KR20060101481A - Flow channel for a heat exchanger, and heat exchanger having flow passage of this type - Google Patents

Abstract

The invention relates to a flow channel of a heat exchanger with two parallel heat transfer areas (F1, F2) that are arranged at a distance corresponding to a channel height H. Each heat transfer area (F1, F2) is provided with a structure that is formed by a plurality of structural elements which are placed next to each other in rows running perpendicular to the direction of flow P and extend into the flow channel. Each structural element has a width B, a length L, a height h, a flow-off angle a, and an overlap U while being provided with a longitudinal axis.

Description

Heat exchanger with flow path of heat exchanger and flow path {FLOW CHANNEL FOR A HEAT EXCHANGER, AND HEAT EXCHANGER HAVING FLOW PASSAGE OF THIS TYPE}

The present invention relates to a flow path of a heat exchanger in which a medium according to claim 1 flows in a flow direction. The invention also relates to a heat exchanger having a flow path according to claim 40.

A first medium, for example exhaust gas or liquid coolant, flows through the flow path of the heat exchanger, the flow path defining the first medium from the second medium and the heat of the first means is transferred. This type of flow path may be in the form of a circular cross section, a rectangular tube, a flat tube or a pair of disks and each of the two plates or disks may be joined at the edge side. The media exchange heat with each other and are generally different. For example, the thermal exhaust gas flows particulates in the tube, and the liquid coolant flows around the exhaust gas tube to the outside and varies the heat transfer state inside and outside the tube. Therefore, in particular, the exhaust tube has a V-shaped vortex generator which is formed in the form of a diffusion plate inside, and the vortex generator swirls the flow and prevents the settling of particulates and increases the thermal conductivity of the exhaust gas. Methods of the type between exhaust gas heat exchangers are described in European Patent A 677 715, German Patent 195 40 683, German Patent A 196 54 367 and German Patent A 196 54 368. Conventional exhaust heat exchangers have rectangular tubes made of stainless steel assembled from two half-shells welded and soldered, and a vortex generator, known as a winglet, is formed, stamped or arranged on one rear side. The pair of winglets of the two half shells are offset from each other on the vertical side of the tube and are formed in the direction of the flow (German patent 196 54 367, German patent 196 54 368) or facing each other (German patent 195 40 683).

In German patent A 101 27 084 the name of the invention is a heat exchanger, in particular in a coolant / air cooler with flat tubes and corrugated fins, the planar side of the flat tube having a structure comprising structural elements. The structural element has a vortex generation function by forming a V-shape in the transverse heat in the flow direction of the coolant and / or improving heat transfer to the transverse direction by the vertical axis of the tube and to the coolant side. The vortex generator is stamped on opposite tube walls and projects into the coolant inlet. The row of vortex generators on the planar tube side is offset in the flow direction by the row on the other planar tube side. Thus, projecting the height of the vortex generator inward is greater than half the clear width of the flat tube cross section.

European patent A 1 061 319 relates to a planar tube of an automobile radiator, the planar axis having a structure comprising respective structural elements formed to extend side by side. In order to divert the flow inside the planar tube in a zigzag form, structural elements arranged differently are formed in the flow direction. In particular, however, the row includes a structural element in one planar tube which is offset in the flow direction by a column facing the planar tube side. Thus, in each case, the smooth area of the inner wall of the planar tube is located opposite to the row of structural elements. The flow in the coolant tube is crossed but simultaneously affected by the structural elements of one planar tube and the other planar tube. The above prevents the tube from clogging in particular. In addition, there is potential due to thermal conductivity.

It is an object of the present invention to improve the flow path and heat exchanger of the type by the thermal conduction force and in particular to improve the formation of the vortex, the pressure loss occurring only by an acceptable temperature.

The object of the invention is achieved by the description of claim 1. According to the present invention, the structural elements formed side by side on one side and the other side of the flow path are located facing each other, and in each case are formed at the same level in the flow direction. The structural elements or rows are located opposite each other and can be offset from each other in the flow direction and overlap still exists. Therefore, the structural element protrudes from the surface of one heat exchanger into the flow path and the other heat exchanger surface is simultaneously disturbed in the flow and vortex flow is induced to improve the thermal conduction inside the flow path. Therefore, in the case of the exhaust gas, precipitation of fine particles is prevented. The reduction in compression maintains an acceptable limit. The flow in the flow path is disturbed from two sides at the same time, the two interfaces being separated at the same time, in particular causing a wide range of vortices. The structural elements or rows of structural elements face each other and are located outside of the flow path (exhaust gas cooler on the side of the coolant). Preferred embodiments of the invention are described in the dependent claims.

According to the invention the heat comprises a structural element formed in a position or in another form in parallel with each other in the flow path (P). Thus, in particular, the columns may be formed by a single structural element, for example a single structural element in which no further structural elements are formed side by side.

A preferred embodiment of the present invention provides another embodiment, which is a straight or curved line of structural elements, which may have a constant or varying flow stop angle depending on the flow direction. Conversion from the relatively large flow angle of the flow stop angle to the flow stop angle results in a 'flexible' flow change and a somewhat reduced pressure loss. According to another embodiment of the present invention, the structural elements in the column are offset, wherein the structural elements are formed in a row formed laterally by the flow path but are wave-shaped in the flow direction and of lower pressure loss. You have an advantage. Thus, the opposing rows, ie one flat tube or the other flat tube, are offset from one another in the flow direction but the overlap is always maintained between the two rows. The offset in the flow direction leads to lower pressure losses. If the structures are formed facing each other, the strength can be increased if they contact each other and are joined together by welding or soldering. According to another embodiment the structural elements are not formed at the same distance in the column but the columns have empty spaces and in each case they have structural elements located opposite each other on opposite sides as shown in plan view. The empty space is 'filled'. The above has the advantage of lower pressure loss.

Furthermore, studs and / or webs stamped inside or outside (rows comprising structural elements) between or between the structural elements are achieved by 'supporting' and increase in strength. The vortex generating structure may have the function in whole or in part.

According to a preferred embodiment the surfaces of the heat exchanger can be located facing each other and in particular the structural elements can be formed in a curved line. Preferred embodiments of the invention can be achieved in particular by tubes having a circular or elliptical cross section.

In a preferred embodiment the heat exchanger surfaces are located facing each other and are the first thermal engineering surface. In yet another embodiment the heat exchanger surface is a second thermal engineering surface, in particular formed by fins, webs or the like and is preferably clamped, welded or soldered to the flow path.

In a preferred embodiment the height h of the structural element is between 2 mm and 10 mm, in particular between 3 mm and 4 mm and preferably about 3,7 mm.

According to a preferred embodiment of the present invention, the flow path is rectangular, and the width b is 5 mm to 120 mm and preferably 10 mm to 50 mm.

In a preferred embodiment the hydraulic diameter of the flow path is between 3 mm and 26 mm, in particular between 3 mm and 10 mm.

In a preferred embodiment at least one, in particular the row of structural elements has a plurality of structural elements.

The object of the invention is achieved by the description of claim 40. The flow path described above by the present invention is provided as a planar, round, oval or rectangular tube of the heat exchanger and is preferably an exhaust gas heat exchanger. The formation of the structural element according to the invention is preferably stamped on the inner wall of the tube and improves the performance of the heat exchanger. Particularly in the exhaust gas heat exchanger, the structural element is formed of heat because the deposition of particulates inside the planar tube is avoided. The coolant is obtained by the coolant circulation by the inner combustion engine which discharges the exhaust gas flowing around the outer surface of the exhaust gas tube. In addition, a structure stamped on the plate or disk of the heat exchanger is possible.

Embodiments of the present invention are explained in more detail by the accompanying drawings.

1 illustrates a flow path according to the prior art.

2A, 2B and 2C are cross-sectional views of the flow path.

Figure 3 shows a planar tube having a structure according to the present invention.

4 shows a half shell of the planar tube of FIG. 3.

5A, 5B and 5C illustrate various structural elements.

6A, 6B, 6C, 6D, 6E, 6F, 6G, and 6H show the structure of the flow path according to the present invention.

7A and 7B show another structure according to the present invention.

8 shows another structure of the present invention.

9A, 9B, 9C, and 9D show structural elements of right and left symmetry.

10A, 10B, 10C, and 10D illustrate planar offset structural elements.

11A, 11B, 11C, and 11D show rows of modified structural elements.

12A and 12B show another structural element.

1 is a schematic diagram of a flow path formed of a rectangular tube and has a rectangular inlet end face 2, two opposing planar sides F1 and F2 and two opposing narrow sides S1 and S2. Flow medium, such as exhaust gas, flows through the path 1 in the direction indicated by arrow P. Vortex generators 3a, 3b, 4a, 4b are V-shaped and are formed on the lower plane side F2 by generating vortices and affect the increased vortex flow and at the same time settling particulates in the case of exhaust gases To prevent. It is shown by the above-mentioned prior art. In addition, the vortex generators 3a, 3b, 4a, 4b are formed in pairs and installed in a V-shape and extend from the diffuser type in the flow direction and are due to the winglets according to the prior art.

2A shows a cross section of a flow path formed as a planar tube, in which winglet pairs 5a, 5b, 6a, and 6b are formed on the upper plane side F1 and the lower plane side F2. The path cross section has a path height H and a path width b. The winglets 5a, 5b, 6a, 6b have a height h protruding in the path cross section. The formation of the winglets corresponds to the prior art. The shapes F1 and F2 are applied to the embodiments of the present invention described below.

FIG. 2B shows a cross section of the flow path 1 ′ formed of a circular tube and the structural elements 13 ′ and 13 are formed on the upper planar tube side F1 and the lower planar side F2, respectively. The path cross section has a path height H.

FIG. 2C shows a cross section of the flow path 1 formed of a planar tube, in which the heat exchanger surfaces F1 and F2 represent a second thermal engineering surface since no heat transfer is directly from one medium to the other. The heat exchanger surface has structural elements 13, 13 ′.

3 is a plan view showing a flow path formed of the planar tube 7 according to the present invention. The planar tube (7) is formed of a vertical axis (7a), width (b) and two rows (8, 9) or winglets (10, 11, winglet) of the structural elements, is formed in a V shape and in more detail the same pattern In the upper side (F1) and the lower side (F2) of the planar tube (7) is stamped in each case the upper winglet row covers the lower row. In the case of eight winglets arranged uniformly over the entire width (b), they are formed in rows but may be six or seven. If the tube, disc or plate is narrow, there may be six or less winglets, and in the wide case, eight or more. In the distance s two rows 8, 9 can be measured from the middle to the middle and can be twice to six times the winglets. A smooth area between each row is supported by the stamp. The row of winglets extends over the entire length of the flat tube 7 and at this distance s in particular on both sides of the flat tube 7.

4 shows the lower half shell 7b of the planar tube 7 as seen in the direction of the vertical axis 7a of the planar tube 7. The half shell 7b has a base F2 and two side rims 7c and 7d and the winglets 11 'are formed on the base or lower side F2, ie stamped on the tube wall. The upper half shell is not shown. The above is formed symmetrically and welded vertically to the lower half shell 7b of the side rims 7c and 7d. The winglet 11 ′ has a height h by protruding in the cross-sectional area of the flat tube 7. The tube is formed from a sheet metal member that is deformed and welded on one side.

In a preferred embodiment the width b of the planar tube is 40 mm or 20 mm leaving a cross section height of 1.4 mm for the core flow. The distance s between the rows is about 20 mm.

The flat tube (7) is preferably used in an exhaust gas heat exchanger (not shown), and from the internal combustion engine of the vehicle while the coolant from the coolant circulation of the internal combustion engine cools the air flowing to the outer surface. Exhaust gas flows through the inner surface. The outer surface of the flat tube 7 according to the prior art can be flexible and fixed at a distance from the adjacent tube by a stamped stud. However, it may be provided on the outer surface of the flat tube 7 to improve the thermal conductivity on the coolant side for fins.

Figures 5a, 5b, 5c and 5d show the respective structural elements provided for the structure according to the invention of the flow path.

FIG. 5a shows an elongated structural element 13 having an angle α with a reference line q, a vertical axis forming a flow stop angle. The direction of the flow is indicated by arrow P in FIGS. 5A-5D. The reference line q is formed perpendicular to the flow direction P. The structural element 13 has a length L and a width B. The rear side may be constant or inconsistent and may be improved in the flow direction P. FIG.

5B is expanded but the angular structure elements with two vertical axes 14a and 14b include the reference lines q and angles α and β, respectively, when tilted by each other. The angle β is the flow flow angle and the angle α is the flow stop angle. The flow direction, indicated by arrow P, can be expanded even further because it can be started lightly in two steps. Thus, a lower pressure loss results in comparison with structural elements having the same flow stop angle α in FIG. 5A. The length of the structural element extending the vertical axes 14a, 14b is denoted by L.

5c shows an arcuate structural element 15 having a curved vertical axis 15a corresponding to an arc of radius R. As shown in FIG. The upstream angle refers to the flow flow angle β and the downstream angle refers to the flow stop angle α. The flow transitions smoothly through the angle (90 ° -β) and is further extended by the angle (90 ° -α). The continuous increase in flow divergence causes a lower pressure loss compared to the structural element 13 shown in FIG. 5A. The length of the structural element 15 extends the vertical axis 15a denoted by L.

5D shows another structural element, which is Z-shaped and has a vertical axis 167a formed in the Z-shape.

The vertical axis 16a has two different curvatures but is connected to two arcuate cross sections having the same radius (R1 = R2). The flow flow angle is denoted by β and the flow stop angle is denoted by α, which corresponds to a flow transition of (90 ° -α) and is located in the central region of the structural element 16. The flow in contact with and not in contact with the structural element is actually located in the flow direction (P). Thus, the flow is converted to a particularly low pressure loss. The length of the structural element extends along the vertical axis 16a, denoted L.

6a, 6b, 6c, 6d, 6e, 6f, 6g, 6h illustrate the formation pattern of the structural element 13 in particular in part of the flow path by FIG. 5a. In the preferred embodiment, only a single structure facing each other is not shown.

6a shows an extended structural element 13 formed in two rows 17, 18 of the flow direction P distance s. The structural element 13 by the thick line is stamped on the upper side F1 of the flow path. Structural element 13 ′ is indicated by a dashed line and what is formed in rows 19 and 20 is formed on the lower heat exchanger surface or on the side face F2 of the flow path. The row is shown by the dashed line. The structural element 13 ′ of the lower surface F2 faces the structural element of the upper surface F1 and has a flow stop angle (α, see FIG. 5A) facing each other. Further, the rows 19, 20 are offset in the flow direction P by the columns 17, 18, in particular by the offset f. The structural elements 13, 13 ′ and the rows 17, 18, 19, 20 have a depth T and extend in the flow direction P, respectively. The offset f is shallower than the depth T due to the overlap U due to the difference between the depth T and the offset f and remains between the rows 18, 20, 17, 19. 100% overlap (U) in the case of rows of equal depth (T) means that the offset is equal to 0 (f = 0). In the case of rows having different depths T1 and T2 (for example, T1 < T2), 100% overlap means the same as the overlap U, which is a smaller depth T1 (U = T1). The offsets between the rows 17, 19, 18, 20 are located opposite each other and preferably cause a lower pressure drop than in the case of rows without offsets.

FIG. 6B shows different patterns of structural elements formed in the columns, in particular in the case of rows 21 and 22 with different flow perception angles (α, not shown). ) Is shown by the thick line stamped on the upper surface F1 of the flow path. The structural element 13 ′ is formed to intersect the upper structural element in the plan view of the flow path P and is shown by a dotted line. The upper row has a structural element 13 which is not offset by the lower row comprising the structural element. The overlap U is 100%.

6C-6H illustrate the structural elements 13, 13 ′ of the upper side (F1, shown in bold line) and the lower side (F2, shown in dashed line) of the flow path.

FIG. 6h also shows a support element 13 ″ outside the flow path, in which the support element of the preferred embodiment is formed adjacent to the structural element 13, 13 ′ and in particular the structural element 13, 13 ′. It is formed in the heat formed by). It is preferred for a support element stamped on the wall of the flow path. In order to preferably support each said flow path, the support element 13 ″ has a distance between two flow paths or a height between each flow path and corresponding to the housing wall of the heat exchanger.

7A and 7B illustrate various embodiments of the formation of the structural element in columns.

FIG. 7A shows a flow path with two columns 23, 24 of the structural element 13 formed in the letter V on the upper side F1. However, the structural elements 13 are not formed at a constant distance from each other, but have empty spaces 25, 26, 27, which are filled in the lower side F2 by the structural elements 13 ′. Structural elements 13, 13 'are uniformly formed. The formation of rows 23 and 24 with 'empty spaces' and the heat corresponding to the lower side results in a lower pressure loss in the flow direction P, in which the structural element inhibits inter-partition flow.

FIG. 7B shows the similar formation of the structural elements 13 parallel to each other on the upper side F1 with the void space between the columns 28, 29. The empty space between the structural elements 13 is filled by the structural element 13 'of the lower side F2 and the structural element 13 of the upper side F1 and the structural element 13 of the lower side F2. ') Complement each other to form the zigzag arrays described above. The formation includes a relatively low pressure loss.

FIG. 8 shows another embodiment of the arrangement of the structural elements 13, 13 ′ in two columns 30, 31 of the upper side F1. The structural elements 13 of the rows 30 and the structural elements 13 ′ of the opposite rows (the lower side F2) are formed in parallel and are equally spaced from each other. The same application to the second column 31 leads to a change of flow in the flow direction P as shown except for the opposite flow stop angle.

Each structure shown in FIGS. 6A, 6B, 7A, 7B and 8 has a structural element 13 as shown in FIG. 5A. The structural element 13 is identically located by the structural element 14 (FIG. 5B), the structural element 15, FIG. 5C or the structural element 16 (FIG. 5D). The foregoing may be formed identically using other structural elements, for example as indicated by reference numerals 13 and 14 in a single column.

9A, 9B, 9C, and 9D illustrate various embodiments of structural elements 13, 14, 15, 16 arranged symmetrically. Thus, the pair of winglets 32, 33, 34, 35 are spaced apart at the minimum distance in each case provided between the two structural elements. The flow direction is the direction indicated by arrow P and flows the pair of winglets located at the narrowest point (a). Thus, different winglet pairs 32 to 35 result in a reduction in pressure loss. The winglet pairs are formed parallel to each other, for example, as shown in FIGS. 6 to 8.

10A, 10B, 10C and 10D show various embodiments of the structural elements 13, 14, 15 and 16 by parallel adjustment. Thus, the dual structures 36, 37, 38, 39 are equally spaced on the flow and stop sides and are formed as in the structural elements shown in FIGS. 6 to 8.

An important point of the structural element on the upper side and / or the lower side is that it does not have to have the same shape or dimension as shown in FIG. 11A. As shown in FIG. 11, the structural element is formed with an offset f in the flow direction P. FIG.

FIG. 11C shows various embodiments of the flow stop angle of the structural element and FIG. 11D shows an embodiment with various lengths L1 and L2 of the structural element. Various embodiments are possible as shown in FIGS. 11B, 11C and 11D. In addition, various embodiments of the upper and / or lower surfaces F1 and F2 are possible respectively.

FIG. 12A shows another structural element 43 formed at an angle with two straight lines 43a and 43b, joined by an arcuate of apex. Thus, the structural element 43 illustrates another embodiment of the winglet pair 32 shown in FIG. 9A. The medium preferably flows in the direction of apex 43c, indicated by arrow P. FIG.

FIG. 12B illustrates another embodiment of the pair of structural elements 34 shown in FIG. 9C, that is, a structural element having two curved rims 44a and 44b connected by an arc 44c at the apex. 44 is shown. The structural element 44 has a larger flow change due to the rims 44a and 44b which flows in the direction of the vertex 43c by the arrow P and is curved into the flow.

12A and 12B may be formed in a V-shaped structure.

All structures can be combined with each other in a preferred manner as described above.

Claims (48)

In the flow path 1 of the heat exchanger through which a medium flowing in the flow direction P of the heat exchanger having the heat exchanger surfaces F1 and F2 positioned opposite to each other, The flow path 1 is formed in parallel and / or in the space of the flow height (H), formed parallel to each other in the transverse row for each flow direction (P) and protruding toward the flow path (1) side Has a structure formed in various forms of elements, The structural element has a width (B), a length (L), a height (h), a flow stop angle (α) and a vertical axis, respectively, The at least two rows 17, 18, 19, 20 are characterized in that they comprise structural elements 13, 13 ′ having mutually overlapping U and having heat exchanger surfaces F1, F2 facing each other. Flow path of heat exchanger. The method of claim 1, The overlap (U) is a flow path of the heat exchanger, characterized in that 100%. The method of claim 1, The flow path of the heat exchanger, characterized in that the at least one structural element (13) is in particular extending in a rectangular shape and has a straight vertical axis (13a). The method of claim 1, The at least one structural element 14 is angularly formed and has an angular vertical axis 14a, 14b which forms the flow stop angle α and the flow flow angle β in the flow direction P. Chi flow path. The method of claim 1, The at least one structural element 15 is arcuate and has a radius R and is curved and has a vertical axis 15a which forms the flow stop angle α and the flow flow angle β in the flow direction P. Flow path of the heat exchanger, characterized in that. The method of claim 1, At least one structural element 16 is formed in a Z shape and is bent twice with radii R1 and R2 and has a vertical axis forming the flow stop angle α and the flow flow angle β in the flow direction P. 16a), wherein the flow path of the heat exchanger. The method of claim 1, At least one structural element (43) is a V-shaped flow path of the heat exchanger, characterized in that it has a V rim (43a, 43b) straight from the flow direction. The method of claim 1, At least one structural element (44) is V-shaped and has a V-rim (44a, 44b) curved from the flow direction. The method according to claim 1, wherein At least one of the structural elements (13, 14, 15, 16) has a height (h) of 20% to 50% of the path height (H). The method of claim 9, The length L of at least one of the structural elements 13, 14, 15, 16 is two to twelve times that of the structural element. The method according to claim 1, wherein The distance (s) between the rows is a flow path of the heat exchanger, characterized in that 0.5 to 8 times the depth (T). The method according to claim 1, wherein The flow path of the heat exchanger, characterized in that the distance between each two rows vary in the flow direction (P). The method according to claim 1, wherein At least one structural element (13, 14, 15, 16) has a constant width (B) of 0.1 to 6.0 mm and preferably a flow path of the heat exchanger, characterized in that 0.1 to 3.0. The method according to claim 1, wherein The at least one structural element 13, 14, 15, 16 has a width that increases in the flow direction between the start width B1 and the end width B2, the start width B1 having a width of 0.1 to 4 mm. The end width (B2) is a flow path of the heat exchanger, characterized in that having a width of 0.1 to 6mm. The method according to any one of the preceding claims, The flow stop angle α is 20 ° to 70 °, preferably 40 ° to 65 °, and more preferably 50 ° to 60 °. The method according to claim 4 to 6 and 15, The flow flow angle (ß) is a flow path of the heat exchanger, characterized in that larger than the flow stop angle (α). The method of claim 6, The radius (R) is 1 to 10mm and preferably a flow path of the heat exchanger, characterized in that 1 to 5mm. The method according to claim 5, wherein The radius (R1, R2) is the flow path of the heat exchanger, characterized in that the same as the radius (R). The method according to any one of claims 1 to 18, The flow path of a heat exchanger, characterized in that the columns (17, 18, 19, 20) in each case have the same structural elements (13, 13 '). The method according to any one of claims 1 to 18, Wherein in each case heat is provided with different structural elements. The method of claim 19, The individual structural elements (13, 14, 15, 16) are formed parallel to each other in pairs (32, 33, 34, 35) at a distance (a). The method of claim 19, Some or all of the structural elements 13, 14, 15, 16 are characterized in that they are formed in pairs 36, 37, 38, 39 at distances parallel but offset relative to one another and transverse to the flow direction. Flow path of the heat exchanger. The method of claim 21 or 22, A flow path for a heat exchanger, characterized in that the distance between two structural elements can vary within at least one column. The method of claim 21 or 22, The distance is the flow path of the heat exchanger, characterized in that 0 to 8mm. The method according to claim 19, 21, 22 or 24, The structural elements 13 of the individual rows 40 are offset by the amount f by each other in the flow direction P and the amount f is less than the depth T of the structural element 13. T is a flow path of the heat exchanger, characterized in that protrudes in the length (L) transversely by the flow direction (P). The method of claim 22 or 25, Said individual structural elements (13) of the row (41) are not formed in parallel and have different flow stop angles (α). The method according to claim 22, 25, 26, The flow path of the heat exchanger, characterized in that the individual structural elements (13) of the rows have different lengths (L1, L2). The method according to any one of the preceding claims, Said opposing rows (17, 18, 19, 20) having an offset in the flow direction (P) and smaller than the depth (T) of the columns (17, 19). The method according to any one of the preceding claims, The flow path of a heat exchanger, characterized in that some or all of the structural elements (13, 13 ') located in opposition to each other have a flow stop angle (α) in particular. The method according to any one of the preceding claims, The rows 23 and 24 are formed with empty spaces between the structural elements 13 located in one side row, and empty spaces are formed between the structural elements located in the other side row, and the flows of the heat exchanger are positioned to face each other. Route. The method according to any one of the preceding claims, Heat flow paths of heat exchangers, characterized in that the thermal structural elements facing each other are joined in particular by welding or soldering. The method according to any one of the preceding claims, Opposing rows of structural elements have the same depth (T) in said flow direction (P). The method according to any one of the preceding claims, Opposing heat of the structural element has a different depth (T1, T2) in the flow direction (P). The method according to any one of the preceding claims, The heat exchanger surfaces are located facing each other and in particular the structural elements are formed to be curved. The method according to any one of the preceding claims, The heat exchanger surfaces are located opposite each other and are a thermal engineering primary surface or secondary surface, the secondary surface being in particular a fin, a web or the like and preferably clamp, weld or A flow path of a heat exchanger, characterized in that the soldering. The method according to any one of the preceding claims, The height (h) is 2mm to 10mm, especially 3mm to 4mm and preferably 3,7mm flow path of the heat exchanger characterized in that the vicinity. The method according to any one of the preceding claims, The flow path is rectangular, in particular 5 mm to 120 mm and preferably 10 mm to 50 mm in width. The method according to any one of the preceding claims, The hydraulic diameter of the flow path is 3mm to 26mm and especially the flow path of the heat exchanger, characterized in that 3mm to 10mm. The method according to any one of the preceding claims, At least one particularly row of each structural element comprises a plurality of respective case structural elements. Especially in heat exchangers having flow paths of fluids in exhaust gas coolers in automobiles, At least one flow path has a shape as described in any one of the preceding claims. The method of claim 39, The flow path (1) is formed by a plate or rectangular tube (7) brazed or welded and the heat exchanger surfaces (F1, F2) are formed by plate tube walls. The method according to any one of the preceding claims, And the flow path is formed by a stacking plate or a disk having structural elements on top of each other. The method according to any one of the preceding claims, The structural element (10, 11) is formed in the tube wall (F1, F2) and in particular formed by a stamp. The method according to any one of the preceding claims, The exhaust gas flows through the tube (7) and the liquid coolant flows around the tube. The method according to any one of the preceding claims, The rows 8, 9 of the structural elements 10, 11 are spaced apart from each other with a distance s in the flow path and the flow path 7a is two to six times the length L of the structural element. Heat exchanger characterized by the above. The method according to any one of the preceding claims, Said heat of structural element (fluid 1) further comprises a row of structural elements protruding into fluid 2. The method of claim 45, The outwardly projecting structural elements support a stud, web or element and are in contact with each other or joined by welding or soldering. 47. The method of claim 45 or 46, And wherein the outwardly projecting structural element provides an improvement in thermal conductivity.

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