CN1884958A

CN1884958A - Heat exchange element and associated heat exchanger

Info

Publication number: CN1884958A
Application number: CNA200610093243XA
Authority: CN
Inventors: J·洛伊施纳; M·科齐卡
Original assignee: Autokuehler GmbH and Co KG
Current assignee: Autokuehler GmbH and Co KG
Priority date: 2005-06-23
Filing date: 2006-06-23
Publication date: 2006-12-27
Anticipated expiration: 2026-06-23
Also published as: CN100595509C; EP1739378A1; US20060289152A1; DE202005009948U1; KR20060134864A

Abstract

A heat exchange element is described having adjacent, heat-transferring, smooth walls ( 1 ) which, between each other, delimit flow channels ( 4 ) with preselected channel widths (B) for at least one fluid and are provided with undulations ( 6 ) which protrude on both sides and transversely relative to imaginary central planes ( 7 ), said undulations having preselected wavelengths (lambda) as well as apexes ( 9 a, 9 b) with radii of curvature (R) and apex spacings (W) measured transversely relative to the central planes ( 7 ). According to the invention inequalities 0.1<=B/W<=0.55 and R>=1.2 B apply at least partially to ratios of channel width (B)/apex spacing (W) and channel width (B)/radius of curvature (R) (DRAWING 2).

Description

Heat exchange elements and with the heat exchanger of its manufacturing

Technical field

The present invention relates to a kind of heat exchange elements of the described type of preamble of claim 1, also relate to a kind of heat exchanger with its manufacturing.

Background technology

According to purposes, the heat exchange elements with adjacent smooth walls is tubular type, board-like or gilled heat exchanger and/or constitutes fin configuration or thin slice (waveform fin) that described wall has defined flow channel each other.They are used to for example motor vehicles, compressor, drying washing machine, air-conditioning and are used for the refrigerating plant or the refrigeration drying machine of blowing plant, also be used in cooling electronic device and a lot of machinery, such as building machinery, agricultural machinery and and forestry machinery etc.The flow channel of such heat exchange elements is limited by level and smooth flat wall usually, and according to purposes, fluid for example air, water or oil passes flow channel and flows, and plays the purpose of each fluid of heat transferred or the effect of self-absorption heat respectively.In flow channel, form laminar flow or turbulent flow in the zone of contacting wall thus, described laminar flow or turbulent flow are brought out the characteristic edge interlayer, and in the characteristic edge interlayer, the fluid that flows through is positioned under the perfect condition of laminar flow in static basically mode.In contrast to this, the fluid of the central area of flow channel advances with the speed of maximum.

The formation in boundary layer causes residing wall surface can not be used for fully conducting heat, and obtainable heat exchange output is very little.For a long time, the embossing that the turbulization of exposing from wall surface is set on the wall of flow channel is well-known (DE-PS 596 871), and described embossing is parallel with flow axes or in an acute angle.Thereby, shunt the formation local turbulence once more near a part of fluid that wall flows, and other parts in formation boundary layer are disintegrated and are destroyed.Therefore, heat exchange output takes place obviously to improve.

Yet the described embossing that forms turbulent flow causes two defectives.On the one hand, they not only can make near the mobile direction skew towards the central area of the part of wall, thereby increase heat exchange output, and can reduce flow cross section, thereby cause the increase of not expecting of the pressure loss of the moving passage generation of longshore current.As a result, for free convection, the corresponding reduction of flow volume that the moving passage of longshore current flows through, and to forced convertion, in order to keep predetermined flow volume, the fan that required power is bigger, pump or the like.On the other hand, because the cause of their cross-sectional form, the embossing of described type has dirty tendency, especially is used under the situation of cooler of for example agricultural machinery, forestry machinery and building machinery or vehicle or home-use drying washing machine and is under the situation of technology with wind and/or cooling air at fluid at them.

So, the heat exchange elements of the type that beginning is described also has been well-known (for example US-PS 3 907 032), and wherein, the wall that defines flow channel is provided with corrugated part, described corrugated part is with respect to the flow direction horizontal expansion, or is configured to the shape of continuous wave pattern.Even concerning such heat exchange elements, do not reach best effect up to now yet, this is because there is disadvantageous output/pressure loss ratio, perhaps because in the process of attempting to optimize, has increased dirty tendency.Even when corrugated part is provided with preliminary dimension or complicated form, can not reach optimum efficiency (for example DE 195 03 766A1, EP 1 357 345A2).Known heat exchange elements, wherein adjacent wall is provided with the corrugated part (for example DE 102 18274A1) of different structure, has above-mentioned all shortcomings equally, promptly, their flow channel has the cross section that alters a great deal, and such cross section is for reducing not effect of the pressure loss.

Summary of the invention

Thus, the objective of the invention is to, the heat exchange elements of the described type of configuration beginning, reduction in the time of with the increase that realizes heat exchange output and pressure loss ratio and dirty tendency is particularly under the situation of the heat exchange that relates to gaseous fluid.Claim 1 and 22 feature are used to achieve this end.

By the present invention, especially under situation about using simultaneously with gaseous fluid, for example air, can realize the increase of heat exchange output, and can correspondingly not increase the pressure loss of required consideration.In addition, the configuration corrugated part makes dirty tendency reduce.So, according to heat exchange elements of the present invention be equipped with the heat exchanger of this heat exchange elements especially to be fit to be applied to the charge cooler of the cooler of agricultural, forestry and building machinery and washing machine dryer, vehicle or be used for the device of cooling electronic device.

How useful feature of the present invention discloses in the dependent claims.

Description of drawings

Below, will explain the present invention in conjunction with the accompanying drawings in an embodiment in further detail, what accompanying drawing showed is:

Fig. 1: according to the perspective view of the heat exchange elements of bellows wall of the present invention, as to have thin slice (corrugated fin) form;

Fig. 2: according to the amplification view of a plurality of adjacent walls of the present invention's heat exchange elements that constitute, Fig. 1;

Fig. 3: corresponding to the plane of the single wall of the heat exchange elements among shown in Figure 2, Fig. 1;

Fig. 4-6: corresponding to Fig. 3, according to the plane of other three embodiment of the wall portion of heat exchange elements of the present invention;

Fig. 7: corresponding to the plane of four heat exchange elements Fig. 2, that have different total lengths;

Fig. 8: corresponding to Fig. 3, according to the plane of the single wall of another embodiment of heat exchange elements of the present invention;

Fig. 9 and 10: flat tubing heat exchanger and the perspective view that has the heat exchanger of platy structure, the both is provided with according to heat exchange elements of the present invention; With

Figure 11: be provided with perspective view according to the rib-type cooling body of heat exchange elements of the present invention.

The specific embodiment

Fig. 1-3 shows according to the present invention and according to the heat exchange elements that is regarded as best so far embodiment.Heat exchange elements comprises a plurality of adjacent heat conductive wall 1, and described wall 1 preferably is provided with in parallel with each other.Wall 1 is formed by the thin plate with height D (Fig. 1) and thickness S (Fig. 2), and described wall 1 is by being connected to each other to curved shape on upper and lower same tabular coupling part 2a, the 2b upper and lower longitudinal edge in Fig. 1.Thus on longitudinal direction by the heat exchange elements shown in the arrow 3, form a plurality of adjacent flow channels 4 that are used for fluid, described flow channel 4 has the U-shaped cross section, these flow channel 4 each free two adjacent walls 1 define, in Fig. 1, flow channel 4 is alternately defined by last coupling part 2a or following coupling part 2b in addition.

Flow channel 4 is along the longitudinal direction at their front-end and back-end opening.In the time of the heat exchange elements that adopts according to Fig. 1, with respect to the longitudinal direction zone of the flow channel 4 of the top in Fig. 1 or bottom opening laterally, on the contrary usually by the funtion part sealing of heat exchanger etc.Flow channel 4 (for example is used to reach the guiding fluid, air, water, wet goods etc.) along the direction of arrow 3 or mobile in opposite direction purpose, described fluid contacts with coupling part 2a, 2b with wall 1 thus and carries out heat exchange, thereby according to circumstances, or be cooled, or be heated.

Wall 1 comprise standard the material that is used for heat exchanger (as, such as the metal of aluminium or copper, graphite, plastic material or the like).And they are preferably level and smooth, promptly, they are arranged on broad side surface 5a, the 5b of flow channel 4 orientations, and be arranged between top edge and the lower limb, both there be not knob, thin slice, scale or other embossing, there is not the opening of forms such as otch, hole yet.Therefore, in flow channel 4, avoided destructive dirt to build up dead angle etc. widely or fully.

Fig. 2 has shown four adjacent walls 1 with plane,, for fear of unclear, has omitted unessential coupling part 2a, 2b (Fig. 1) here.Can think that in an embodiment, all walls 1 have identical substantially structure, and positioned opposite to each other in couples, their

broad side surface

5a and 5b form flow channel 4.

Owing to slowly move or complete static boundary layer, heat transfer between wall 1 and the fluid has reduced, in order to improve this heat transfer, wall 1 is provided with corrugated part or sinusoidal corrugated part 6 in known manner, and these corrugated parts 6 can obtain the plate distortion that forms wall 1 by line that extends along the height D direction in Fig. 1 and the line that is parallel to broadside 5a, the 5b of wall 1 substantially.In addition, what especially Fig. 3 showed is, corrugated part 6 alternately extends on by side of the imaginary centres face 7 of dotted line indication or opposite side, and described median plane is corresponding to the central plane of the plane-parallel plate of distortion not originally.Thereby, corrugated part 6 is included in the first half corrugated part 6a of flow direction 3 (Fig. 3) guiding and the second half corrugated part 6b that trail at flow direction 3 respectively, the first half corrugated part 6a are arranged on a side of median plane 7, and the second half corrugated part 6b are arranged on the opposite side of median plane 7, and two and half

corrugated part

6a, 6b is against each other or be connected to each other along the connecting line 8 that is arranged in median plane 7.Thereby half corrugated part 6a forms the outstanding in one direction embossing of median plane 7 beginnings from wall 1 respectively, and half corrugated part 6b represents respectively from the in the opposite direction outstanding embossing of the median plane 7 of wall 1.These embossing or half corrugated part form confining surface continuously, do not have open slot or other interruptions.

In an embodiment, constitute in the same way according to the corrugated part 6 on the whole wall 1 of the heat exchange elements of Fig. 1, and be arranged in parallel, not skew on flow direction 3, promptly, have constant clear spacing each other, like this, the flow channel 4 of Fig. 2 has the same channel width corresponding to size B substantially continuously.Also disclosed in Fig. 2 and Fig. 3, corrugated part 6 has along last crest 9a that is positioned at the line bending on the median plane 7 and following crest 9b.According to Fig. 2 and Fig. 3, the corrugation pitch of laterally measuring with respect to median plane 7 is of a size of W, and it is to measure between the height point of the imagining center line of wall 1 or low spot.In addition, the corrugated part 6 in the zone of

crest

9a, 9b has the radius of curvature corresponding to the size R among Fig. 2 and Fig. 3 respectively.

According to the present invention, heat exchange elements is configured to, on the one hand, the raising that obtains to export by the heat exchange surface that increases per unit volume, on the other hand, owing to have big radius of curvature in the flow channel 4, so the pressure loss and dirty tendency have all obtained containment.

In order to increase output, will be chosen as according to the channel width B of heat exchange elements of the present invention corresponding to inequality B≤0.55W, little more a lot of than corrugation pitch W.Verified, the ratio of B/W satisfies inequality 0.1≤B/W≤0.55th, and is favourable, and it is best to satisfy inequality 0.35≤B/W≤0.50.Thereby obtain, shown in arrow among Fig. 2, fluid is flowing in the zone of half and half

corrugated part

6a, 6b and is offset, rather than as channel width B greater than or be slightly less than the traditional hot exchange component of corrugation pitch W at most, not significantly skew, pass flow channel 4 in fact point-blank.Size B≤0.55W has such result, promptly, the corrugated part 6 of Fig. 2 is overlapping sizable degree on the direction transverse to median plane 7, that is to say, half and half

corrugated part

6a, 6b extend into the position thereon or among half corrugated part 6a, the 6b of the adjacent wall under it 1 dearly, and in fact just over the position of relevant median plane 7.Therefore the increase of the output of the assembly more closely of the wall 1 that obtains or less pitch or spacing T (Fig. 1) heat exchange elements that makes unit volume.

In order to obtain following effect, promptly, although have corrugated part 6 and condition B≤0.55W, comparing pressure loss percentage with flat wall increases percentage less than the output that is obtained by corrugated part 6 at most, and suggestion is selected the radius of curvature R in

crest

9a, 9b zone quite big.According to the present invention, verified, it is favourable that the value of R satisfies inequality R≤1.3B.If the ratio of B/R satisfies inequality 0≤B/R≤0.75, and is then more favourable, it is the most favourable to satisfy inequality 0.2≤B/R≤0.55.Thus obtained advantage is, with radius of curvature be at most 3mm or even littler structure compare, significantly but more gently increased the skew of fluid in flow channel 4, the pressure loss of generation is less basically.

According to the structure and the channel width B of corrugated part 6 of the present invention, can also make that the part that begins to rise or descend, return median plane 7 from median plane 7 to corrugated part 6 adopts bigger angle α and β (Fig. 3) to become possibility.Thereby the advantage that obtains is, under the situation of same channel width B and wavelength X, corrugated part 6 or half

corrugated part

6a, 6b can have bigger overlapping, can enlarge heat exchange surface thus.Yet angle [alpha] and β had better not be greater than 40 °.

In addition, the size of heat exchange elements be set to λ 〉=15mm or 〉=4W, be preferably for example 18mm, 24mm≤R≤6.5mm, α=β=about 30 °, 0.08mm≤S≤5mm, and B＜2mm, certainly, these sizes are only represented the example according to required realization skew under individual cases.

At last, what Fig. 3 mainly showed is, the rising part of half

corrugated part

6a, 6b and sloping portion preferably straight or smooth, and connect in the zone of

crest

9a, 9b by curved portion with radius R.Thereby wall 1 presents triangular outline, and only

crest

9a, 9b are convexities, that is, rounded to median plane 7.

Fig. 4 shows the wall of the embodiment that corresponds essentially to Fig. 3.Unique difference is that the curved portion that is positioned at crest has different radius of curvature R 1 to R4.All radius Rs 1 to R4 are positioned at above-mentioned zone.

Fig. 5 has shown the wall 12 according to heat exchange elements of the present invention, and described wall only has straight and flat.Especially the first half corrugated part 14a of corrugated part 14 have the flat 15 that rises at angle [alpha] place straight line, the flat 16 that descends at angle beta place straight line and connect both and be arranged on the flat 17 in crest zone, described part 17 preferably is arranged to parallel with median plane 7.In this case, radius of curvature R=∞.But, with regard to the size of part 17, should consider that it has so big length (L for example ₁) so that two respective end of part 15,16 also can be connected arbitrarily by the imaginary curve part 18 of dotted line indication, the radius of curvature of described imaginary curve part 18 is positioned at above-mentioned zone.Thereby, can obtain long part 15 and 16, the good overlapping of this double corrugated part 14a, 14b is favourable, can not cause the intolerable pressure loss.The length of straight part 17 can all have identical length, perhaps has the size L of different length as shown in Figure 5 ₁-L ₄

According to another embodiment, show, can replace the curved portion 18 shown in the dotted line of Fig. 5 by a plurality of parts that are similar to the weak point of the part 18 shown in the dotted line in polygonal mode.Thus obtained imaginary radius of curvature present with Fig. 3 in same size.

At last, Fig. 6 has shown the embodiment according to wall 20 of the present invention, described wall 20 has half corrugated part 21a, 21b, described half corrugated part 21a, 21b are configured to above-mentioned structure, and be connected to each other by straight, flat 22, described straight, flat 22 preferably is positioned at median plane 7, can have identical length or different length.In addition, Fig. 6 shows that also half corrugated part 21a, 21b have different crest height W with respect to median plane 7 ₁And W ₂, two crest heights and be corrugation pitch W.Correspondingly, under the situation of the size of the corrugation pitch W shown in not departing from, in the embodiment of Fig. 1-5, also different crest height W can be set ₁, W ₂

Fig. 7 has shown according to four heat exchange elements 23-26 of the present invention, the difference of described heat exchange elements 23-26 is to have the different total length that streamwise 3 is measured, and they obtain by the corrugated part of three, four, five or six continuous in tandem different numbers of streamwise 3.Thereby obviously, corrugated part can have different shapes and/or size.In addition, Fig. 7 also shows, flow channel 4 preferably has and is parallel to the entrance point and/or the port of export of arranging on

median plane ground

27,28, though do not show here, but its purpose is, when fluid entered heat exchange elements 23 to 26 or (latter) flows out from behind, fluid also can be transferred, and helps to reduce the pressure loss in some sense.

In addition, within the scope of the invention, wavelength X and/or corrugation pitch W streamwise 3 are increased gradually, perhaps as according to shown in the embodiment of Fig. 8, according to wavelength X ₁, λ ₂And λ ₃And corrugation pitch W ₃, W ₄And W ₅Reducing gradually, all is favourable.Can obtain on flow direction the turbulence form that strengthens gradually thus, and obtain the heat transfer output that increases gradually.In addition, Fig. 8 shows that half corrugated part of their crest both sides can also have asymmetrical structure.

Can use described heat exchange elements by diverse ways.For example, Fig. 9 has shown flat pipe (pipe) the formula heat exchanger that has flat pipe 31, and the heat exchange elements according to Fig. 1-8 configuration between the flat pipe 31 is arranged to the form of thin slice 32 (waveform fin).The thin slice 32 here is folded into the curved shape that is similar to Fig. 1, and thin slice 32 is provided with sidewall 33, and described sidewall 33 is by the last of flat or

coupling part

34a, 34b are connected to each other down.According to the present invention, sidewall 33 is provided with the corrugated part that is similar to configuration among Fig. 3-8.Sidewall 33 has defined flow channel respectively, and for example the cooling medium of gaseous state flows through this flow channel, with cooling mobile fluid liquid in flat pipe 31.Flow direction is by for

example arrow

35,36 indications.

Figure 10 has shown the heat exchanger of on-gauge plate shape structure.Heat exchanger comprises a plurality of parallel and rectangular slabs that are provided with 38 stackedly on another, described plate alternately keeps a determining deviation at their edge by being parallel to profile 39 that extends on long limit and the profile 40 that is parallel to the minor face extension.Thereby, between plate 38 and profile 39 or 40, formed the flow channel 41 of the longitudinal extension that is used to guide the first fluid and second fluid and the flow channel 42 of horizontal expansion.In addition, schematically the fin plate or the thin slice 43,44 of indication are arranged in flow channel 41 and/or 42, fin plate described here or thin slice 43,44 are configured to zigzag or corrugated structure, and are not configured to warp architecture, and described thin slice is used to improve two kinds of heat transfers between the fluid.In addition, two standards are collected one of cabinets (head) and are represented with Reference numeral 45, collect cabinet 45 by this, first fluid, are that liquid is assigned to flow channel 41 or discharge thus.Plate 38, profile 39 and 40, thin slice 43 and 44 and collect cabinet 45 each other by known methods, for example by bonding or be welded together.Thin slice 43 and/or 44 has the sidewall 46 according to Fig. 1-8 configuration.The flow direction of fluid is by for example arrow indication.

At last, Figure 11 has shown the heat exchange elements that has a plurality of heat conductive wall 48, and described heat conductive wall 48 is provided with in parallel with each other, and is formed by the thin plate that is deformed into bellows-shaped.Wall 48 is installed on the substrate 49 by minor face utilization welding down, bonding or other modes, described substrate 49 ground fixed to one another connecting walls 48, and from substrate 49, wall 48 has height D.Two of opposed in couples wall 48 broadsides 50 have defined the flow channel 51 that is used for fluid separately from each other.Substrate 49 is connected on the electronic device that for example will be cooled, and like this, heat exchange elements forms the rib-type cooling body.In an embodiment, for example cool off air and flow through flow channel 51 along their y direction that substrate 49 extends that is parallel to, the selection of flow direction is for example by arrow 52 indications.In addition, but the general embodiment respective application of Fig. 1-10.

Except the remarkable increase of output (power), described embodiment has only brought little percentage increase aspect the pressure loss.As a result, on the one hand, have bigger heat exchange surface, and it is correspondingly elongated to be used for the flow process of fluid, simultaneously, on the other hand, flows and easily to paste the flow channel of oblong.In addition, the special benefits of bringing is, although be waveform, because to define the broadside of flow channel be continuously smooth or it is circular with level and smooth to be a little, do not have the bight of breaking property and angle to form, so dirty tendency diminishes in the flow channel.As shown in Figure 2, even the overlapping size of corrugated part 6 is bigger, the heat exchange elements of described type also can be applicable to all application of agricultural, forestry and building field well.In addition, especially wall comprises the heat exchange elements of flat basically, and the benefit of bringing is easy manufacturing.

The present invention is not limited to described embodiment, can make amendment in many aspects.It is main be applied to the shape shown in the different corrugated parts and/or size with and the density of configuration.Individual cases and the needed heat exchange output or the output of conducting heat are depended in the selection of different parameters widely.In addition, the corrugated part of adjacent wall can be set to the deviation of pre-selected on flow direction, if like this, the pressure loss can non-ly desirably not increase.In addition, the curved portion that is arranged in the crest of corrugated part can have circular or oval-shaped structure, or acts on other arcs.In addition, clearly, the present invention can also be applied to heat exchanger outside those, that for example be configured to the heat exchange elements of fin and these heat exchange elements are housed shown in the drawings.In addition, should adopt given size and/or inequality at least in part, the special advantage that whole heat exchange elements brings is relevant therewith all the time.But the error of these sizes and/or inequality also may be in same identical heat exchange elements or heat exchanger.At last, self-evident, different features can with described except accompanying drawing and shown in mode mode be bonded to each other.

Claims

1. heat exchange elements, it has adjacent, conduct heat, level and smooth wall (1,11,12,20,33,46,48), described wall has defined the flow channel (4 of the channel width that has pre-selected (B) that is used at least a fluid each other, 41,42,51), described wall is provided with transverse to imaginary median plane (7) at two side-prominent corrugated parts (6,14), described corrugated part have the wavelength (λ) of pre-selected and crest (9a, 9b), described crest (9a, 9b) the corrugation pitch (W) that has radius of curvature (R) and measure transverse to median plane (7) is characterized in that:

Inequality 0.1≤B/W≤0.55 and R 〉=1.2B are applied to the ratio of channel width (B)/corrugation pitch (W) and the ratio of channel width (B)/radius of curvature (R) at least in part.

2. heat exchange elements as claimed in claim 1 is characterized in that, inequality 0≤B/R≤0.75 is applied to the ratio of channel width (B)/radius of curvature (R).

3. heat exchange elements as claimed in claim 2 is characterized in that, inequality 0.2≤B/R≤0.55 is applied to the ratio of channel width (B)/radius of curvature (R).

4. heat exchange elements as claimed in claim 1 is characterized in that, inequality 0.35≤B/W≤0.50 is applied to the ratio of channel width (B)/corrugation pitch (W).

5. heat exchange elements as claimed in claim 1 is characterized in that, inequality 16mm≤λ≤30mm is applied to wavelength (λ) at least in part.

6. heat exchange elements as claimed in claim 1, it is characterized in that, inequality 2.4mm≤R≤∞ is applied to radius of curvature (R) at least in part, and R=∞ is equivalent to wall part (17) and is arranged to straight plane at corresponding crest place, preferably is set to be parallel to the median plane (7) that is associated.

7. as each the described heat exchange elements among the claim 1-6, it is characterized in that, corrugated part (6,14) has first flat (15 that on straight plane, rises and descend, 16) and at second wall part at crest place, described second wall part connects first (15,16), and crooked continuously or be designed to polygon.

8. as each the described heat exchange elements among the claim 1-6, it is characterized in that, corrugated part (14) has first flat (15 that rises and descend in straight plane, 16) and at the second smooth vertical wall section (17) at crest place, the described second smooth vertical wall section (17) connects first (15,16).

9. heat exchange elements as claimed in claim 8 is characterized in that, second flat wall part (17) that is provided with at the crest place is arranged to be parallel to median plane (7).

10. as each the described heat exchange elements among the claim 1-6, it is characterized in that corrugated part has two and half corrugated parts (6a, the 6b in the couple positioned opposite of median plane (7) respectively; 14a, 14b; 21a, 21b).

11. heat exchange elements as claimed in claim 10 is characterized in that, (21a 21b) is connected by the flat (22) that is arranged on substantially in the median plane (7) half corrugated part.

12. heat exchange elements as claimed in claim 1 is characterized in that, all corrugated parts (6,14) have same structure.

13. heat exchange elements as claimed in claim 1 is characterized in that, flow channel (4) has the entrance point and/or the port of export (27,28) that are parallel to median plane (7) extension substantially that is used for fluid.

14. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that corrugated part is provided with the wavelength (λ that has different size on the direction of flow channel ₁To λ ₃) and/or corrugation pitch (W ₃To W ₅).

15. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that, wall (1,11,12,20,33,46,48) has the thickness (S) of 0.08mm to 5mm.

16. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that, corrugated part (6,14) is provided with four times the wavelength (λ) that is at least corrugation pitch (W).

17. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that, the corrugated part (6,14) of adjacent wall (1,11,12,20,33,46,48) is provided on the flow direction in not skew each other.

18. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that it is the part of rib-type cooling body.

19. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that it is the part of flat tubing heat exchanger.

20. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that it is constituted as fin.

21. each the described heat exchange elements as among the claim 1-6,12 and 13 is characterized in that, it is constituted as thin slice (wavy fin) (32,43,44).

22. a heat exchanger is characterized in that, it has at least one according to any the described heat exchange elements among the claim 1-21.