JP6948461B2 - Heat transfer device - Google Patents

Description

The present invention relates to a heat transfer device, more particularly a heat transfer device for use in an automobile, in which heat is preferably a cooling material as a first fluid, such as water or a water-glycol mixture. And transmitted between air as a second fluid, the device is a pipe element for passing the first fluid, one or more pipe bottoms and one or more with through openings for each pipe element to pass through. With respect to a heat transfer device comprising an assembly consisting of a sealing element of.

Conventionally known coolant-air heat exchangers for transferring heat from the coolant circulation system to the ambient air are used in so-called high temperature coolant circulation systems for releasing heat from combustion engines. NS. The coolant-air heat exchanger made of aluminum has a small number of pipes, multi-discs and side elements fixed within the bottom of the pipe, and the coolant collectors arranged at the crimp connection site are for heat exchange. It has various elements that can be assembled into. Pipes aligned parallel to each other and arranged as a matrix are used to guide the liquid coolant between the collectors. The coolant collectors arranged on both sides at the end of the pipe are sealed to the pipe and the bottom of the pipe by an ethylene propylene diene rubber sealing element, abbreviated as EPDM sealing, according to conventional methods. The pipes, pipe bottoms, multi-disks and side elements are either completed in a fully soldered state as a so-called slot cooler or completely soldered as a so-called solder cooler by a plugging method. Completed in the state.

When using a soldering method in a controlled atmosphere called CAB (Controlled Atmospheric Brazing) for short, a matrix of pipes and multi-discs is placed between each other and, in some cases, as a metal element of the collector. It is connected to the bottom of the pipe. In the plugging method, welding or soldering of adjacent metal parts is avoided by using a mechanical assembly of a matrix and a collector, which is abbreviated as MA (Mechanical Assembly).
The air that absorbs heat from the coolant flows on the outer surface of the pipe, which allows it to flow along between the pipes. Multi-discs or ribs arranged between the pipes on the outer surface are used to expand the heat transfer surface on the air side, thereby increasing the output of the heat exchanger.
Known coolant-air heat exchangers have 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 quickly open within the coolant circulation system. It can be operated by a coolant having a temperature of about 120 ° C. At this time, the coolant-air heat exchanger experiences a very strong temperature shift and a thermal shock. The time-displaced thermal expansion of the individual pipes creates very large material stresses.

The slot cooler has a very high resistance to temperature changes in the coolant due to the slide bearing connection between the pipe and the bottom of the pipe as an element of the collector, but a forced coupling method connection between the pipe and the multi-disk. Therefore, it has less cooling performance than the soldering cooler. The soldering cooler again has limited durability against temperature shifts and thereby thermal expansion of the individual pipes due to the rigid soldering connection between the pipes and the bottom of the pipes.
DE 10 2015 113 905 A1 includes heat exchangers with collectors mechanically mounted for use in automobiles, especially methods for manufacturing and mounting airflow heat exchangers and such heat exchanges. The vessel is shown. The heat exchanger includes a matrix of fully mechanically bonded metal pipes and metal ribs arranged in parallel. The pipe comprises a heat transfer section having a straight tubular cross-sectional shape with two longer and shorter sides facing each other. One or more pipes are provided to provide a seal and to allow relative movement between the mechanically connected pipes and the first collector by thermal expansion and contraction of the matrix. At the first end section, it is connected to the first collector by one or more flexible elements that extend by the first end section of the pipe.

In this case, the slot cooler, depending on how the pipe and the multi-disc are soldered without the bottom of the pipe and then inserted onto the pipe with the bottom of the pipe sealed in the seal through a press fit. And the synergies of the method of manufacturing the soldering cooler are described. Due to the material properties reduced by providing temperatures above 600 ° C during soldering in the soldering oven, the pipe guarantees a sealing device over the entire circumference of the pipe, especially in the end regions. The demands made are permanently unable to withstand the resistance provided by the press-fit sealing.
Traditional pipes of heat exchangers used in automobiles, especially those made of aluminum alloy, often cannot withstand the sealing pressure acting on the walls of the pipe after compression of the sealing between the pipe and the bottom of the pipe. In this case, heat exchangers known in the art and methods for making such heat exchangers are pipes having a width or pipe depth of up to about 11 mm, especially pipes, to resist sealing pressure. Limited to the use of welded pipes. The seal must, on the one hand, be compressed within the range of 10% to 50% over the entire circumference of the pipe, in which case the compressed seal is due to the forces as described above applied to the wall of the pipe. Causes a situation where a wide unsupported pipe wall can collapse. On the other hand, the compression of the seal is placed in the central region of the pipe wall, in other words, within the region of the pipe crown, often below the above-mentioned target values.

DE 10 2015 113 905 A1

An object of the present invention is to provide a device for efficiently transferring heat between two fluids, particularly between a liquid fluid as a cooling material and air, and an object of such a device is intended. It's about trying to make up the street. At this time, the heat exchanger must have a sufficiently and uniform compressed state and a maximum sealed state of the sealed portion over the entire circumference of the pipe, in other words, high thermal shock durability, even when the temperature change is large. .. Depending on the heat exchanger, the maximum heat output must be transferred with the minimum structural size or with the minimum installation space demand. The heat exchanger must also have a minimum weight, resulting in minimum manufacturing and material costs.

The above problem is solved by an object having the characteristics of each independent claim. Examples of improvements are specified in each dependent claim.
The above problem is solved by the apparatus according to the present invention for transferring heat between the first fluid and the second fluid. The device comprises an assembly consisting of pipe elements for passing a first fluid, including one or more pipe bottoms with through openings and one or more sealing elements with through openings.
The pipe elements arranged so as to pass through the through openings are sealed and fixed at the first region having the first height (X) and the width (W) and the bottom of the pipe having the second height (Y), respectively. It can consist of a flat pipe having one or more second regions arranged at one end of the pipe element with a support surface for the pipe element.
Thus, each pipe element will have, in some first regions, a heat transfer region in which the pipe element is circulated by a second fluid, particularly air, and in some second regions, preferably a region connected to the bottom of the pipe. To have.

The sealing elements are arranged between the supporting surface of the pipe element and the edge of the edge of the through opening at the bottom of the pipe, respectively, and have a specific wall thickness (G). Depending on the intermediately supported sealing element, one or more pipe bottoms with through openings are connected to the pipe element in a fluid sealing manner. The through openings of the pipe bottom and the sealing element each match each other in shape and also match the external shape of the pipe element. In this case, preferably each pipe element exists in a state of passing through the through opening, and as a result, exactly one through opening is assigned to each end of the one pipe element.
The pipe elements have wide sides and are aligned parallel to each other and at intervals (F) from each other in the first region. Between the adjacently arranged through openings at the bottom of the pipe, one web each having a predetermined height (H) is further provided.

上記式中、ＣＭは、高さ方向でパイプ要素の端部の変形程度を示し、最大値（ＣＭ_ｍａｘ）と最小値（ＣＭ_ｍｉｎ）の間の領域に置かれている。パイプ要素の第１高さ（Ｘ）の値と第２高さ（Ｙ）の値とが同一の場合に、ＣＭ_ｍｉｎは密封要素の２倍の壁厚（Ｇ）に相当するが、言い換えれば、
ＣＭｍｉｎ＝２・Ｇ である。最小値ＣＭｍｉｎ＝２・Ｇでは、パイプ要素のパイプ端部が少なくとも高さ方向に形状破壊されていないか変形されていない。
特に、変形限界ＣＭ_ｍａｘを最大値と規定し、変形限界ＣＭ_ｍｉｎを最小値と規定することで、パラメーターとしてのＣＭは、プレスフィット内で周辺を取り囲む密封要素に対する周りにあるパイプ要素の堅固且つ確実な密封を保障しようとする目的からなされるパイプ要素の端部の好適な変形を記述する。
パイプ要素は、好ましくは金属から形成される。パイプ要素の横断面は、縦方向に対して垂直に整列された平面で第２領域内で好ましく拡張している。 According to the aspect of the present invention, when viewed from the height direction, the expansion of the pipe element composed of the first height (X) of one pipe element and the distance (F) of adjacent pipe elements inside the first region. Is inside the second region of the pipe element, which is composed of the second height (Y) of one pipe element, the height of one web at the bottom of the pipe (H) and the wall thickness (G) twice that of the sealing element. Corresponds to expansion, in which case Equation 2 applies.
[Number 2]

In the above formula, CM indicates the degree of deformation of the end portion of the pipe element in the height direction, and is placed in a region between the _{maximum value (CM max} ) and the minimum value (CM _min). When the value of the first height (X) and the value of the second height (Y) of the pipe element are the same, CM _min corresponds to twice the wall thickness (G) of the sealing element, in other words. ,
CMmin = 2 · G. At the minimum value of CMmin = 2 · G, the pipe end portion of the pipe element is not deformed or deformed at least in the height direction.
In particular, by _{defining the deformation limit CM max} as the maximum value and the deformation limit CM _min as the minimum value, the CM as a parameter is the firmness of the surrounding pipe element with respect to the sealing element surrounding the periphery in the press fit. Describes the preferred deformation of the end of the pipe element made for the purpose of ensuring a secure seal.
The pipe element is preferably made of metal. The cross section of the pipe element is a plane aligned perpendicular to the vertical direction and preferably extends within the second region.

で示され、［数４］中、Ａは、変形以前のパイプ端部におけるパイプ要素の周りに対する変形以後のパイプ端部におけるパイプ要素の周りの割合を示す。幾何学的構造及び材料特性は、パイプ要素の材料の引張限界による変形が材料の亀裂を引き起こす時までのパイプ端部の最大変形、特に拡張を可能にする。 According to an improved example of the present invention, the flow cross-section of the pipe element is limited by two sides facing each other, and these sides form a pair on the narrow side or the vertical side of the flow cross-section, respectively.
According to an alternative first embodiment of the present invention, the sides of the pipe elements arranged next to each other are aligned at right angles to each other with vertically traveling contact edges. In this case, the contact edges each include a rounded transition with an angular radius (R).
The first height (X) of the first region of the pipe element is preferably larger than the value of the angular radius (R) twice that of the pipe element. In this case, the maximum value (CM _max ) is
[Number 4]

In [Equation 4], A indicates the ratio of the circumference of the pipe element at the pipe end after the deformation to the circumference of the pipe element at the pipe end before the deformation. The geometric structure and material properties allow maximum deformation of the pipe end, especially expansion, until the deformation of the material of the pipe element due to the tensile limit of the material causes a crack in the material.

から最大値（ＣＭ_ｍａｘ）が示され、［数５］中、Ａは、パイプ膨脹容量に相当する。
本発明の一つの長所は、縦方向に対して垂直に整列された平面でパイプ要素の第２領域の横断面が拡張する時には、それぞれパイプ要素の壁によって制限された流動チャンネルが実質的に矩形の横断面形状から楕円形の横断面形状へと変形されることにある。
本発明の一改善例によって、パイプ要素は、第１領域では０．２２ｍｍの壁厚、約２．５ｍｍの第１高さ（Ｘ）及び約１０．８ｍｍの幅（Ｗ）を有し、第２領域１１では、約４．６９ｍｍの第２高さ（Ｙ）及び約１０．９５ｍｍの幅を有する。 According to an alternative second embodiment of the present invention, the side surfaces arranged on the vertical side of the flow cross section of the pipe element are curved outward in a semicircular hollow cylinder shape, and are narrow sides having an external radius (R). They are connected to each other via the sides of the.
The first height (X) of the first region of the pipe element preferably corresponds to a radius (R) twice the narrow side surface of the pipe element that is bent outward in a semicircular hollow cylinder. In this case
[Number 5]

The maximum value (CM _max ) is shown from, and in [Equation 5], 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 extends in a plane aligned perpendicular to the vertical direction, the flow channels restricted by the walls of each pipe element are substantially rectangular. It is to be transformed from the cross-sectional shape of the above to an elliptical cross-sectional shape.
According to an improved example of the present 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. The two regions 11 have 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 ends of the pipes are formed in an extended state starting from the front in the region of the vertical apex, resulting in the pipe elements. The walls are deformed so as to have molded portions on the outside from the height direction. Therefore, the pipe elements are formed with a shape in the apex regions of the upper surface and the lower surface, respectively. At this time, the pipe element preferably has an extension portion of about 7.6 mm in the maximum expansion region of the molded portion in the height direction.
According to a preferred embodiment of the invention, the bottom of the pipe can each be provided with a ring element in the area of the web to at least locally reduce the open cross section of the through opening for accommodating the sealing element.
In another preferred embodiment of the invention, the bottom of the pipe can be formed as a side wall element of the collector of the heat transfer device.
The heat transfer device is preferably formed with two pipe bottoms having through openings and two sealing elements with through openings. The bottom of the pipe is connected to the pipe element in a fluid-sealed manner, in which case the through-opening coincides with the external shape of the pipe element in shape, and each pipe element has a through-opening formed in the bottom of the first pipe. A first end portion passing through the pipe and a second end portion passing through a through opening formed in the bottom portion of the second pipe are provided.

The pipe element is preferably straight and preferably made of an aluminum alloy.
According to an improved example of the present invention, the pipe elements are arranged in one or more rows within the array.
A row of pipe elements of the device according to the invention, aligned side by side and parallel to each other and with wide sides relative to each other, preferably a second fluid, between the pipe elements arranged directly adjacent to each other. In particular, they are arranged so that one flow path for air is formed.
Within the flow path formed within the first region by the pipe elements arranged next to each other, preferably a multi-disc or for changing the flow cross-section and / or for increasing the heat transfer area. The ribs are arranged. In this case, the multi-disc has an extension in the height direction, which corresponds to the spacing (F) of the adjacently arranged pipe elements. The multi-disc or rib is preferably formed from an aluminum alloy.
Preferred embodiments of the present invention allow the heat transfer device according to the present invention to be used as a coolant-air heat exchanger in the coolant circulation system of an automobile, particularly in the engine coolant circulation system.

In summary, the heat transfer device according to the present invention has various advantages as follows.
-Expanding the use of CAB / MA manufacturing principles within the framework of the existing pipe portfolio
− If the size of the structure is minimal or the demand for installation space is minimal, in other words, if the ratio of the open volume to the transferable heat output is optimal, then also by the optimal ratio of geometric structures. Maximum heat output is transferred,
− Reduced complexity and material costs, which reduced manufacturing costs
-Has the least weight and
-When the maximum sealing degree, in other words, high thermal shock durability and high resistance to temperature shift, results in flexible connection between the pipe element, sealing element and the bottom of the pipe, even when the temperature shift is large. Allows for large opening and closing speeds of valves in the fluid circulation system, especially in the coolant circulation system.
-Guaranteed use even when pressure pulsation load is high
-The press fit, which provides uniform sealing compression at a specified level, ensures maximum life by permanently ensuring the connection between the bottom of the pipe and the end of the pipe inside the sealing element.

According to the heat transfer device of the present invention, the utilization of the CAB / MA manufacturing principle is expanded within the framework of the existing pipe portfolio, and when the size of the structure is the minimum or the demand for the installation space is the minimum, in other words, the transfer is performed. If the ratio of the open volume to the possible heat output is optimal, then the optimal geometrical ratio also transfers the maximum heat output.
It also reduces complexity and material costs, which reduces manufacturing costs and has minimal weight.
In addition, even when the temperature change is large, the maximum degree of sealing, in other words, high thermal shock durability and high resistance to the temperature change, results in flexible connection between the pipe element, the sealing element and the bottom of the pipe. In some cases, it allows for large opening and closing speeds of valves in the fluid circulation system, especially in the coolant circulation system, ensuring use even under high pressure pulsation load and uniform at specified levels. A press fit that provides good sealing compression ensures maximum life by permanently ensuring the connection between the bottom of the pipe and the end of the pipe inside the sealing element.

Further details, features and advantages of the embodiments of the present invention are set forth in the following detailed description of the embodiments of the present invention made with reference to the relevant drawings.
FIG. 5 is an exploded detail view of a heat transfer device comprising a pipe element array having an intermediately supported multi-disk as individual components, a pipe bottom, a sealing element and a collector. a is a side view of a pipe element formed as a flat pipe including a first region and a second region. FIG. b is a perspective view of a pipe element formed as a flat pipe having different flow cross sections. c is a detailed view of the pipe element shown in b. d is a perspective view of a pipe element formed as a flat pipe having different flow cross sections. a is a side view of an array of pipe elements having an intermediately supported multi-disk of the heat transfer device shown in FIG. b is a detailed cross-sectional view of an array of pipe elements having an intermediately supported multi-disk, a pipe bottom and a sealing element for the heat transfer device shown in FIG. c is a detailed view of the bottom of the pipe having the sealing element shown in b. a is a perspective view of a pipe element that is partially enlarged at the end of the pipe and has an elliptical cross section similar to the pipe element shown in FIG. 2a. b is a plan view of a pipe element that is partially enlarged at the end of the pipe and has an elliptical cross section similar to the pipe element shown in FIG. 2a. c is a perspective view of the pipe element shown in a and b, in which the end of the pipe is finally enlarged. d is a plan view of the pipe element shown in a and b, in which the end of the pipe is finally enlarged. e is a perspective view of the pipe element finally enlarged at the end of the pipe shown in a and b. reference numeral f is a perspective view of the pipe element finally enlarged at the end of the pipe shown in a and b. a is a perspective view of a pipe element that is partially enlarged at the end of the pipe and has an elliptical cross section similar to that of the pipe element shown in FIG. 4a. b is a plan view of a pipe element that is partially enlarged at the end of the pipe and has an elliptical cross section similar to the pipe element shown in FIG. 4a. a is a side sectional view of the array of pipe elements shown in FIG. 5a within the through opening of the bottom of the pipe having the sealing element. b is a detailed view of the bottom of the pipe having the sealing element and the pipe element shown in a.

FIG. 1 shows a pipe element 3 having a pipe bottom 5 and a sealing element 7 of the heat transfer device 1, particularly an array 2 of flat pipes. This drawing shows a detailed view of a heat transfer device 1 including a multi-disk 4 intermediately supported as individual components, a pipe bottom 5, a pipe element 3 having a sealing element 7 and a collector 9, and an array 2. There is. The collector 9 is also referred to as a coolant collector when the coolant is used as a fluid.
The array 2 made of flat pipes is formed in one row or a plurality of rows depending on the output requirement, and can be adjusted in terms of size, in other words, particularly in terms of length or width. The pipe elements 3 are arranged in two columns.
The pipe elements 3 aligned side by side and aligned in parallel with each other align with each other within a row having wide sides, resulting in direct adjacent pipe elements 3 for fluids, especially for air. Flow paths are generated respectively. At this time, each flow path travels between the pipe elements 3. A row of pipe elements 3 are arranged in a straight line with respect to each other and each extend between two collectors 9. The internal volume of the pipe element 3 is connected to the internal volume of the collector 9.

In the flow path, and in the intermediate space of the pipe elements 3 arranged adjacent to each other, elements for changing the flow cross section and / or expanding the heat transfer area are formed. The multi-disk 4 is provided as an element for changing the flow cross section and / or for increasing the heat transfer area. As an alternative, ribs can also be used. Like the pipe element 3, the multi-disc 4 is preferably made of a material having very good thermal conductivity, such as an aluminum alloy.
In the assembled state of the apparatus 1, a pipe bottom 5 that can also be used as a side wall element of the collector 9 is provided on the front surface or the narrow side of the array 2. In this case, the side surface where the ends of the pipe elements 3 are aligned is referred to as the front surface. The pipe bottom 5 is formed from a metal, particularly an aluminum alloy, as a deep-drawn portion, a perforated portion, or a hydroforming portion, which is substantially in the form of a rectangular sheet. In this case, the sheet is understood to be the final product of a flat rolling mill made of metal. Hydroforming, also referred to as high pressure deformation, is considered to deform the sheet within a closed mold tool using the pressure generated within the tool by the water-oil-emulsion.

Not only the pipe bottom 5 whose corner region is rounded, but also the sealing element 7 is provided with through openings 6 and 8 for accommodating the pipe element 3. In order to make a fluid-sealed connection between the individual pipe element 3 and the pipe bottom 5, the through-opening 6 of the pipe bottom 5 and the through-opening 8 of the sealing element 7 match each other and also the external dimensions of the pipe element 3. do. Webs 5-1 are formed between the through openings 6 of the bottom portion 5 of the pipe.
The pipe bottoms 5 arranged on opposite sides of the collector 9 are fixedly connected to the pipe element 3. Fixed connections can be viewed as zero leaks, each technically sealed by a sealing element 7. The pipe bottom 5 is arranged on the array 2 so as to be aligned perpendicular to the pipe element 3 on the narrow side of the pipe element 3.
FIG. 2a shows a pipe element formed as a flat pipe having an undeformed first region 10 as a heat transfer region, an undeformed second region 11 as a deformed region, and a connecting portion with a pipe bottom 5. 3 is shown as a side view. The regions 10 and 11 of the pipe element are formed in a state of being connected to each other when viewed from the vertical 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 uniform between the first region 10 where the pipe element 3 is circulated by the fluid and the second area 11 towards the end of the pipe. Expand to. Inside the regions 10 and 11, the cross-sectional areas of the flow channels are constant, respectively. Each of the second regions 11 of the pipe element 3 is preferably used as a support surface for a sealing element 7 formed flat, in other words, without a structure such as a notch or groove.
Within the undeformed first region 10, the pipe element 3 includes an external extension X, also referred to as the height (X) of the first region 10 when viewed from the height direction (c). The second region 11 of the pipe element 3, which is at least partially expanded, is formed by an external extension portion Y, which is also referred to as the height (Y) of the second region 11 when viewed from the height direction (c). The width of each of the pipe elements 3 is extended in the depth direction (b).

2b and d show perspective views of pipe elements 3a and 3b formed as flat pipes having different flow cross sections. These drawings show one cross section of the undeformed first region 10 of the pipe elements 3a and 3b, respectively. The flow cross section is extended in the plane set by the depth direction (b) and the height direction (c).
The flow cross-section is limited by two sides facing each other, each of which forms the narrow or vertical side of the flow cross-section. The sides formed in pairs facing each other have the same dimensions. In this case, the narrow side surfaces as the first pair in the height direction (c) have the same height (X), while the second side in the depth direction (b) is aligned parallel to each other. The vertical sides as a pair have the same width (W).
Substantial differences in FIGS. 3a and 3b are in the dimension of height (X), in the shape of the transition between the side surfaces in contact with each other or in the shape of the side surface on the narrow side.

The pipe element 3a of FIG. 2b is formed with a rounded transition on the side surfaces aligned at right angles to each other. The transition portion has an angular radius (R), and such a situation is particularly shown in the detailed view of the pipe element 3a of FIG. 2c.
The side surfaces of the pipe element 3b shown in FIG. 2d arranged on the vertical side of the flow cross section are connected to each other via a semicircular hollow cylindrical side surface on the narrow side. In this case, the outer radius (R) of the side surface corresponds to half of the height (X).
3a and 3b show a detailed view of an array 2 of pipe elements 3 having an intermediately supported multi-disk 4 of the heat transfer device 1 shown in FIG. In this case, FIG. 3a shows a side view, while FIG. 3b discloses a detailed view of the array 2 shown in a as a side sectional view in a state where the pipe bottom 5 and the sealing element are expanded by 7 minutes.
The pipe element 3 is formed by a height (X) in the first region 10 and by a height (Y) in the second region 11, respectively. In this case, the extension portion of the pipe element 3 is formed. When viewed from the height direction (c), it is smaller in the first region 10 than in the second region 11. The pipe element 3 extends uniformly around the central axis aligned in the vertical direction (a) within the second region 11.

In the intermediate space inside the first region 10, formed within the pipe elements 3 aligned side by side and parallel to each other with wide sides, and / or heat transfer to change the flow cross section. The multi-disk 4 is provided as an element for expanding the area. The multi-disks 4 connected to the pipe elements 3 on the wide side of the adjacently arranged pipe elements 3 completely fill the intermediate space between the pipe elements 3, resulting in the adjacently arranged pipe elements. The interval (F) of 3 further corresponds to the height (F) of the multi-disc 4 when viewed from the height direction (c). In this case, the multi-disk 4 is formed only in the first region 10 of the pipe element 3.
The pipe elements 3 each include a second region 11 and are arranged in the sealing elements 7 and the through openings 6 and 8 of the pipe bottom 5. Webs 5-1 are formed between the through openings 6 of the pipe bottoms 5 arranged adjacent to each other in the height direction (c), and the webs form the through openings 6 in the depth direction (b). It is substantially in contact with the wide side of the pipe element 3 in a state of being connected to the sealing element 7. FIG. 3c shows a detailed view of the web 5-1 of the pipe bottom 5 having the sealing element 7 shown in b.
The web 5-1 and the sealing element 7 of the pipe bottom 5 are arranged in the intermediate space inside the second region 11 formed in the pipe elements 3 having wide sides and aligned and parallel to each other. Has been done. Thus, when viewed from the height direction (c), the intermediate space between the adjacently arranged pipe elements 3 is completely filled by one web 5-1 at the bottom of the pipe 5 and two sections of the sealing element 7. ing. When viewed from 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).

［数１］の変換後には、
［数２］

が示され、［数２］中、ＣＭは、パイプ底部５の隣り合う貫通開口６の間に形成された高さ方向（ｃ）での延長部としてのパイプ底部５のウェブ５−１の高さ（Ｈ）とマルチディスク４の高さ（Ｆ）との間に現われる差の最適な範囲、及び高さ方向（ｃ）でのパイプ要素３の端部の変形程度を記述する。
［数３］

In the first region 10 of the pipe element 3, 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), from the pipe element 3 and the multi-disk 4. Indicates an extension of the unit. Further, 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 wall thickness (G) twice that of the sealing element 7 in the height direction (c) of the pipe element 3 are increased. From the value plus the height (Y), the 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, and such a situation leads to the following equation. :
[Number 1]

After the conversion of [Equation 1],
[Number 2]

In [Equation 2], the CM is the height of the web 5-1 of the pipe bottom 5 as an extension in the height direction (c) formed between the adjacent through openings 6 of the pipe bottom 5. The optimum range of the difference appearing between the height (H) 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) are described.
[Number 3]

それぞれ狭い側の半円円筒形状の側面を介して互いに連結された縦側の側面を有する図２ｄによって、第１領域１０の高さ（Ｘ）が、パイプ要素（３ｂ）の２倍の半径（Ｒ）と一致すれば
Ｘ＝２・Ｒ、最大値ＣＭｍａｘは次のように示される
［数５］

パイプ要素３がパイプ端部で拡張しないか形態変更されないか変形されないことから、結果として第２領域１１の高さ（Ｙ）がパイプ要素３、３ａ、３ｂの第１領域１０の高さ（Ｘ）と一致することでＹ＝Ｘ、最小限界ＣＭ_ｍｉｎが確定する。これで、最小値ＣＭ_ｍｉｎは、常に次のように密封要素７の壁厚（Ｇ）の２倍から示される：
［数６］

The above equation shows the structure of the pipe element 3 with reference to the radius (R), width (W) and height (X) of the first region 10, the height (Y) of the second region 11, and the multi-disk 4. Of the pipe element 3 at the end referring to the height (F), the height (H) of the web 5-1 between the through openings 6 of the pipe bottom 5 and the wall thickness (G) of the sealing element (7). Describe the optimal relationship between the transformations. In this case, particularly referring to the following equations (4) to (6), the maximum value (CM _max ) and the pipe element 3 that the deformation of the pipe end portion of the pipe element 3 induces a circular flow cross section. The range between the _{minimum values (CM min} ) at which the end of the pipe is not deformed is indicated.
The height (X) of the first region 10 is twice that of the pipe element 3a according to FIGS. 2b and c in which the sides are aligned at right angles to each other and the transitions between the adjacent sides are rounded. If it is larger than the value of the angular radius (R) of, X> 2 · R, and the maximum value CMmax is shown as follows.
[Number 4]

The height (X) of the first region 10 is twice the radius of the pipe element (3b), according to FIG. 2d, each having vertical sides connected to each other via a narrow semicircular cylindrical side surface. If it matches R), X = 2 · R, and the maximum value CMmax is shown as follows [Equation 5].

Since the pipe element 3 is not expanded, reshaped, or deformed at the end of the pipe, as a result, the height (Y) of the second region 11 is the height (X) of the first region 10 of the pipe elements 3, 3a, and 3b. ), Y = X, and the minimum limit CM _min is determined. _Now the minimum value CM min is always indicated by twice the wall thickness (G) of the sealing element 7 as follows:
[Number 6]

Parameter A describes the pipe expansion capacity as the ratio around the pipe element at the end of the pipe after deformation to around the pipe element at the end of the pipe before deformation.
4a and 4b show the pipe element 3 at least partially enlarged at the end of the pipe as a perspective view and a plan view, similar to the pipe element 3a shown in FIGS. 2a or b and c, respectively. The deformation and expansion of the pipe element 3 in the region of the pipe end results in the flow channel restricted by the wall of the pipe element 3 being deformed from a substantially rectangular cross-section to an elliptical cross-section. rice field. The elliptical cross-sectional shape of the flow channel is very stable to external pressure, but especially 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, a width (W) of about 10.8 mm and a height (X) of 2.5 mm. The pipe element 3, which is at least partially enlarged, has a height of about 4.69 mm in the second region 11, for example, when the width is about 10.95 mm in the region of the maximum extension portion Y. The second region 11 is formed as a support surface 13 having the indicated dimensions, which may be on the pipe bottom 5 or on the sealing element 7 compressed between the pipe element 3 and the pipe bottom 5. The walls of a pipe element 3 touch.
To withstand the resistance of the compressed sealing element 7, the pipe element 3 finally expands in the region of the apex 12. In this case, the wall of the pipe element 3 is deformed from the vertical side to the outside in order to further increase the rigidity of the support surface 13 with respect to the sealing element 7. In the finally deformed state, the structure of the wall of the pipe element 3 is reinforced, especially on the vertical side.
4c to 4f show the pipe element 3 finally enlarged at the end of the pipe as a perspective view and a plan view. After the pipe element 3 has at least partially expanded according to FIGS. 4a and 4b, each of the pipe elements 3 starts from the front in the already deformed region of the pipe end and finally expands. In this case, the edges of the upper surface and the lower surface are deformed to the outside in the height direction (c), respectively. By using the perforation blade, the apex 12 of the pipe element 3 expands with respect to the sealing element 7 in the second region 11, and the compression of the sealing element 7 increases. After removing the blades, the elastic pipe material is minimally reshaped in the direction of the starting position, in which case the compression of the sealing material 7 remains within the intended range. Finally, the pipe element 3 includes a forming portion 14 in the region of the apex 12 on the upper surface and the lower surface, respectively.

The wall of the pipe element 3 deformed at the end of the pipe by the forming portion 14 is formed continuously and without cracks. The shape of the molded portion 14 is used on the one hand to increase the structural rigidity of the wall of the pipe element 3, and on the other hand for fixing and sealing inside the through opening 6 in the pipe bottom 5. In this case, the relative position change of the pipe element 3 with respect to the pipe bottom 5 and the fixing force for avoiding the movement of the pipe element 3 inside the pipe bottom 5 also increase.
The finally enlarged pipe element 3 also includes, for example, an extension portion Z of about 7.6 mm in the maximum expansion region of the molding portion 14.
The device 1 formed with the pipe element 3 is provided with a very high thermal shock due to the flexible and non-rigid pipe element-sealing element-pipe bottom connection formed on one or more sides of the array 2. Has durability.
5a and 5b show a perspective view of the pipe element 3 which is partially magnified at the end of the pipe and has an elliptical cross section similar to the pipe element shown in FIG. 4a, and the pressure provided from the outside. It is shown as a plan view in the action direction 15 of. Pressure is generated by sealing elements that are in contact over the entire range, not shown in the drawings.
In this case, when viewed on the cross section, the arcuate surface on the narrow side of the deformed end of the pipe element 3 has a diameter smaller than that of 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 oval shape that better withstands externally provided pressure.

The pipe element 3 further includes an elliptical shape of a cross section at the end of the pipe according to FIG. 5a and a deformation of the end of the pipe having a molded portion 14 in the region of the apex 12 of the upper surface and the lower surface according to FIGS. 4c to 4f. It can also be formed by a combination of structural features.
FIG. 6a shows a detailed view of the arrangement of the pipe elements 3 in the through opening 6 of the pipe bottom 5 having the sealing element 7 as a side sectional view. FIG. 6b shows a detailed view of the bottom portion 5 of the pipe having the sealing element 7 and the pipe element 3 shown in a.
FIG. 6a shows an array of deformed and enlarged pipe elements 3, preferably having an elliptical cross section, arranged through through openings formed within the pipe bottom 5 and the sealing element 7. Due to the expansion of the pipe element 3, the pipe element 3 is tightly connected to the sealing element 7 arranged between the pipe element 3 and the edge of the through opening of the pipe element 3, and the pipe bottom 5 is fluid-sealed. It is connected.
The bottom of the pipe 5 is formed in a region 16 of the web 5-1 each with a ring element 17, which ring element 7 is used to locally increase the compression of the sealing element 7 in the region 16. And the open cross section of the through opening 6 for accommodating the pipe element 3 is at least locally reduced. The ring element 17 of the sealing element 7 is made less, especially in the area of the apex of the pipe element 3, when the sealing element 7 is further compressed in the planned section or planned surface, as a result. The compression is formed to increase as intended. Since the sealing element 7 is compressed more strongly only in a small area, the resulting force acting on the pipe wall is less and the pipe wall does not collapse.

The device 1 again has an elliptical cross-sectional shape at the end of the pipe, according to FIG. 5a, in order to reach efficient compression of the sealing element 7 over the entire circumference of the pipe, especially in the region 16 at the apex 12. By any combination of structural features of the pipe element 3, such as deformation of the end of the pipe having the moldings 14 in the regions of the vertices 12 of the upper and lower surfaces according to FIGS. 4c-5, and the web 5- of the bottom 5 of the pipe. A ring element 17 is provided in the region of 1.
The connection between the pipe bottom 5 and the pipe element 3 ensures that the pipe element 3 is aligned at the exact location of the through openings 6 and 8 and thereby produces a secure fluid sealing connection. .. In order to ensure sufficient and reliable compression of the sealing element 7, the intended expansion magnitude is predetermined as the final extension of the pipe element 3. At this time, the compression of the sealing element 7 is placed in the range of 10% to 50%, and in this case, most of the compression is realized immediately after the sealing element 7 and the pipe bottom 5 are attached to the pipe element 3. do.

The present invention particularly relates to a heat transfer device for use in automobiles. In this device, heat is preferably transferred between the coolant as the first fluid, such as water or a water-glycol mixture and air as the second fluid. The device comprises a pipe element for passing a first fluid, one or more pipe bottoms each having a through opening for passing the pipe element, and an assembly consisting of one or more sealing elements.

1 Heat transfer device 2 Array 3, 3a, 3b, 3c Pipe element 4 Multi-disk 5 Pipe bottom 5-1 Web 6, 8 Through opening 7 Sealing element 9 Collector 10 1st area 11 2nd area 12 Vertex 13 Support surface 14 Molded part 16 Region 17 Ring element

Claims (19)

One or more pipe elements (3, 3a, 3b, 3c) for passing the first fluid, one or more pipe bottoms (5) with through openings (6), and one or more seals with through openings (8). A device (1) for transferring heat between a first fluid and a second fluid having an array (2) composed of elements (7).
The pipe element (3, 3a, 3b, 3c), one end of the first region having a first height (X) and width (W) (10), and said pipe element (3, 3a, 3b, 3c) A flat pipe arranged in a portion and having one or more second regions (11) having a support surface (13) having a second height (Y) equal to or higher than the first height (X). Consists of
The second region (11) of the pipe element (3, 3a, 3b, 3c) is arranged in the through opening (6) of the pipe bottom (5) and the through opening (8) of the sealing element (7).
The sealing element (7) is arranged between each of the pipe bottom the the through the edge of the edge of the opening (6) (5) the support surface (13), have a wall thickness (G),
Before Symbol pipe element (3, 3a, 3b, 3c) are parallel to each other, and are arranged in a state where each of the first region (10) aligned in spaced relation to each other (F),
Each web having a height (H) (5-1) is provided between the pipe bottom (5) through the opening (6) arranged adjacent the,
When viewed from the height direction (c), the intermediate space between the pipe elements (3) arranged adjacent to each other is one of the webs (5-1) of the pipe bottom (5) and the sealing element (7). ) Are completely filled by two sections, each with a wall thickness (G).
In the area (16) of the web (5-1), the pipe bottom (5) is formed with a ring element (17), and the ring element (17) is sealed in the area (16). In order to locally increase the compression of the element (7), the open cross section of the through opening (6) for accommodating the sealing element (7) and the pipe element (3) is at least locally reduced. Let me
When viewed from the height direction (c), first value obtained by adding the height (X) of the pipe element to the spacing (F) (3, 3a, 3b, 3c), the pipe bottom (5) the double wall thickness of the height of the web (5-1) (H) and the sealing element (7) (G) pipe element (3,3a, 3b, 3c) second height of the (Y) Corresponds to the added value
When the degree of deformation of the end portion of the pipe element (3, 3a, 3b, 3c) in the height direction (c) is defined as CM, the CM is represented by the following equation 2.
[Number 2]

In the above formula, CM describes the degree of deformation of the end portion of the pipe element (3, 3a, 3b, 3c) in the height direction (c), F is the interval, and H is the web (5-1). The height, Y is the second height, X is the first height, G is the wall thickness, and the CM is within the range between the maximum value (CM _max ) and the minimum value (CM _min). When the first height (X) and the second height (Y) of the pipe elements (3, 3a, 3b, 3c) are the same, the CM is the minimum value (CM _min). ) , Shown by CM _mini = 2 · G,
The pipe element (3) is characterized by having a molded portion (14) having a shape in which the edges of the upper surface and the lower surface of the second region (11) are deformed outward in the height direction (c), respectively. Heat transfer device (1). The heat transfer device (1) according to claim 1, wherein the pipe elements (3, 3a, 3b, 3c) are formed of metal. The cross section of the pipe element (3, 3a, 3b, 3c) is a plane aligned perpendicular to the vertical direction (a) of the pipe element (3, 3a, 3b, 3c) and the second region (11). ), The heat transfer device (1) according to claim 1. The flow cross section of the pipe elements (3, 3a, 3b) is limited by two side surfaces facing each other, and the side surfaces form a pair of narrow side or vertical side of the flow cross section, respectively. The heat transfer device (1) according to claim 1. The side surfaces of the pipe elements (3, 3a) arranged adjacent to each other are aligned at right angles to each other by contact edges traveling in the longitudinal direction (a), and the contact edges each have an angular radius (R). The heat transfer device (1) according to claim 4, further comprising a rounded transition portion. The first height (X) of the first region (10) of the pipe element (3, 3a) is larger than the value of the angular radius (R) twice that of the pipe element (3, 3a), and is the maximum value. (CM _max ) is the following formula [Equation 4]

The heat transfer device (1) according to claim 5, wherein A corresponds to a pipe expansion capacity in the above formula. The side surfaces of the pipe elements (3, 3b) arranged on the vertical side of the flow cross section are curved outward in a semicircular hollow cylinder shape, and are mutually arranged via the narrow side side surfaces having an external radius (R). The heat transfer device (1) according to claim 4, wherein the heat transfer device is connected. The first height (X) of the first region (10) of the pipe element (3, 3a) is twice the narrow side surface of the pipe element (3, 3b) bent outward in a semicircular hollow cylinder shape. Corresponds to the radius (R) of, and the maximum value (CM _max ) is the following formula [Equation 5].

The heat transfer device (1) according to claim 7, wherein A corresponds to a pipe expansion capacity. The pipe elements (3, 3a, 3b) have 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 (10). The heat transfer device (1) according to claim 2, wherein the second region (11) has a second height (Y) of about 4.69 mm and a width of about 10.95 mm. The pipe elements (3, 3a, 3b) at the end of the pipe are formed in an expanded state starting from the front in the region of the apex (12) on the vertical side, respectively, and the pipe elements (3, 3a, 3b) are formed. The heat transfer device (1) according to claim 2, wherein the wall of) is deformed so as to have a molded portion (14) on the outside in the height direction (c). The tenth aspect of the present invention, wherein the pipe elements (3, 3a, 3b) have an extension portion (Z) of about 7.6 mm in the maximum expansion region of the molding portion (14) in the height direction (c). The heat transfer device (1). The pipe bottom (5) is a region (16) of the web (5-1) of a through opening (6) for accommodating a sealing element (7) and a pipe element (3, 3a, 3b, 3c), respectively. The heat transfer device (1) according to claim 1, further comprising a ring element (17) for at least locally reducing the open cross section. The heat transfer device (1) according to claim 1, wherein the pipe bottom portion (5) is formed as a side wall element of the collector (9) of the device (1). Two pipe bottoms (5) having a through opening (6) and two sealing elements (7) having a through opening (8) are formed, and the pipe bottom (5) is a pipe element (3, 3a, 3b, respectively). 3c) is connected by a fluid sealing method, and the through openings (6, 8) match the external shape of the pipe elements (3, 3a, 3b, 3c) in shape, respectively, and the respective pipe elements (3, 8) are connected. 3a, 3b, and 3c) have through openings (6) formed in the first end and the second pipe bottom (5) that pass through the through openings (6) formed in the first pipe bottom (5), respectively. The heat transfer device (1) according to claim 13, wherein the heat transfer device (1) is arranged so as to include a second end portion through which the heat transfer device is provided. The heat transfer device (1) according to claim 2, wherein the pipe elements (3, 3a, 3b, 3c) are formed of an aluminum alloy. A row of pipe elements (3, 3a, 3b, 3c) of device (1) arranged side by side and parallel to each other and with wide sides relative to each other are pipes arranged directly next to each other. The heat transfer device (1) according to claim 1, wherein one flow path for the second fluid is arranged between the elements (3, 3a, 3b, 3c). ). In the flow path formed inside the first region (10) by the pipe elements (3, 3a, 3b, 3c) arranged next to each other, and / or the heat transfer area for changing the flow cross section. The multi-disc (4) or ribs for enlarging the The heat transfer device (1) according to claim 16, wherein the heat transfer device (1) corresponds to an interval (F) of 3, 3a, 3b, 3c). The heat transfer device (1) according to claim 17, wherein the multi-disc (4) or rib is formed of an aluminum alloy. The heat transfer device (1) according to any one of claims 1 to 18 is used as a coolant-air heat exchanger in the coolant circulation system of an automobile, particularly in the engine coolant circulation system. Application of the device (1) characterized by.

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