KR20190000288A - Device for heat transfer - Google Patents

Abstract

The present invention relates to a heat transfer device (1) for transferring heat between a first fluid and a second fluid. The device (1) includes: one or more pipe bottoms (5) having pipe elements (3, 3a, 3b, 3c), through which the first fluid passes, and a through opening (6); and an arrangement including one or more sealing elements (7) having a through opening (8). The pipe elements (3, 3a, 3b, 3c) include flat pipes each having a first area (10) having a first height (X) and a width (W), and one or more second areas (11) which is arranged at ends of the pipe elements (3, 3a, 3b, 3c) and has a support surface (13) having a second height (Y). The sealing element (7) is arranged between an edge of a periphery of the through opening (6) of the pipe bottom (5) and the support surface (13), and has a specific wall thickness (G). The pipe elements (3, 3a, 3b, 3c) having wide sides are arranged in parallel to each other and are spaced apart from each other in the first area (10). Webs (5-1) having a height (H) are provided between the through openings (6) arranged to be adjacent to the pipe bottom (5). The deformation degrees of the ends of the pipe elements (3, 3a, 3b, 3c), which are positioned in a range from a maximum value (CM_max) to a minimum value (CM_min) in the height direction (c) are set in advance with reference to a size relationship.

Description

TECHNICAL FIELD [0001] The present invention relates to a heat transfer device,

The present invention relates to a heat transfer device, particularly for use in automobiles. In this arrangement, the heat is preferably transferred between a coolant as a first fluid, for example a water or water-glycol mixture, and air as a second fluid. The apparatus comprises a pipe element for passing a first fluid, and an assembly comprising at least one pipe bottom and at least one sealing element each having a through opening for passing a pipe element therethrough.

The coolant-air-heat exchanger known in the art for transferring heat from the coolant circulation system to ambient air is used in a so-called hot coolant circulation system for releasing the heat of the combustion engine. The coolant-air-heat exchanger formed from aluminum has a small number of pipes, multi-discs and side elements fixed in the bottom of the pipe, and the coolant collector arranged on the crimp connection has various components to be assembled for heat exchange. Pipes arranged in parallel and arranged as a matrix are used to guide the liquid coolant between the collectors. The coolant collectors arranged on both sides of the pipe ends are sealed to the pipe and pipe bottoms by means of an ethylene-propylene-diene-rubber-sealing element, briefly referred to as EPDM-seal, according to conventional methods. The pipe, the pipe bottom, the multi-disk and the side elements are completed in a completely soldered condition as a so-called slot cooler in the plugging method, or are completed in a fully soldered condition as a so-called braze cooler.

In the case of using the soldering method in a controlled atmosphere, which is briefly referred to as CAB ("Controlled Atmospheric Brazing"), the matrix of pipes and multi-discs is connected to each other and possibly to the bottom of the pipe as a metallic element of the collector . In the plugging method, welding or soldering of neighboring metal parts is avoided, using a mechanical assembly of the collector and a matrix, briefly referred to as a mechanical assembly (MA).

Air that absorbs heat from the coolant flows from the outside surface of the pipe, thereby flowing along the pipes. A multi-disc or rib arranged between the pipes at the outer surface is used for expansion of the air side heat transfer surface and is thus used to increase the heat exchanger output.

The known coolant-air-heat exchanger has an unsatisfactory durability against the rapidly changing temperature of the coolant. Thus, the coolant-air-heat exchanger can be cooled to temperatures in the range of -20 ° C to -10 ° C in extreme applications and the temperature of about 120 ° C due to the rapidly opening valve in the coolant circulation system Lt; / RTI > At this time, the coolant-air-heat exchanger experiences a very intense temperature change and experiences a thermal shock. A very large material stress appears due to the time-displaced thermal expansion of the individual pipes.

The slot cooler has a very high resistance to temperature changes of the coolant due to the sliding bearing-connection between the pipe as the element of the collector and the bottom of the pipe, but because of the forced connection between the pipe and the multi- . The brazing cooler has a limited durability against temperature changes due to the rigid solder connection between the pipe and the bottom of the pipe and again against the thermal expansion of the individual pipes caused thereby.

DE 10 2015 113 905 A1 discloses a heat exchanger having a mechanically mounted collector for use in a motor vehicle, in particular a method for manufacturing and mounting an air flow-heat exchanger, and such a heat exchanger. The heat exchanger includes a matrix mechanically bonded from a plurality of metal pipes and a plurality of metal ribs arranged in parallel. The pipe has a heat transfer section having an intimate cross-sectional shape with two longer sides and a shorter side facing each other. In order to provide a seal and allow relative movement between the mechanically connected pipe and the first collector due to the thermal expansion and contraction of the matrix, the one or more pipes may extend in the first end section by a first end section of the pipe RTI ID = 0.0 > 1 < / RTI >

In this case, by means of the method in which the pipe and the multi-disc are soldered without a pipe bottom, and then the bottom of the pipe is inserted into the pipe in a sealed state through a press fit, The synergy of the manufacturing methods is described. Due to the reduced material properties due to the provision of temperatures in excess of 600 [deg.] C during soldering in the soldering oven, the pipe is subjected to a sealing by the press pit, in particular in the end regions, So that it can not withstand permanently the resistance provided by it.

Conventional pipes of heat exchangers used in automobiles, especially pipes made of aluminum alloys, often can not withstand the sealing pressure acting on the walls of the pipes after compression of the seals between the pipes and the bottom of the pipes. In this case, heat exchangers known in the prior art and methods for manufacturing such heat exchangers are limited to the use of pipes having a width or pipe depth of up to approximately 11 mm, in particular welded pipes, . The seal must be compressed in the range of 10% to 50% over the entire circumference of the pipe on one side, in which case the compressed seal will not be supported by the pipe, Causing the wall to collapse. On the other hand, the compression of the seal lies in the central region of the pipe wall, i. E. In the region of the pipe crown, often below the aforementioned target value.

It is an object of the present invention to provide a device for efficiently transferring heat between two fluids, in particular, between a liquid fluid as a coolant and air, and also to configure such devices as intended. At this time, the heat exchanger must have a sufficient and uniformly compressed state of the seal portion and a maximum sealing state, that is, a high thermal shock endurance, over the entire circumference of the pipe, even if the temperature change is large. With heat exchangers, the maximum heat output must be delivered at minimum structural size or at minimum installation space demand. The heat exchanger must also have a minimum weight and must cause minimal manufacturing and material costs.

This problem is solved by objects having the features of the independent patent claims. Improvements are specified in the dependent patent claims.

This problem is solved by an apparatus according to the invention for transferring heat between a first fluid and a second fluid. The apparatus comprises an assembly of pipe elements for passing a first fluid, the pipe comprising at least one pipe bottom having a through opening and at least one sealing element having a through opening.

The pipe elements arranged in a state of passing through the through openings respectively have a first region having a first height X and a width W and a second region having a second height Y, And a flat pipe with one or more second regions arranged at one end of the pipe element.

Thus, each of the pipe elements has a heat transfer area in which the pipe element is circulated by the second fluid, in particular air, by the first area, and preferably has an area connected to the pipe bottom by the second area.

The sealing elements are each arranged between the support surface of the pipe element and the edge of the edge of the through opening of the pipe bottom and have a specific wall thickness G. [ By means of the intermediate supported sealing element, one or more pipe bottoms with through openings are fluid-tightly connected with the pipe elements. The through-openings of the pipe bottom and of the sealing element correspond to each other in shape and conform to the external shape of the pipe element. In this case, preferably one pipe element is present with each passing through the through opening, so that exactly one through opening is assigned to each end of the one pipe element.

The pipe elements are arranged with a wide side, parallel to each other and at an interval F with respect to each other in the first region. Between the through holes arranged next to each other on the bottom of the pipe, there can also be provided one web each having a predetermined height (H).

According to the inventive concept, the expansion in the first region of the pipe element, which consists in the height direction, consisting of the first height X of one pipe element and the spacing F of neighboring pipe elements, The second height Y of the pipe element, the height H of one web of the pipe bottom and twice the wall thickness G of the sealing element, in this case, The following equation applies:

이다. 최소값(

)에서는, 파이프 요소의 파이프 단부들이 적어도 높이 방향으로 형상 파괴되지 않았거나 변형되지 않았다.In the above equation, CM represents the degree of deformation of the end portion of the pipe element in the height direction, and lies in an area between the maximum value (CM _max ) and the minimum value (CM _min ). If the value of the first height X of the pipe element is equal to the value of the second height Y, CM _min corresponds to twice the wall thickness G of the sealing element,

to be. Minimum value (

), The pipe ends of the pipe element were not deformed or deformed at least in the height direction.

In particular, by defining the deformation limit CM _max as the maximum value and by defining the deformation limit CM _min as the minimum value, the CM as a parameter is defined by the fact that the CM is a solid and reliable seal of the pipe element around the perimeter- Of the end of the pipe element.

The pipe element may preferably be formed of a metal. The cross-section of the pipe element preferably extends within the second region in a plane perpendicular to the longitudinal direction.

According to an improvement of the invention, the flow cross-sections of the pipe elements are each limited by two sides facing each other, these sides forming a narrow side or a longitudinal side of the flow cross-section, respectively.

According to an alternative first embodiment of the invention, the sides of the pipe elements arranged next to each other are aligned at right angles to each other at the contact edges progressing in the longitudinal direction. In this case, the contact edges are each provided with a rounded transition having a corner radius (R).

The first height X of the first area of the pipe element is preferably greater than the value of the double corner radius R of the pipe element. In this case, the maximum value (CM _max )

Where A describes the ratio of the circumference of the pipe element at the end of the pipe after deformation of the periphery of the pipe element at the pipe end before deformation. The geometry and material properties enable maximum deformation, particularly expansion, of the pipe ends until deformation along the tensile limit of the material of the pipe element causes material cracking.

According to an alternative second embodiment of the present invention, the side surfaces arranged respectively on the longitudinal side of the flow cross-section of the pipe element are bent outwardly in the form of a semicircular hollow cylinder, It is connected.

The first height X of the first region of the pipe element corresponds to a double radius R of the side of the narrow side of the outwardly bent pipe element, preferably in the form of a half-circle hollow cylinder. In this case,

(CM _max ), where A corresponds to the pipe expansion capacity.

One advantage of the present invention is that when the cross-section of the second region of the pipe element in a plane vertically aligned with respect to the longitudinal direction is expanded, the flow channels defined by the walls of the respective pipe elements are shifted from a substantially rectangular cross- Sectional shape.

According to an improvement of the invention, the pipe element has a wall thickness of 0.22 mm, a first height X of about 2.5 mm and a width W of about 10.8 mm in the first region, Has a second height (Y) of about 4.69 mm and a width of about 10.95 mm.

According to another preferred embodiment of the present invention, the pipe elements at the end of the pipe are each formed in an expanded state starting from the front at the area of the vertex of the longitudinal side, As shown in Fig. Thus, the pipe elements are formed with shapes in the regions of the apexes of the upper and lower surfaces, respectively. At this time, the pipe element preferably has an extension of approximately 7.6 mm in the maximum extension area of the forming part in the height direction.

According to a preferred embodiment of the invention, the bottom of the pipe may each comprise a ring element for at least locally reducing the open cross-section of the through-opening for receiving the sealing element in the region of the web.

In another preferred embodiment of the present invention, the bottom of the pipe can be formed as a sidewall element of the collector of the heat transfer device.

The heat transfer device may be formed with two sealing elements, preferably with two pipe bottoms with through openings and through openings. The pipe bottoms are each connected in a fluid-tight manner with the pipe elements, in which case the through-openings coincide with the external shape of the pipe element in each shape, and each pipe element passes through a through- And having a first end and a second end passing through a through opening formed in the bottom of the second pipe.

The pipe elements are preferably formed in a straight line and preferably of an aluminum alloy.

According to one improvement of the invention, the pipe elements are arranged in a row or in a plurality of rows within the arrangement.

The row of pipe elements of the device according to the invention, arranged side by side and parallel to one another and with a wide side relative to one another, are preferably arranged such that the flow of the second fluid, in particular the air, between directly adjacently arranged pipe elements Path are formed one by one.

Within the flow path formed within the first region by the adjacently arranged pipe elements are preferably arranged a multi-disc or rib for changing the flow cross-section and / or for enlarging the heat transfer area. In this case, the MD has an extension in the height direction, which corresponds to the spacing F of the adjacent pipe elements. The multi-disc or rib is preferably formed of an aluminum alloy.

The preferred embodiment of the present invention makes it possible for the heat transfer device according to the invention to be used as a coolant-air-heat exchanger in the coolant circulation system of an automobile, in particular in the engine coolant circulation system.

In summary, the heat transfer device according to the present invention has the following various advantages:

- The use of CAB / MA-manufacturing principles within the existing pipe portfolio framework is expanding,

- Maximum thermal output is delivered by the optimal geometric ratio if the structure size is minimal or the space requirement is minimal, ie the ratio of deliverable heat output to open volume is optimal,

- Reduced complexity and material costs, which reduces manufacturing costs,

- with a minimum weight,

- High sealability, that is, high thermal shock resistance and high resistance to temperature change, even when the temperature change is large. As a result, if the connection between the pipe element, the sealing element and the bottom of the pipe is flexible, , In particular the large opening and closing speeds of the valves in the coolant circulation system,

- It is guaranteed to be used even if the pressure pulsation load is high,

- Maximum life is guaranteed by permanently ensuring the connection of the pipe bottom and the end of the pipe inside the sealing element, by press pits which perform a uniform sealing compression at the specified level.

Further details, features and advantages of embodiments of the present invention will be apparent from the following detailed description of embodiments of the invention, made with reference to the accompanying drawings. here:
Figure 1 shows a heat transfer device with disassembled detail, with a multi-disc supported as a separate component, a pipe bottom and a pipe element arrangement with a sealing element and collector,
2A shows a side view of a pipe element formed as a flat pipe with a first region and a second region,
Figures 2b and 2d show a pipe element in perspective view, each having a different flow cross section and formed as a flat pipe,
Fig. 2c shows a detailed view of the pipe element shown in Fig. 2b,
Figure 3a shows a side detail view of an arrangement of a pipe element with an intermediate supported multi-disc of the heat transfer device shown in Figure 1,
Fig. 3b shows a side cross-sectional view of an arrangement of pipe elements having a sealing element of the heat transfer device shown in Fig. 1 and an intermediate supported multi-disc,
3C shows a detail view of the pipe bottom with the sealing element shown in Fig. 3B,
4A and 4B are partially enlarged at the pipe end and show a pipe element with an elliptical cross section similar to the pipe element shown in Fig. 2A in a perspective view and a plan view,
Figs. 4C-4F show in perspective and plan view the finally enlarged pipe element at the pipe end, shown in Figs. 4A and 4B,
Figures 5a and 5b are partially enlarged at the end of the pipe and show in a perspective and plan view a pipe element having an elliptical cross section similar to the pipe element shown in Figure 4a,
Figure 6a shows a side cross-sectional view of the arrangement of the pipe elements shown in Figure 5a in the through opening of the pipe bottom with the sealing element,
6B shows a detail view of the pipe bottom with the sealing element and the pipe element shown in Fig. 6A.

1 shows a pipe element 3, in particular a flat pipe arrangement 2, having a pipe bottom 5 and a sealing element 7 of a heat transfer device 1. In Fig. This figure shows a heat transfer device 1 with a multi-disc 4 intermediate supported as individual components, a pipe bottom 5 and an arrangement 2 of pipe elements 3 having a sealing element 7 and a collector 9 (1) is shown in detail. The collector 9 is also referred to as a coolant collector when the coolant is used as a fluid.

The arrangement body 2 made up of the flat pipe 3 is formed in one row or in a plurality of rows in accordance with the output requirement and is adjustable in terms of size, in particular, in terms of length or width. The pipe elements 3 are arranged in two rows.

By arranging the pipe elements 3 arranged side by side and in parallel to one another in a row with a wide side, the result is a flow path for the fluid, in particular for air, between directly adjacent pipe elements 3 Respectively. At this time, the flow path proceeds between the pipe elements 3, respectively. A row of pipe elements 3 are arranged in a straight line with respect to each other and extend between two collectors 9, respectively. The inner volume of the pipe element (3) is connected to the inner volume of the collector (9).

Within the flow path and in the intermediate space of the adjacent pipe element 3 there is formed an element for changing the flow cross-section and / or for enlarging the heat transfer area. A multi-disk (4) is provided as an element for changing the flow cross-section and / or for enlarging the heat transfer area. Alternatively, ribs may be used. Like the pipe element 3, the multi-disc 4 is preferably formed of a material having excellent thermal conductivity, such as an aluminum alloy.

In the assembled state of the device 1, on the front face or on the narrow side of the arrangement body 2 there is provided a pipe bottom 5 which can also be used as a sidewall element of the collector 9, respectively. In this case, the side on which the end of the pipe element 3 is aligned is referred to as the front face. The pipe bottom 5 is formed as a deep drawing part, perforation or hydroforming part, which is in the form of a substantially rectangular sheet of metal, in particular an aluminum alloy. In this case, the sheet is understood to be a flat mill finished product made of metal. Hydroforming, also referred to as high-pressure deformation, is considered to deform the sheet in a closed mold tool, using the pressure generated in the tool by the water-oil-emulsion.

The sealing element 7 as well as the pipe bottom 5 with rounded edge areas has through openings 6, 8 for receiving the pipe element 3. The through openings 6 of the pipe bottom 5 and the through openings 8 of the sealing element 7 meet to form a fluid tight connection between the individual pipe element 3 and the pipe bottom 5, And also conforms to the external dimensions of the element (3). And a web 5-1 is formed between the through openings 6 of the pipe bottom 5, respectively.

The pipe bottoms 5 arranged on the side facing each other of the collector 9 are fixedly connected to the pipe element 3. The fixed connection can be regarded as a technically sealed zero-leak due to the sealing element 7, respectively. The pipe bottom 5 is arranged on the arrangement 2 perpendicular to the pipe element 3 on the narrow side of the pipe element 3.

2a shows a pipe element formed as a flat pipe (not shown) having a first undeformed region 10 as a heat transfer region and a second undeformed region 11 as a deformation region, 3) as a side view. The regions 10 and 11 of the pipe element are formed to be connected to each other when viewed in the longitudinal direction (a).

The pipe element 3 is at least partially expanded and deformed at the end of the pipe. The cross section of the flow channel surrounded by the wall of the pipe element 3 is constant and constant between the first region 10 in which the pipe element 3 is circulated by the fluid and the second region 11 towards the pipe end, And is uniformly enlarged. In the regions 10 and 11, the cross-sectional areas of the flow channels are constant. The second area 11 of the pipe element 3 is used as a supporting surface for the sealing element 7 which is preferably formed flat, that is to say without a structure such as a notch or a groove.

In the unmodified first region 10 the pipe element 3 has an external extension X which is also referred to as the height X of the first region 10 when viewed in the height direction c do. The second region 11 of the at least partially expanded pipe element 3 is defined by an external extension Y which is also referred to as the height Y of the second region 11 in the height direction c Respectively. The widths of the pipe elements 3 extend in the depth direction b, respectively.

2b and 2d, pipe elements 3a, 3b, each formed as a flat pipe with a different flow cross-section, are shown in perspective view. In these figures, one end face of the first undeformed region 10 of the pipe element 3a, 3b is shown respectively. The flow cross-section extends in the plane defined by the depth direction (b) and the height direction (c).

The flow cross-sections are each confined by two opposing sides, each of which forms a narrow side or a longitudinal side of the flow cross-section. The sides formed to face each other in pairs have the same dimensions. In this case, the narrow sides as the first pair in the height direction c have the same height X, while the longitudinal sides as a second pair in the depth direction b, aligned parallel to each other, And has the same width (W).

The substantial difference in Figures 3a and 3b lies in the dimension of the height X and in the shape of the transitions or in the shape of the narrow side of the side between the adjacent sides.

The pipe element 3a of Fig. 2b is formed with a transition section that is rounded at a side aligned at right angles to each other. The transition has a corner radius R, which is particularly shown in the detailed view of the pipe element 3a of figure 2c.

The side surfaces respectively arranged on the longitudinal side of the flow cross-section of the pipe element 3b shown in Fig. 2d are connected to each other via the side of the semicircular hollow cylinder shape on the narrow side. In this case, the outer radius R of the side corresponds to half of the height X. [

3a and 3b, a detailed view of the arrangement 2 of the pipe element 3 with the intermediate supported multi-disc 4 of the heat transfer device 1 shown in Fig. 1 is shown. In this case, a side view is shown in Fig. 3A, while Fig. 3B shows a detailed view of the arrangement 2 shown in Fig. 3A in a side sectional view with the pipe bottom 5 and the sealing element 7 extended. .

The pipe element 3 is formed by the height X in the first region 10 and by the height Y in the second region 11 respectively and in this case the extension of the pipe element 3 Is smaller in the first region (10) than in the second region (11) as viewed in the height direction (c). The pipe element 3 extends uniformly around the central axis aligned in the longitudinal direction (a) within the second region 11.

Within the intermediate space within the first region 10, formed in the pipe element 3 arranged parallel and parallel to one another with the wide side, there is provided an element for changing the flow cross-section and / A multi-disc 4 is provided. The multidisk 4 connected to the pipe element 3 on the wide side of the adjacently arranged pipe element 3 completely fills the intermediate space between the pipe elements 3 and consequently the adjacent arranged pipe elements 3 3 also correspond to the height F of the multi-disc 4 when viewed in the height direction c. In this case, the MD 4 is formed only in the first region 10 of the pipe element 3.

The pipe elements 3 each have a second region 11 and are arranged in the through openings 6 and 8 of the sealing element 7 and the pipe bottom 5. A web 5-1 is formed between the through openings 6 of the pipe bottom 5 which are arranged adjacent to each other in the height direction c and this web is provided with the through openings 6 in the depth direction b And abuts the broad side of the pipe element 3 substantially in connection with the sealing element 7. Fig. 3c shows a detailed view of the web 5-1 of the pipe bottom 5 with the sealing element 7 shown in Fig. 3b.

Within the intermediate space inside the second region 11 formed in the pipe element 3 arranged parallel and parallel to one another with the wide side the web 5-1 and the sealing element 7 of the pipe bottom 5 ) Are arranged. The intermediate space between the adjacent pipe elements 3 as seen in the height direction c is thus formed by two sections of one web 5-1 and the sealing element 7 of the pipe bottom 5 It is completely filled. In the height direction c, the web 5-1 is formed at a height H while the two sections of the sealing element 7 each have a wall thickness G. [

From the value obtained by adding the height X of the pipe element 3 to the height F of the multi disk 4 in the height direction c in the first region 10 of the pipe element 3, ) And a multi-disc (4). In the second region 11 of the pipe element 3, the height H of the web 5-1 at the bottom of the pipe and the double wall thickness G of the sealing element 7 in the height direction c, An extension of the unit consisting of the pipe element 3, the sealing element 7 and the web 5-1 of the pipe bottom 5 is shown from the sum of the height Y of the pipe element 3, The situation leads to the following equation:

After the conversion of the equation (1), the following equation

Where CM is the height of the web 5-1 of the pipe bottom 5 as an extension in the height direction c formed between adjacent through openings 6 of the pipe bottom 5 ) And the height F of the multi-disc 4, and the degree of deformation of the end portion of the pipe element 3 in the height direction (c).

The above equations are based on the structure of the pipe element 3 referring to the radius R, the width W and the height X of the first region 10, the height Y of the second region 11, The height H of the web 5-1 between the height F of the disk 4 and the through opening 6 of the pipe bottom 5 and the wall thickness G of the sealing element 7 The optimal relationship between the deformation of the pipe element 3 at the end will be described. In this case, with particular reference to the following equations (4) to (6), it is assumed that the deformation of the pipe end of the pipe element 3 has a maximum value CM _max leading to a circular flow cross- A range between the minimum value (CM _min ) at which the pipe end is not deformed is indicated.

), 최대값(CM_max)은 다음과 같이 나타난다:2B and 2C in which the sides are aligned at right angles to each other and the transitional rounding between adjacent sides is processed so that the height X of the first region 10 is twice the height of the pipe element 3a If it is larger than the value of the corner radius R

), The maximum value (CM _max ) appears as follows:

), 최대값(CM_max)은 다음과 같이 나타난다:The height X of the first region 10 coincides with the double radius R of the pipe element 3b in accordance with Figure 2d with the side of the longitudinal side connected to each other through the side of the semi- if(

), The maximum value (CM _max ) appears as follows:

), 최소 한계(CM_min)가 확정된다. 이로써, 최소값(CM_min)은 항상 다음과 같이 밀봉 요소(7)의 벽 두께(G)의 2배로부터 나타난다:As a result of the fact that the height Y of the second region 11 is smaller than the height Y of the first region 10 of the pipe element 3, 3a, 3b because the pipe element 3 is not extended or deformed or deformed at the end of the pipe, (X) < / RTI >

), The minimum limit (CM _min ) is confirmed. Thus, the minimum value _(min CM) is always displayed in the second multiple of the wall thickness of the sealing element (7) (G), as follows:

The parameter A describes the pipe expansion capacity as a ratio of the circumference of the pipe element at the end of the pipe after deformation of the circumference of the pipe element at the pipe end before deformation.

Figures 4a and 4b show respectively a perspective view and a plan view of a pipe element 3 at least partially enlarged at the pipe end similar to the pipe element 3a shown in Figure 2a or 2b and 2c. As a result of the deformation and expansion of the pipe element 3 in the region of the pipe end, the flow channels limited by the walls of the pipe element 3 have thus been transformed from a substantially rectangular cross-sectional shape to an elliptical cross-sectional shape. The elliptical cross-sectional shape of the flow channel is very stable with respect to the external pressure, in particular with respect to the pressure provided by the compressed sealing element 7.

In this case, the undeformed pipe element 3 was formed with a wall thickness of 0.22 mm and a width W of approximately 10.8 mm and a height X of 2.5 mm. The at least partially enlarged pipe element 3 has a height of approximately 4.69 mm in the second region 11, for example approximately 10.95 mm wide in the region of the maximum extension Y. [ The second region 11 is formed as a supporting surface 13 with the indicated dimensions and which is provided with a sealing element 15 on the bottom of the pipe 5 or between the pipe element 3 and the bottom of the pipe 5, The wall of the pipe element 3 in the pipe 7 is tangent.

In order to withstand the resistance of the compressed sealing element 7, the pipe element 3 is finally enlarged in the region of the apex 12. In this case, the wall of the pipe element 3 is deformed from the longitudinal side to the outside in order to further increase the rigidity of the supporting surface 13 with respect to the sealing element 7. [ In the finally deformed condition, the structure of the wall of the pipe element 3 is reinforced, especially at the longitudinal side.

In Figures 4C-4F, the finally enlarged pipe element 3 at the end of the pipe is shown in perspective and in plan view. After the pipe element 3 has been at least partially enlarged according to Figs. 4a and 4b, the pipe element 3 is finally enlarged starting from the front in the already deformed area of the pipe end. In this case, in particular, the edges of the top and bottom surfaces are deformed outwardly in the height direction c, respectively. By using the piercing blades the apex 12 of the pipe element 3 in the second region 11 is enlarged with respect to the sealing element 7 and the compression of the sealing element 7 is increased. After removing the blades, the resilient pipe material is restored to its minimum in the direction of the starting position, in which case the compression of the sealing material 7 remains within the predetermined range. Finally, the pipe element 3 has a forming part 14 in the region of the apex 12 of the upper and lower surfaces, respectively.

The wall of the pipe element 3 deformed at the pipe end by the forming part 14 is formed continuously and without cracking. The shape of the forming part 14 is used for increasing the structural rigidity of the wall of the pipe element 3 on the one hand and is fixed and fixed in the through opening 6 in the pipe bottom 5 on the other hand. It is used for sealing. In this case, also the clamping force, which avoids the relative displacement of the pipe element 3 relative to the pipe bottom 5 and the movement of the pipe element 3 inside the pipe bottom 5, is also increased.

Finally, the enlarged pipe element 3 has, for example, an extension Z of approximately 7.6 mm in the maximum enlarged area of the forming part 14, for example.

The device 1 formed with the pipe element 3 is also characterized by a flexible and non-rigid pipe element-sealing element-pipe bottom-connection formed on one or more sides of the arrangement 2, - Has durability.

5A and 5B show the pipe element 3, which is partially enlarged at the pipe end and has an elliptical cross section similar to the pipe element shown in Fig. 4A, in the direction of action 15 In a plan view. The pressure is generated by a sealing element tangent over the entire range, not shown in the figure.

In this case, as viewed in cross section, the arc-shaped surface on the narrow side of the deformed end of the pipe element 3 has a smaller diameter than the end of the pipe element 3 shown in Fig. 4A. The wall of the pipe element 3c was formed with a thicker cross section formed in an elliptical shape, which withstands the pressure externally provided better.

The pipe element 3 also has an elliptical shape of the cross section at the pipe end according to figure 5a and a pipe end with the shaping part 14 at the area of the apex 12 of the upper and lower surfaces according to figures 4c to 4f And may be formed by a combination of structural features such as deformation.

In figure 6a a detailed view of the arrangement of the pipe element 3 in the through opening 6 of the pipe bottom 5 with the sealing element 7 is shown in side sectional view. In Fig. 6b, a detailed view of the pipe bottom 5 with the sealing element 7 and the pipe element 3 shown in Fig. 6a is revealed.

Figure 6a shows an arrangement of a deformed enlarged pipe element 3 having a preferably elliptical cross section arranged through a through opening formed in the pipe bottom 5 and the sealing element 7 in particular. Due to the enlargement of the pipe element 3 the pipe element 3 is tightly connected with the sealing element 7 arranged between the pipe element 3 and the edge of the through opening of the pipe element 3, (5) in fluid sealing manner.

The pipe bottom 5 is formed with a ring element 17 in the region 16 of the web 5-1 which respectively compress the sealing element 7 in the region 16 At least locally reduces the open cross-section of the through-opening 6 for receiving the sealing element 7 and the pipe element 3, in order to increase it locally. The ring element 17 is arranged in such a way that the sealing element 7 is further compressed in a predetermined section or in a predetermined plane so that the sealing element 7 is of a lesser extent than in the region of the apex of the pipe element 3, So that compression is increased as intended. Since the sealing element 7 is compressed more strongly only in a small area, the resultant force acting on the pipe wall is less and the pipe wall is not collapsed.

The device 1 is again designed to have an elliptical shape and a cross-sectional profile in the cross-section at the pipe end according to figure 5a, in order to reach efficient compression of the sealing element 7, in particular in the region 16 of the apex 12, By any combination of the structural features of the pipe element 3, such as the deformation of the pipe end with the forming portion 14 in the region of the apex 12 of the upper and lower surfaces according to 4c to 4f, And a ring element 17 in the region of the web 5-1 of the bottom 5.

The connection of the pipe bottom 5 to the pipe element 3 ensures that the pipe element 3 is arranged at the correct position of the through openings 6, 8 and thereby ensures a fluid-tight connection. In order to ensure a sufficient and reliable compression of the sealing element 7, the intended enlargement size is determined in advance as the last extension of the pipe element 3. At this time, the compression of the sealing element 7 lies in the range of 10% to 50%, in which case most of the compression is accomplished immediately after the sealing element 7 and the pipe bottom 5 are mounted on the pipe element 3 do.

1: Device
2: arrangement
3, 3a, 3b, 3c: Pipe element, flat pipe
4: MD
5: Pipe floor
5-1: Web of the pipe bottom (5)
6: Through hole of pipe bottom (5)
7: Sealing element
8: Through-hole of sealing element 7
9: Collector
10: first region
11: second region
12: Vertex of the pipe element (3)
13: Support surface of the pipe element (3) of the pipe bottom (5)
14:
15: Direction of action of pressure
16: a locally increased compression area of the sealing element 7
17: Ring element
a: orientation, portrait orientation
b: Direction, Depth direction
c: direction, height direction
A: Pipe expansion capacity
F: the spacing of the pipe element 3, the height of the MD 4
G: wall thickness of the sealing element 7
H: height of the web 5-1 between the through openings 6 of the pipe bottom 5
R: Corner radius, the radius of the pipe element (3)
CM: Difference between the height F of the multi disk 4 and the height H of the web 5-1
W: Width of the pipe element (3)
X: height of the extension portion, first region 10
Y: height of the extension portion, second region 11
Z: an extension of the forming part 14

Claims (19)

Comprises at least one sealing element (7) having at least one pipe bottom (5) and a through opening (8) with a pipe element (3, 3a, 3b, 3c) An apparatus (1) for transferring heat between a first fluid and a second fluid, the arrangement having an arrangement (2)
(3, 3a, 3b, 3c) comprises a first zone (10) having a first height (X) and a width (W) Each of which has at least one second region (11) arranged with a support surface (13) having a second height (Y)
The sealing element 7 is arranged between the edge of the edge of the through opening 6 of the pipe bottom 5 and the support surface 13 and has a wall thickness G,
The pipe elements 3, 3a, 3b and 3c having a wide side are arranged in alignment with each other in parallel to each other and in the first region 10 with respect to each other at an interval F,
- a web (5-1) having a height (H) between adjacent through-apertures (6) of the pipe bottom (5)
(3, 3a, 3b, 3c) appearing from the value obtained by adding the first height (X) of the pipe element (3, 3a, 3b, 3c) The extension in the interior of the first region 10 is connected to the pipe element 3, 3a, 3b at the height H of the web 5-1 of the pipe bottom 5 and twice the wall thickness G of the sealing element 7, 3a, 3b, 3c, which is represented by the sum of the first height (Y) of the first pipe (3b, 3c) and the second height (Y)

CM describes the degree of deformation of the ends of the pipe elements 3, 3a, 3b and 3c in the height direction c and lies in the range between the maximum value CM _max and the minimum value CM _min , when the height (X, Y) of the elements (3, 3a, 3b, 3c ) , the same CM _min

(1). ≪ / RTI > The heat transfer device (1) according to claim 1, characterized in that said pipe elements (3, 3a, 3b, 3c) are formed of metal. 3. A pipe element according to claim 1, characterized in that the cross-section of the pipe element (3, 3a, 3b, 3c) is arranged in a plane perpendicular to the longitudinal direction (a) (11). ≪ / RTI > 2. A method as claimed in claim 1, characterized in that the flow cross-sections of the pipe elements (3, 3a, 3b) are limited by two sides which are respectively opposed to each other, the sides forming a narrow side or a longitudinal side of the flow cross- (1). ≪ / RTI > 5. A method according to claim 4, characterized in that the sides of the pipe elements (3, 3a) arranged next to each other are arranged at right angles to each other at the contact edges going in the longitudinal direction (a) R). ≪ / RTI > 6. The method according to claim 5, wherein the first height (X) of the first region (10) of the pipe element (3, 3a) is greater than the value of the double corner radius (R) of the pipe element The maximum value (CM _max )

, Wherein A represents the pipe expansion capacity. 5. A pipe element according to claim 4, characterized in that the sides arranged respectively on the longitudinal side of the flow cross-section of the pipe element (3, 3b) are bent outwardly in the form of a semicircular hollow cylinder, (1). ≪ / RTI > 8. A pipe element according to claim 7, characterized in that the first height (X) of the first region (10) of the pipe element (3, 3a) Corresponds to the double radius (R), and the maximum value (CM _max ) corresponds to the following formula

, Wherein A represents the pipe expansion capacity. 3. A method according to claim 2, characterized in that the pipe element (3, 3a, 3b) has a wall thickness of 0.22 mm, a first height (X) of approximately 2.5 mm and a width (W) of approximately 10.8 mm in the first region , And has a second height (Y) of about 4.69 mm and a width of about 10.95 mm in the second region (11). 3. A pipe element according to claim 2, characterized in that said pipe element (3, 3a, 3b) at the end of the pipe is formed in an expanded state starting from the front in the region of the vertex (12) , 3b) are deformed so as to have a molded part (14) on the outside in the height direction (c), respectively. 11. A method as claimed in claim 10, characterized in that the pipe element (3, 3a, 3b) has an extension (Z) of approximately 7.6 mm in the maximum extension area of the forming part (14) (1). 3. A method as claimed in claim 1, characterized in that the pipe bottom (5) comprises a through-hole (5) for receiving the sealing element (7) and the pipe element (3, 3a, 3b, 3c) Characterized in that it comprises a ring element (17) for at least locally reducing the open cross-section of the body (6). A heat transfer device (1) according to claim 1, characterized in that said bottom region (5) is formed as a sidewall element of the collector (9) of the device (1). 14. A method as claimed in claim 13, characterized in that two sealing elements (7) are formed with two pipe bottoms (5) and a through opening (8) with a through opening (6) 3, 3a, 3b, 3c), the through openings (6, 8) coinciding with the external shape of the pipe elements (3, 3a, 3b, 3c) The pipe elements 3, 3a, 3b and 3c each pass through a first end passing through a through opening 6 formed in the first pipe bottom 5 and a through opening 6 formed in the second pipe bottom 5, The second end of the heat transfer device (1) being arranged with a second end (12) which is arranged in the first direction. The heat transfer device (1) according to claim 2, characterized in that the pipe element (3, 3a, 3b, 3c) is formed of an aluminum alloy. 3. A device according to claim 1, characterized in that one row of pipe elements (3, 3a, 3b, 3c) of the device (1), arranged side by side and parallel to one another and wide with respect to each other, Characterized in that a flow path for the second fluid is arranged between the elements (3, 3a, 3b, 3c), one for each. A method according to claim 16, characterized by the fact that in the flow path formed inside the first region (10) by means of the adjacent pipe elements (3, 3a, 3b, 3c) (4) or ribs for expanding said multi-discs (4), said multi-discs (4) having an extension in the height direction (c) (F). ≪ / RTI > The heat transfer device (1) according to claim 17, characterized in that said multi-disc (4) or rib is formed of an aluminum alloy. Use of the device (1) according to any one of the claims 1 to 18 in the use of the heat transfer device (1) as a coolant-air-heat exchanger in the coolant circulation system of an automobile, in particular in an engine coolant circulation system.

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