a minor extent. That is, the flow of the second fluid FL2 generated between two adjacent fin sections 4b of one corrugated fin 3 is already a short path section T / 2 (FIGS. 1a, 1b, 3, 5c) or T / 4 (FIGS. 2a, 2b, 4, 5d), it is disturbed by the corrugated fins 3 provided downstream in the flow direction S2 to generate an increase in temperature gradient, which leads to an improved heat transfer. Thus, even when the depth T of the heat exchanger 1 is as small as 12 to 20 mm, for example, extremely effective heat transfer is provided between the second fluid FL2 and the first fluid FL1a.

  Each of the corrugated fins 10a, 10b,... 10l shown in FIG. In the current state of the technology of cooling fins having flow guide plates (casings) in individual fins, one fin is usually provided between two pipes in one main plane without any deviation in the main flow direction of the second fluid. (FIGS. 5a and 5b). These cooling fins have at least two so-called housing zones 11, 12 or 13, 14 which are separated from one another by one abdomen of different shaping. In that case, the direction of the flow guide plates (frames) in the adjacent housing zones is usually reversed.

  According to the present invention, mainly two, three, or more corrugated fins (cooling fins) formed in the same manner are arranged one behind the other. That is, the one corrugated fin having the flow guide plate (casing) can be shifted from each other in a plurality of planes. In this case, the number of corrugated fins arranged at the front and rear in the flow direction of the second fluid can be selected depending on the depth of the heat exchanger and / or the depth of the corrugated fins. In the case of a structure depth of 12 to 18 mm, for example, two columns, three columns or more can be used, and in the case of a structure depth of 24 mm or less, for example, two columns, three columns, four columns or more can be used. For 30 mm or less, for example, 2 rows, 3 rows, 4 rows, 5 rows or more can be used, and for a structure depth of 36 mm or less, for example, 2 rows, 3 rows, 4 rows, 5 rows, 6 rows or more If the structure depth is 42 mm or less, for example, 2 columns, 3 columns, 4 columns, 5 columns, 6 columns, 7 columns or more can be used, and if the structure depth is 48 mm or less, for example 2 columns 3 rows, 4 rows, 5 rows, 6 rows, 7 rows, 8 rows or more can be used, and when the structure depth is 54 mm or less, for example, 2 rows, 3 rows, 4 rows, 5 rows, 6 rows, Use 7, 8, 9 or more rows If the structure depth is 60 mm or less, for example, 2 columns, 3 columns, 4 columns, 5 columns, 6 columns, 7 columns, 8 columns, 9 columns, 10 columns or more can be used, and the structure depth is 66 mm or less. In some cases, for example, 2, 3, 4, 5, 6, 7, 8, 9, 10, 10, 11 or more can be used.

  An example of two rows 15, 16 is shown in cross-sectional view in FIG. 5c.

  An embodiment of three rows 17, 18, 19 is shown in cross-sectional view in FIG. 5d.

  An example of four rows 20, 21, 22, 23 is shown in cross section in FIG. 5e.

  Examples of five rows 24, 25, 26, 27, 28 are shown in cross-sectional view in FIG. 5f.

  An example of five rows 29, 30, 31, 32, 33 is shown in cross-sectional view in FIG. 5g.

  Examples of five rows 34, 35, 36, 37, 38 are shown in cross-sectional view in FIG. 5h.

  Three or more staggered rows can be distributed mainly in a total of two staggered planes as in the embodiments of FIGS. 5d, 5e, and 5g. However, they can also be distributed over three or more different planes as in the embodiment of FIGS. 5f, 5h, and the spacing between each two planes can be the same or different.

  Alternatively, only the region 41 or 44 between the two housing zones 39, 40 or 42, 43 in one plane can be shifted with respect to the housing zones 39, 40 or 42, 43 (FIG. 5i and FIG. 5j). In the region 41 or 44, the corrugated fins 10i or 10j have no housing. This configuration also results in the effect of a temperature boundary layer at the tube wall and / or improved plate flow.

  Similarly, the housing bands 45, 46, 47 of the corrugated fin 10k can be of different sizes (FIG. 5k). In this case, for example, it is advantageous to assign the housing bands 45 and 47 [original: 46] of the first tube row and the housing bands 46 [original: 47] of the second tube row. This is because the thermal coupling between the tube rows is suppressed by the shift 49 between the housing zones 46 and 47.

  It is also possible to combine the variously sized housing zones 65, 66, 67, 68, 69 in various planes as in the corrugated fin 10l (Fig. 5l).

  The number of enclosures per row is, for example, 2 to 30 enclosures depending on the number of rows and depth of the heat exchanger. Mainly, the number of enclosures per enclosure band is not the same when the number of columns is odd, that is, 3, 5, 7, 9 or 11 columns from the viewpoint of manufacturing technology. For an even number of columns, the number of enclosures per enclosure band can be the same, but this is not essential.

  In the following (FIGS. 6 to 9), a simulation of air flow in a heat exchanger having three differently configured corrugated fins is described.

The simulation is performed under the following conditions: tube wall temperature = 60 ° C .; air inlet temperature = 45 ° C .; air density = 1097 kg / m ³ ; air inlet velocity v _Luft = 1 and 3 m / s; fin height = 8 mm; fin Depth = 16mm. In the simulation, on the other hand, a single wave fin consisting of a single line having two frame bands separated from each other in the roof shape by the abdomen, that is, one wavy fin without deviation is considered as a base (current state of the art). In addition, one corrugated fin having two rows and one corrugated fin having three rows are considered. In addition to the air side pressure drop, the simulation measures the mass flow in the individual plate openings and the radiation output from the tube to the cooling air.

FIG. 6 shows a heat exchanger 51 with corrugated fins 52, 53, air inlet velocity v _Luft = 3 m / s, air flow in the region between the boundary conditions and the two enclosure zones 54, 55 or 56, 57. Indicates the bandwidth. The abdomen 58 or 59 between each two housing zones in this case has a roof shape. An arrow 60 indicates the main flow path of air particles, which air particles flow through the last plate opening 61 in front of the abdomen 59 and subsequently undergo a flow direction change, and the plate openings 62, It flows in 63. As can be seen from the figure, first, the second plate opening 62 of the housing zone 57 again circulates a large number of air particles, and first the velocity zone in the third plate opening 63 is within the preceding housing zone 56. Again approximately matches the velocity pattern.

FIG. 7 shows a heat exchanger 71 with corrugated fins 72, 73, air inlet velocity v _Luft = 3 m / s, the above boundary conditions, a deviation 74 or 75 between each of the two housing zones 76, 77 or 78, 79. The air flow band in the region of An arrow 80 indicates the main flow path of air particles before the shift 75, on the one hand, in the last plate opening 81 before the shift, and on the other hand in the shift opening 75. The air particles undergo a change of direction after flowing through the offset opening 75, and the air particles flowing through the offset opening continue to flow mainly in the first and second plate openings 82 and 83 of the adjacent enclosure zone 79. The air particles that have flowed through the last plate opening 81 before the deviation again flow mainly in the third plate opening 84 of the subsequent enclosure zone 79 after undergoing a flow direction change.

8 and 9 show three different configurations of corrugated fins, air inflow velocity v _Luft = 1 m / s (FIG. 8), v _Luft = 3 m / s (FIG. 9). shows a curve diagram obtained by plotting the ratio against depth of the tube or the heat exchanger of the half _^1/2 m _ges of the total mass flow rate of air as a plate opening) the mass flow rate m _Kieme fluid FL2. The mass flow rate% in the opening of the shift part is not shown.

  As is apparent from FIG. 8, in both corrugated fin configurations having two or three rows (one or two offsets), the air mass flow% is always above 9%, whereas the corrugated fins Are in one plane / row, the air mass flow rate drops below 8% following the abdominal region at both plate openings, with a minimum of about 4%. In the corrugated fin consisting of one plane, the air mass flow rate is reduced from about 12% to about 10% at the plate opening in front of the abdominal region, whereas in the corrugated fin consisting of two planes / rows in this case The mass flow rate in the last plate opening increases from about 12% to about 13%. Here again, air flow realignment follows the offset and the first plate opening is only added at about 10% air mass flow rate. In a three-row corrugated fin, the mass flow rate is still increased to about 13% by the last plate opening before the offset. Here again, air flow realignment follows the offset, and the first plate openings are only added at about 10-11% air mass flow rate, respectively.

  As is apparent from FIG. 9, the corrugated fins have an air mass flow rate% always above 12% in both corrugated fin configurations having two or three rows (one or two offsets). Are in one plane / row, the air mass flow rate drops below 11% following the abdominal region at both plate openings, with a minimum of about 4.5%. In a corrugated fin consisting of one plane, the air mass flow rate drops from about 16.5% to about 15% at the plate opening in front of the abdominal region, whereas in the corrugated fin consisting of two planes / rows, there is a shift The mass flow rate in the last plate opening before the section increases from about 16.5% to about 18%. The realignment of the air flow again follows the offset and the first plate opening is only added at an air mass flow rate of about 14%. With three rows of corrugated fins, the mass flow rate in the last plate opening before the offset is again increased to about 18-19%. The realignment of the air flow again follows the offset and the first plate openings are only added at about 14% air mass flow rate, respectively.

  A heat exchanger 1 in which parts a and b in FIG. 10 and a and b in FIG. 11 are respectively provided includes flat tubes 2 arranged in parallel to each other in two rows 1a and 1b, and the flat tubes are the first fluid. FL1a and FL1b circulate in the first flow direction S1. Similarly, reverse distribution is also possible. The flat tube 2 is connected to a collecting pipe (not shown) or a collecting pipe. The fluids FL1a and FL1b are, for example, a coolant and a refrigerant condensed in the heat exchanger 1. Just as well, it can be two identical fluids inside a two-row or multi-row heat exchanger 1.

  Between two adjacent flat tubes 2, two (a and b in FIG. 10) or three (a and b in FIG. 11) corrugated fins 3 are arranged as cooling fins. An embodiment with a larger number of corrugated fins 3 is also feasible. The corrugated fins 3 are bent in a meandering manner from one thin plate, and each one fin section 4 a that abuts one flat tube 2 alternates with one fin section 4 b that connects two adjacent flat tubes 2. ing. The fin area 4a that abuts the flat tube 2 is heat transfer coupled to the flat tube 2 and is particularly brazed. A fin section 4b that connects two adjacent flat tubes 2 is perpendicular to the flat tube 2 and forms a flow path for a second fluid FL2, for example air, that flows through the heat exchanger 1 in the flow direction S2. The second fluid FL2 flows substantially parallel to the surface of the corrugated fin 3. That is, when the second fluid FL2 flows into the heat exchanger 1, it first collides only with the thin front surface 6 of the corrugated fin 3. This allows the second fluid FL2 to flow through the heat exchanger 1 at a high speed and a correspondingly high mass throughput.

  The casing 7 formed from the fin section 4b extends across the flow direction S2 of the second fluid FL2 and across the flow direction S1 of the first fluids FL1a and FL1b. The housing 7 inside the fin section 4b provides, on the one hand, a particularly good heat transfer between the second fluid FL2 and this fin section 4b, and on the other hand to the fin section 4b arranged obliquely rearward in the flow direction S2. Proper guidance of two fluids FL2. Thus, the mass flow rate of the second fluid FL2 flowing through the heat exchanger 1 is used for heat transfer substantially completely by fully utilizing the temperature difference between the first fluids FL1a, FL1b and the second fluid FL2. .

  The two corrugated fins 3 arranged in the front-rear direction between the two flat tubes 2 are shifted from each other. The manufacture of the wavy fins that are shifted and integrated is performed, for example, as described with reference to FIGS. 1a and 1b.

  The corrugated fins 3 are shifted from each other in the intermediate region 9 shown enlarged in FIG. 10b and FIG. 11b between the flat tube rows 1a and 1b. Due to the integral construction, the corrugated fins 3 of the various tube rows are connected to each other via a thin abdomen 9a in the region of the fin area 4a that abuts the flat tube 2. Since these abdominal portions 9a are the only heat transfer coupling portions between the tube rows 1a and 1b, heat transfer from one tube row to the other tube row is effectively suppressed.

The heat exchanger which has two corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of one tube row is shown. The heat exchanger which has two corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of one tube row is shown. The heat exchanger which has the three corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of one tube row is shown. The heat exchanger which has the three corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of one tube row is shown. Figure 2 shows two corrugated fins formed from a single strip. 3 shows three corrugated fins formed of a single strip. A corrugated fin without displacement with two housing zones is shown in cross-section. A corrugated fin without displacement with two housing zones is shown in cross-section. Two rows of corrugated fins made of one strip are shown in cross-sectional view. Three rows of corrugated fins made of one strip are shown in cross-sectional view. 4 rows of corrugated fins made of one strip are shown in cross-sectional view. 5 rows of corrugated fins made of one strip are shown in cross section. 5 rows of corrugated fins made of one strip are shown in cross section. 5 rows of corrugated fins made of one strip are shown in cross section. Three rows of corrugated fins made of one strip are shown in cross-sectional view. 3 rows of corrugated fins made of one strip are shown in cross section Three rows of corrugated fins made of one strip are shown in cross-sectional view. 5 rows of corrugated fins made of one strip are shown in cross section. Fig. 6 is an instantaneous photograph of a simulated air flow in a corrugated fin without misalignment. FIG. 6 is an instantaneous photograph of simulated air flow in a corrugated fin with a shift. FIG. 5 is a plot of the ratio of the total air mass flow rate to the total air mass flow rate and the depth of the tube at a low air inflow rate. FIG. 6 is a plot of the ratio of the total air mass flow rate to the total air mass flow rate and the tube depth at a high air inflow rate. a shows the heat exchanger which has two corrugated fins arrange | positioned back and forth by shifting as a cooling fin between each two adjacent flat tubes of two tube rows. b shows the heat exchanger which has two corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of two tube rows. a shows the heat exchanger which has three corrugated fins arrange | positioned back and forth as a cooling fin between each two adjacent flat tubes of two tube rows. b shows the heat exchanger which has the three corrugated fins arrange | positioned back and forth by shifting as a cooling fin between each two adjacent flat tubes of two tube rows.

Claims (12)

It is a heat exchanger for automobiles, and has a flat tube (2) through which the first fluid (FL1a, FL1b) can flow, and the flat tube can be added with the second fluid (FL2) on the outside. The flat tubes are arranged in at least two rows substantially crossing the flow direction (S2) of the second fluid (FL2) and parallel to each other, and at least one tube row is attached to each first fluid. The rows of flat tubes are spaced apart from each other and form a flow path through the heat exchanger for the second fluid (FL2), with cooling fins extending between adjacent flat tubes (2) flowing. A plurality of corrugated fins (3) arranged in the path and arranged in the front-rear direction in the flow direction (S2) of the second fluid (FL2) are provided as cooling fins shifted laterally from each other. A plurality of corrugated fins (3) arranged in one common band Heat exchanger, characterized by being formed from (8). 2. A heat exchanger according to claim 1, characterized in that the surface (5) of the corrugated fin (3) is arranged substantially parallel to the flow direction (S2) of the second fluid (FL2). The heat exchanger according to claim 1 or 2, characterized in that a plurality of corrugated fins (3) arranged offset from each other are formed in the same way. The heat exchanger according to any one of claims 1 to 3, characterized in that at least one of the corrugated fins (3) has a housing (7) for guiding the second fluid (FL2). All the casings (7) of one fin section (4b) defined by two flat tubes (2) are inclined in the same direction with respect to the flow direction (S2) of the second fluid (FL2). The heat exchanger according to claim 4, wherein 6. A heat exchanger according to claim 5, characterized in that the housing (7) of the two fin sections (4b) which are displaced forward and backward is tilted in the same direction. 6. A heat exchanger according to claim 5, characterized in that the housing (7) of the two fin sections (4b) which are displaced forward and backward is inclined in the opposite direction. Heat exchanger according to any one of the preceding claims, characterized in that the two fin sections (4b) that are displaced forward and backward are substantially parallel to each other. 9. Heat exchanger according to claim 8, characterized in that the fin section (4b) is arranged substantially perpendicular to the flat tube (2). 10. A heat exchanger according to any one of the preceding claims, characterized in that the corrugated fins (3) have the same spread or a similar spread in the main flow direction of the second fluid. 11. A heat exchanger according to any one of the preceding claims, characterized in that different tube rows allow different fluids to flow. The heat exchanger according to any one of claims 1 to 10, characterized in that various tube rows allow one fluid to flow.

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