CN110770527A

CN110770527A - Heat transfer device

Info

Publication number: CN110770527A
Application number: CN201880033864.XA
Authority: CN
Inventors: G·J·克莱尔; J·拉普西克; J·马蒂尼
Original assignee: Hanon Systems Corp
Current assignee: Hanon Systems Corp
Priority date: 2017-06-22
Filing date: 2018-06-07
Publication date: 2020-02-07
Anticipated expiration: 2038-06-07
Also published as: US20210095926A1; KR102080801B1; KR20190000288A; JP2020521109A; WO2018236076A1; DE102018111580A1; JP6948461B2; EP3644005A4; EP3644005A1; CN110770527B

Abstract

The invention relates to a device for use between a first fluid and a second fluidA heat transfer device (1) for transferring heat. The heat transfer device (1) has an array body (2), and the array body (2) includes: a tube member (3, 3a, 3b, 3c) for passing a first fluid; at least one tube bottom (5) having a through opening (6); and at least one sealing member (7) having a through opening (8). The tube members (3, 3a, 3b, 3c) are formed by flat tubes, which respectively include: a first region (10) having a first height (X) and a width (W); and at least one second region (11) having a support surface (13) arranged at one end of the tube member (3, 3a, 3b, 3c) and having a second height (Y). The sealing members (7) are arranged between the outer peripheral edge of the through opening (6) of the tube bottom (5) and the support surface (13), respectively, and have a wall thickness (G). The pipe members (3, 3a, 3b, 3c) having the wide sides are arranged in parallel with each other and aligned in a state of being spaced apart from each other by a space (F) in the first region (10). Webs (5-1) having a height (H) are respectively arranged between the through-openings (6) arranged adjacent to the tube bottom (5). At the slave maximum (CM)_max) To a minimum value (CM)_min) The degree of deformation of the end portions of the pipe members (3, 3a, 3b, 3c) in the height direction (c) within the range (c) is set in advance by referring to the dimensional relationship.

Description

Heat transfer device

Technical Field

The invention relates in particular to a heat transfer device for a motor vehicle. In the heat transfer device described above, heat is preferably transferred between a coolant, for example water or a water-glycol mixture, as the first fluid and air as the second fluid. The heat transfer device has an assembly comprising: a pipe member for passing a first fluid; at least one tube bottom having a through opening for passing the respective tube member; and at least one sealing member.

Background

The heat exchanger between coolant and air for transferring heat from the coolant circulation system to ambient air disclosed in the prior art is used in a so-called high-temperature coolant circulation system for releasing heat of the combustion mechanism. The heat exchanger between the coolant formed of aluminum and the air includes a small number of tubes fixed in the bottom of the tubes, a multifunctional plate, and side members, and the coolant collector arranged at the crimp connection portion has various members assembled for heat exchange. A plurality of tubes aligned parallel to each other and in a matrix are used to conduct the liquid coolant between the plurality of collectors. The coolant collectors arranged on both sides in the pipe end are sealed off in a conventional manner with respect to the pipe and the pipe bottom by an ethylene-propylene-diene-rubber sealing element, referred to as an ethylene-propylene-diene-rubber (EPDM) seal. The tubes, tube bottoms, multifunctional disks and side members are completed in a completely brazed state by so-called slot coolers (slot coolers) in the plugging method or in a completely brazed state by so-called brazing coolers.

When the Brazing method is used under a Controlled atmosphere, called simply protective gas Brazing ("CAB"), the bases formed by the tubes and the multifunctional discs are connected to each other and, as the case may be, to the bottom of the tubes, which are the metal members of the respective collectors. In the leak stoppage method, adjacent metal parts are prevented from being welded or brazed by Mechanical Assembly using a base body and a collector, which is simply called Mechanical Assembly (MA).

The air that absorbs heat from the coolant flows on the outside faces of the tubes, thereby flowing along between the plurality of tubes. Multifunctional discs or ribs (rib) arranged between the tubes in the outer face serve to enlarge the air-side heat transfer face and thereby to increase the power of the heat exchanger.

Known heat exchangers between coolant and air have unsatisfactory durability with respect to the rapidly changing temperature of the coolant. Thus, in an extremely applicable case, the heat exchanger between the coolant and the air can be cooled to a temperature in the range of-20 ℃ to-10 ℃, working with a coolant having a temperature of about 120 ℃ through a fast opening valve in the coolant circulation system. In this case, the heat exchanger between the coolant and the air undergoes a very large temperature change and thermal shock (thermal shock). Due to the time-shifted thermal expansion of the individual tubes, very large material stresses occur.

The slot cooler has a very high resistance to temperature changes of the coolant due to the slide bearing-connection between the tube as collector member and the tube bottom, but has a lower cooling performance than the brazing cooler due to the connection between the tube and the multifunctional disk in a forced bonding manner. The brazed cooler has a limited durability against temperature changes and thus thermal expansion of the individual tubes, again by a rigid brazed connection between the tubes and the tube bottom.

DE102015113905a1 discloses a heat exchanger with a mechanically mounted collector for use in a motor vehicle, in particular a method for mounting and producing an air flow heat exchanger and a heat exchanger as described above. The heat exchanger comprises a plurality of metal tubes arranged side by side and a base body welded in a fully mechanical manner from a plurality of metal reinforcing ribs. The tube has a heat transfer section in the shape of a straight tube cross section with 2 long and short opposing sides. In order to be useful for providing a seal and for enabling relative movement between the tube and the first collector which are mechanically connected by thermal expansion and contraction of the base, at least one of the tubes is connected to the first collector by at least one flexible member extending in a first end section at a distance corresponding to the first end section of the tube.

In this case, after the tube and the multifunctional disk are brazed without the tube bottom, the tube bottom is inserted into the tube in a state of being sealed inside the sealing portion by press fit (press fit), by which means the synergy of the manufacturing method of the slot cooler and the brazing cooler is expressed. Providing temperatures above 600 ℃ during brazing in a brazing furnace, the tube cannot permanently withstand the resistance offered by sealing by means of press fit, due to the reduced material properties, in particular in the end regions, as required to ensure a sealing means around the entire tube.

Conventional tubes suitable for use in automotive heat exchangers, particularly tubes formed of aluminum alloys, often receive sealing pressure on the tube wall after compressing the seal between the tube and the bottom of the tube. In this case, in the heat exchanger disclosed in the related art and the manufacturing method of the heat exchanger as described above, in order to withstand the sealing pressure, use of the tube, especially the welded tube, which may have a width or a tube depth as wide as about 11mm, is limited. On the one hand, the entire circumference of the seal portion needs to be compressed in the range of 10% to 50%, but in this case, due to the pressure applied to the tube wall as described above, in the compressed seal portion, a situation is caused in which, in particular, the unsupported wide-width tube wall may collapse. On the other hand, the compression of the seal is located in the central region of the pipe wall, in other words in the region of the pipe head, often below the aforementioned target value.

Disclosure of Invention

Technical problem

The object of the invention is to provide a device for the efficient transfer of heat between two fluids, in particular between a liquid phase fluid as coolant and air, and to design the device as described above as intended. In this case, the heat exchanger should have the sealing portions in a sufficiently and uniformly compressed state and a maximum sealing state all around the respective tubes even in the case where the temperature change is large, in other words, it is required to have thermal shock durability. With heat exchangers, it is necessary to transfer maximum thermal power with a minimum of structural dimensions or with minimum installation space requirements. The heat exchanger also needs to have a minimum weight and consume a minimum manufacturing cost and material cost.

Means for solving the problems

The above-mentioned technical problem is solved by the object having the features of the independent claims. Improvements are evident in the dependent claims.

The above technical problem is solved by the device of the present invention for transferring heat between a first fluid and a second fluid. The heat transfer device has an assembly comprising: a pipe member for passing a first fluid; at least one tube bottom having a through opening for passing the respective tube member; and at least one sealing member.

A plurality of tube members arranged in a state passing through the respective through openings may be formed of flat tubes, the flat tubes respectively including: a first region having a first height X and a width W; and at least one second region having a support surface for sealing and fixing at the bottom of the tube having the second height Y, arranged at one end of the tube member.

The plurality of tube elements thus each have, via a first region, a heat transfer region in which the tube elements are circulated by a second fluid, in particular air, and via a second region, preferably a region which is connected to the tube base.

The sealing members are arranged between the support surface of the tube member and the peripheral edge of the through opening of the tube bottom, respectively, with a specific wall thickness G. At least one tube bottom with a through-opening is connected in a fluid-tight manner with a plurality of tube elements by means of an intermediate supported sealing element. The shapes of the plurality of through openings of the tube bottom and the seal member correspond to each other, and also correspond to the outer shape of the tube member. In this case, preferably, one pipe member exists in a state of passing through the through opening, and finally, one through opening is accurately assigned to each end of one pipe member.

The plurality of tube members have wide sides, are aligned in parallel with each other, and are aligned in the first region with a space F therebetween. Between a plurality of through-openings arranged adjacent to the tube bottom and in each case one web with a predetermined height H can be arranged.

According to the idea of the present invention, the expansion in the first region of the pipe member constituted by the first height X of one pipe member and the interval F of the adjacent plurality of pipe members corresponds to the expansion in the second region of the pipe member constituted by the second height Y of one pipe member, the height X of one web of the pipe bottom and the wall thickness G twice as large as the sealing member, as viewed in the height direction, in which case the following applies:

CM＝F-H＝Y-X+2·G

in the above formula, CM represents the degree of deformation of the end portion of the pipe member in the height direction, and CM is a maximum value_maxAnd minimum value CM_minWithin the range of (a). In the case where the value of the first height X and the value of the second height Y of the pipe member are the same, CM_maxCorresponding to a wall thickness G of twice the sealing member, in other words CM _min2 · G. At a minimum value (C)_Mmin2 · G), the shape of the plurality of pipe ends of the pipe member is not broken or deformed at least in the height direction.

Especially the limit of deformation CM_maxSet to maximum value, set deformation limit CM_maxThe CM, which is defined as a minimum value so that it is a parameter that indicates a suitable deformation of the end of the tube member, has the purpose of ensuring that the surrounding tube member seals firmly and reliably against the sealing member located around the periphery during the press-fitting process.

Preferably, the pipe member may be formed of metal. Preferably, the cross-section of the tubular member expands in the second region in a plane aligned perpendicular to the longitudinal direction.

According to a modified example of the present invention, the movement cross section of the pipe member is limited by 2 side surfaces facing each other, and a narrow side or a longitudinal side of the movement cross section is formed by a pair of the side surfaces, respectively.

According to an alternative first embodiment of the invention, the contact edges of the sides of adjacently arranged tube members extending in the longitudinal direction are aligned at right angles to each other. In this case, rounded transitions having corner radii R are provided at the plurality of contact edges, respectively.

Preferably, the first height X of the first region of the tube member is greater than the value of two corner radii R of the tube member. In this case, the maximum value CM_maxRepresented by the formula:

in the above formula, a represents the ratio of the circumference of the pipe member in the pipe end portion before deformation to the circumference of the pipe member in the pipe end portion after deformation. The geometry and material properties allow the material of the pipe element to be deformed by the elongation limit to the maximum deformation, in particular expansion, of the pipe end up to the point where cracking of the material occurs.

According to an alternative second embodiment of the present invention, a plurality of side surfaces respectively arranged at the longitudinal sides of the movement cross section of the pipe member are bent toward the outside in a semicircular hollow cylinder shape and connected by a side surface of a narrow side having an outer radius R.

Preferably, the first height X of the first region of the pipe member corresponds to twice the radius R of the side of the narrow side of the pipe member bent toward the outside in a semicircular hollow cylinder shape. In this case, the maximum value CM_maxRepresented by the formula:

in the above formula, a corresponds to the tube expansion capacity.

One advantage of the present invention is that when the cross-section of the second region of the tubular members expands in a plane aligned perpendicular to the longitudinal direction, the travel passage bounded by the walls of the respective tubular members actually deforms from a rectangular cross-sectional shape to an oval cross-sectional shape.

According to a refinement of the invention, the tube element has a wall thickness of 0.22mm, a first height X of about 2.5mmm and a width W of about 10.8mm in the first region and a second height Y of about 4.69mm and a width of about 10.95mm in the second region 11.

According to still another preferred embodiment of the present invention, the pipe members at the pipe end portions are formed in a state of being expanded from the front at the areas of the apexes on the longitudinal sides, respectively, and finally, the walls of the pipe members are deformed outward in the height direction so as to have the forming portions, respectively. Therefore, the pipe member is formed to have a shape in the vertex regions of the upper surface and the lower surface, respectively. In this case, preferably, the tube member has an extension of about 7.6mm in the height direction at the maximum expansion region of the forming portion.

According to a preferred embodiment of the invention, the tube bottom can each have a ring member in the region of the web, said ring member serving to at least partially reduce the open cross section of the through-opening for receiving the sealing member.

In another preferred embodiment of the invention, the tube bottom may be formed as a side wall member of a collector of the heat transfer device.

Preferably, the heat transfer means may comprise 2 tube bottoms with through openings and 2 sealing members with through openings. The plurality of tube bottom portions are connected to the plurality of tube members in a fluid-tight manner, respectively, and in this case, the plurality of through openings each have the same shape as the outer shape of the tube member, and each tube member has a first end portion passing through the through opening formed in each first tube bottom portion and a second end portion passing through the through opening formed in the second tube bottom portion arranged.

Preferably, the plurality of tube members are formed of an aluminum alloy in a linear manner.

According to a refinement of the invention, the plurality of tube elements are aligned in one or more columns inside the array.

Preferably, the tube elements of a row of heat transfer devices aligned alongside one another, parallel and with broad sides relative to one another are arranged in such a way that a movement path for the second fluid, in particular for air, is formed between a plurality of tube elements arranged directly next to one another.

Preferably, in the moving path formed inside the first region by the plurality of pipe members arranged adjacently, a multifunctional disk or a reinforcing rib for changing a moving cross section and/or enlarging a heat transfer area is arranged. In this case, the multifunctional tray has an extension in the height direction corresponding to the interval F of the plurality of tube members adjacently aligned. Preferably, the multifunctional disc or the reinforcing bar is formed of an aluminum alloy.

In a preferred embodiment of the invention, the heat transfer device of the invention can be used as a heat exchanger between coolant and air in a coolant circulation system of a motor vehicle, in particular in an engine coolant circulation system.

In summary, the heat transfer device of the present invention has several advantages as follows:

expanding the application of the shielding gas brazing/mechanical assembly (CAB/MA) manufacturing principle within the framework of existing tube combinations;

even in the case of a minimum structural size or a minimum installation space requirement, in other words in the case of an optimum ratio of transferable thermal power to open volume, the maximum thermal power can be transferred with the optimum geometric ratio;

reduced complexity and material expense, thereby reducing manufacturing costs;

has a minimum weight;

a maximum sealing degree even in the case of a large temperature change, in other words, high thermal shock durability and high resistance to a temperature change, so that the opening and closing speeds of a plurality of valves located in a fluid circulation system, particularly in a coolant circulation system can be made fast in the case where the connection between the final pipe member, the sealing member, and the bottom of the pipe is smooth;

the use is ensured even under the condition of large pressure pulsation load;

the connection of the pipe ends inside the pipe bottom and the sealing member is permanently ensured by a press fit that performs a uniform sealing compression at a prescribed level, thereby ensuring maximum life.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the heat transfer device of the invention, the application of the protective gas brazing/mechanical assembly manufacturing principle is extended within the framework of the existing tube assembly, enabling the maximum thermal power to be delivered with the optimal geometric ratio, also in the case of minimum structural dimensions or minimum installation space requirements, in other words in the case of an optimal ratio of transferable thermal power to open volume.

Also, complexity and material expense is reduced, thereby reducing manufacturing costs with minimal weight.

Further, the present invention has a maximum sealing degree even in the case of a large temperature change, in other words, has high thermal shock durability and high resistance against a temperature change, so that the opening speed and the closing speed of a plurality of valves located in a fluid circulation system, particularly a coolant circulation system can be made fast in the case where the connection between the final pipe member, the sealing member, and the pipe bottom is smooth, and the use is ensured even in the case where the pressure pulsation load is large, and the connection of the pipe ends located in the pipe bottom and the sealing member inside is permanently ensured by press-fitting that performs uniform sealing compression at a predetermined level, thereby ensuring the maximum life.

Drawings

Further details, features and advantages of embodiments of the invention are described by the detailed description of embodiments of the invention with reference to the drawings. Wherein:

FIG. 1 illustrates in exploded detail a heat transfer device having an arrangement of tube members with a multifunctional tray, tube bottom, sealing member and collector supported in between as separate structural elements;

fig. 2a shows a side view of a tube component comprising a first region and a second region to form a flat tube;

fig. 2b and 2d each show a tube component having different displacement cross sections and formed from flat tubes in a perspective view;

FIG. 2c shows a detail of the tube member shown in FIG. 2 b;

FIG. 3a is a side detail view of the arrangement of tube members with the multifunctional disk supported in the middle of the tube member of the heat transfer device shown in FIG. 1;

FIG. 3b shows in side cross-sectional detail the arrangement of the intermediately supported multifunctional disk, the tube bottom and the tube members with sealing members of the heat transfer device shown in FIG. 1;

FIG. 3c shows a detail of the bottom of the tube with the sealing member shown in FIG. 3 b;

fig. 4a and 4b show in perspective and in top view, respectively, a tube element which is enlarged at the tube end section and which has an oval cross section similar to the tube element shown in fig. 2 a;

fig. 4c to 4f show the finally enlarged tube components at the tube end, as shown in fig. 4a and 4b, in perspective and top views, respectively;

fig. 5a and 5b show in perspective and in top view, respectively, a tube element which is enlarged at the tube end section and which has an oval cross section similar to the tube element shown in fig. 4 a;

FIG. 6a shows in side cross-sectional detail the arrangement of tube members shown in FIG. 5a within the through opening of the tube bottom with the sealing member; and

fig. 6b shows a detailed view of the bottom of the tube with the sealing member and tube member shown in fig. 6 a.

Detailed Description

Fig. 1 shows a tube base 5 of a heat transfer device 1 and a tube component 3 with a sealing component 7, in particular an array 2 of flat tubes. In the present drawing, a detailed view of the heat transfer device 1 including the multifunctional tray 4 supported in the middle, the tube member 3 arrangement 2 having the tube bottom 5, the sealing member 7, and the collector 9 is shown as an independent structural element. In case coolant is used as fluid, the collector 9 is also called coolant collector.

The array 2 formed from the flat tubes 3 is formed in one or more rows according to the output requirement, and can be adjusted in size, in other words in particular in length or width. The tube members 3 are arranged in two rows.

The tube elements 3 aligned alongside one another and parallel to one another are aligned with one another inside a row with wide sides, and finally, a movement path for a fluid, in particular for air, is formed in each case between immediately adjacent tube elements 3. In this case, the moving path extends between the respective pipe members 3. A row of tube members 3 is arranged in line with each other, extending between 2 collectors 9, respectively. The inner volume of the tube member 3 is connected with the inner volume of the collector 9.

Members for changing the movement cross section and/or enlarging the heat transfer area are formed in the movement path and thus the intermediate space of the adjacently arranged tube members 3. The multifunctional tray 4 is provided as a member for changing a movement cross section and/or enlarging a heat transfer area. Alternatively, reinforcing ribs may be used. Preferably, the multifunctional tray 4 is formed of a material having very excellent thermal conductivity, such as an aluminum alloy, as in the tube member 3.

In the assembled state of the device 1, a tube bottom 5, which can also serve as a side wall member of each collector 9, is provided on the front or narrow side of the array 2. In this case, the side where the ends of the pipe member 3 are aligned is referred to as a front face. The tube bottom portion 5 is formed by a deep-drawn portion, a perforated portion, or a hydroformed portion in a substantially rectangular sheet form made of metal, particularly aluminum alloy. In this case, a sheet is understood to be the end product of a flat calender formed from metal. Hydroforming, also known as high-pressure deformation, is considered to deform a sheet in a closed mold by the pressure that occurs in the tool through the water-oil-emulsion.

In addition to the rounded tube bottom 5 in the corner regions, the sealing member 7 also has through openings 6, 8 for receiving the tube members 3. In order to form a fluid tight connection between the individual tube members 3 and the tube bottom 5, the through openings 6 of the tube bottom 5 correspond to the through openings 8 of the sealing member 7 and also to the outer dimensions of the tube members 3. Between the through openings 6 of the tube bottom 5 webs 5-1 are formed, respectively.

The tube bottom 5 arranged on the opposite side of the collector 9 is fixedly connected to the tube member 3. The fixed connection can be regarded as a zero leakage sealed by the respective sealing member 7 technique. The tube bottom parts 5 are arranged on the array body 2 in vertical alignment with respect to the tube member 3 at the narrow side of the tube member 3.

Fig. 2a shows a tube component 3 formed from flat tubes in a side view, the tube component 3 comprising: a first region 10, as a heat transfer region, which is not deformed; a second region 11 as a deformed region, which is not deformed; and a connection portion for connecting the tube bottom portion 5. The

regions

10, 11 of the tube member are formed in a mutually connected state when viewed in the longitudinal direction a.

The tubular member 3 is at least partially expanded and deformed at the end of the tube. The cross section of the moving passage surrounded by the wall of the pipe member 3 is constantly and uniformly enlarged between a first region 10 where the pipe member 3 passes through the fluid circulation and a second region 11 toward the pipe end side. In the interior of the

regions

10, 11, the cross-sectional area of the displacement channel is constant, respectively. Preferably, the second region 11 of the tube member 3 may serve as a support surface for the sealing member 7 formed flat, in other words without structures such as cuts (notch) or grooves.

In the undeformed first region 10, the tube member 3 has an outer extension X, also referred to as the height of the first region 10, when viewed in the height direction c. The second region 11 of the at least partially expanded tube member 3 is, when viewed in the height direction c, extended by an outer extension Y also referred to as the height Y of the second region 11. The widths of the pipe members 3 extend in the depth direction b, respectively.

Fig. 2b and 2d show in perspective views tube components 3a, 3b which have different displacement cross sections and are formed from flat tubes. In these figures, one end face of the undeformed first region 10 of the tube members 3a, 3b is shown, respectively. The displacement cross section extends in a plane defined by the depth direction b and the height direction c.

The plurality of displacement cross sections are each limited by 2 sides facing each other, which sides each form a narrow side or a longitudinal side of the displacement cross section. The plurality of side surfaces formed in a pair of opposing directions have the same size. In this case, the side faces of the first pair of narrow sides have the same height X and are aligned parallel to one another in the height direction c, and the side faces of the second pair of longitudinal sides have the same width W in the depth direction b.

The actual difference between fig. 3a and 3b is the size of the height X and the shape of the transition or narrow side between adjacent sides.

The tube member 3a of fig. 2b has rounded transitions at the sides aligned at right angles to each other. The transitions have a corner radius R, the situation described above being particularly shown in the detail of the tube member 3a of fig. 2 c.

The side faces respectively arranged on the longitudinal sides of the movement cross section of the pipe member 3b shown in fig. 2d are respectively connected by narrow-side semicircular hollow cylinder-shaped side faces. In this case, the outer radius R of the side face corresponds to half the height X.

Fig. 3a and 3b show a detailed view of the arrangement 2 of tube members 3 with the multifunctional discs 4 supported in between of the heat transfer device 1 shown in fig. 1. In this case, fig. 3a shows a side view, and fig. 3b shows a detailed view of the array body 2 shown in fig. 3a on a side end surface in a state expanded in accordance with the tube bottom portion 5 and the sealing member 7.

The tube member 3 is formed at a height X in the first region 10 and at a height Y in the second region 11, in which case the extension of the tube member 3 within the first region 10 is smaller than the extension of the tube member 3 within the second region 11 when viewed from the height direction c. In the second region 11, the tube member 3 expands uniformly around the center axis aligned in the longitudinal direction a.

In the intermediate space inside the first region 10, which has a wide side and is formed in the tube members 3 aligned in a mutually side-by-side and parallel manner, the multifunctional plate 4 is provided as a member for changing the movement cross section and/or enlarging the heat transfer area. The multifunctional trays 4, which are respectively connected to the tube members 3 at the wide sides of the adjacently arranged tube members 3, completely fill the intermediate space between the tube members 3, and finally, the spacing F of the adjacently arranged tube members 3 also corresponds to the height F of the multifunctional trays 4 when viewed in the height direction c. In this case, the multifunctional tray 4 is formed only in the first region 10 of the tube member 3.

The tube member 3 has a second region 11 and is arranged in the through openings 6, 8 of the sealing member 7 and the tube bottom 5, respectively. A web 5-1 is formed between the through openings 6 of the tube bottom 5 arranged adjacently along the height direction c, and the web restricts each through opening 6 in the depth direction b and actually contacts the wide side of the tube member 3 in a state of being connected to the seal member 7. Fig. 3c shows a detailed view of the web 5-1 of the tube bottom 5 with the sealing member 7 shown in fig. 3 b.

In the intermediate space inside the second region 11, which has wide sides and is formed in the tube members 3 aligned in a mutually side-by-side and parallel manner, the web 5-1 of the tube bottom 5 and the sealing member 7 are arranged. Therefore, when viewed in the height direction c, the intermediate space between the adjacently arranged tube members 3 is completely filled by one web 5-1 of the tube bottom 5 and 2 sections of the sealing member 7. The web 5-1 is formed at a height H when viewed in the height direction c, and 2 sections of the sealing member 7 each have a wall thickness G.

In the first region 10 of the tube member 3, the extension of the unit formed by the tube member 3 and the multifunction board 4 is represented by a value obtained by adding the height X of the tube member 3 to the height F of the multifunction board 4 in the height direction c. In the second region 11 of the tube member 3, the value obtained by adding the height H of the web 5-1 at the bottom of the tube and the double-wall thickness G of the sealing member 7 to the height Y of the tube member 3 in the height direction c represents the extension of the unit formed by the tube member 3, the sealing member 7, and the web 5-1 of the bottom of the tube 5, and the following equation is derived from the above-described situation:

X+F＝Y+H+2·G----------(1)

after converting equation 1, it is expressed by the following equation:

CM＝F-H＝Y-X+2·G----------(2)

in the above equation, CM represents an optimum range of a difference between the height H of the web 5-1 of the tube bottom 5 and the height F of the multifunction tray 4 and a degree of deformation of the end portion of the tube member 3 in the height direction c as an extension portion extending in the height direction c formed between the adjacent through openings 6 of the tube bottom 5.

CM_max≥CM≥CM_min----------(3)

The above equation represents the best relationship between the configuration of the tube member 3 with reference to the radius R, the width W and the height X of the first region 10 and the deformation of the tube member 3 in the end portion with reference to the height Y of the second region 11, the height F of the multifunctional disc 4, the height H of the web 5-1 between the through openings 6 of the bottom part 5 of the tube and the wall thickness G of the sealing member 7. In this case, the maximum value CM of the circular movement cross section derived from the deformation of the pipe end of the pipe member 3 is specified with reference to, in particular, the following equations 4 to 6_maxMinimum value CM of pipe end portion of pipe member 3 without deformation_minIn the middle range.

The side faces are aligned at right angles to each other, according to fig. 2b and 2c in which the transitions between adjacent side faces are rounded, when the height X of the first region 10 is greater than the value of twice the corner radius R of the pipe member (3a) (X)>2. R), maximum value CM_maxRepresented by the formula:

according to fig. 2d, which has longitudinal side faces connected by narrow-side, half-cylinder-shaped side faces, the maximum value CM is equal to the maximum value CM when the height X of the first region 10 is equal to the double radius R of the pipe component 3b (X ═ 2-R)_maxRepresented by the formula:

since the pipe member 3 is not expanded or deformed at the pipe end portion, eventually, the height Y of the second region 11 is equal to the height X of the first region 10 of the

pipe members

3, 3a, 3b (Y ═ X), thereby determining the minimum limit CM_min. Thus, the minimum value CM_minThe following equation always represents a value generally corresponding to twice the wall thickness G of the sealing member 7:

CM_min＝2·G----------(6)

the parameter a expresses the pipe expansion capacity as the ratio of the circumference of the pipe member in the pipe end portion before deformation to the circumference of the pipe member in the pipe end portion after deformation.

Fig. 4a and 4b show a tube element 3, which is at least partially enlarged at the end of the tube, in a perspective view and in a plan view, similar to the tube element 3a shown in fig. 2a or fig. 2b and 2c, respectively. The tube element 3 is deformed and enlarged in the area of the tube end, and the displacement channel, which is finally limited by the wall of the tube element 3, changes from a substantially rectangular cross-sectional shape to an oval cross-sectional shape. The elliptical cross-sectional shape of the displacement channel is very stable to external pressure, in particular to the pressure provided by the compressed sealing member 7.

In this case, the undeformed pipe member 3 is formed with a wall thickness of 0.22mm, a width W of about 10.8mm, and a height X of 2.5 mm. The at least partially enlarged tube member 3 has a height of about 4.69mm in the second region 11, for example in the region of the maximum extension Y, with a width of about 10.95 mm. The second region 11 is formed by a support surface 13 of a given size with which the wall of the tubular member 3, which is located at the bottom 5 of the tube or at the sealing member 7 compressed between the tubular member 3 and the bottom 5 of the tube, comes into contact.

The tubular member 3 is eventually enlarged in the region of the apex 12 in order to withstand the resistance of the compressed sealing member 7. In this case, in order to further increase the rigidity of the support surface 13 of the seal member 7, the wall of the pipe member 3 is deformed outward on the vertical side. In the finally deformed state, the structure of the wall of the tube member 3 is reinforced, particularly on the longitudinal side.

Fig. 4c to 4f show the finally enlarged tube component 3 in the tube end in perspective and plan views. According to fig. 4a and 4b, after the pipe element 3 has been at least partially expanded, the pipe element 3 is finally expanded starting from the front in the deformed region of the respective pipe end. In this case, in particular, the edges of the upper and lower faces are deformed outward in the height direction c. By using a perforating blade, in the second region 11, the apex 12 of the tube member 3 is enlarged relative to the sealing member 7, and the compression of the sealing member 7 is increased. After the blade is removed, the elastic tube material is restored in a minimum form toward the direction of the starting position, in which case the compression of the sealing material 7 is maintained as it is within a predetermined range. Finally, the pipe member 3 has a forming portion 14 in the region of the apex 12 of each of the upper and lower surfaces.

The wall of the pipe member 3 deformed at the pipe end by the forming part 14 is formed continuously and without cracks. The shape of the shaped portion 14 serves, on the one hand, to increase the structural rigidity of the wall of the tube member 3 and, on the other hand, to fix and seal inside the through-opening 6 in the tube bottom 5. In this case, the fixing force for preventing the relative position change of the pipe member 3 with respect to the bottom portion 5 and the movement of the pipe member 3 in the inside of the bottom portion 5 also increases.

The finally enlarged tube member 3 has an extension Z of about 7.6mm, for example, at the maximum enlarged area of the forming section 14.

The device 1 formed with the tube member 3 has a very high thermal shock-durability by forming a flexible and not rigid tube member-sealing member-tube bottom-connection on at least one side of the arrangement 2.

Fig. 5a and 5b show, in perspective and plan view, a tube element 3 which is partially enlarged in the respective tube end and which, like the tube element shown in fig. 4a, has an oval cross section in the direction of action 15 of the pressure supplied from the outside. The pressure is generated by a sealing member, not shown, which is in contact over the entire range.

In this case, the diameter of the arc-shaped face of the narrow side of the deformed end portion of the pipe member 3 is smaller than the diameter of the end portion of the pipe member 3 shown in fig. 4a when viewed in cross section. The wall of the pipe member 3c has a thicker cross section in an elliptical shape that better withstands the pressure supplied from the outside.

The pipe member 3 may also be formed by a combination of structural features such as the oval shape of the cross-section in the pipe end of fig. 5a and the deformation of the pipe end having the forming section 14 in the area of the apex 12 of the upper and lower faces of fig. 4 c-4 f.

Fig. 6a shows a detailed view of the arrangement of tube members 3 in the through opening 6 of the tube bottom 5 with the sealing member 7 in a side end view. Fig. 6b shows a detailed view of the tube bottom 5 with the sealing member 7 and the tube member 3 shown in fig. 6 a.

Preferably, fig. 6a shows in particular an arrangement of the enlarged deformed tube members 3 with an oval cross-section arranged through openings formed in the tube bottom 5 and the sealing member 7. Due to the enlargement of the tube member 3, the tube member 3 is firmly connected with the sealing member 7 arranged between the tube member 3 and the edge of the through opening of the tube member 3 mentioned above, and is connected with the tube bottom 5 in a fluid-tight manner.

The tube bottom 5 has in the region 16 of the web 5-1 respective ring members 17 which at least partially reduce the open cross-section of the through-opening 6 for receiving the sealing member 7 and the tube member 3 in order to locally increase the compression of the sealing member 7 in the region 16. The ring member 17 increases the compression of the sealing member 7, which is less compressed, as expected, by further compressing the sealing member 7 in a predetermined interval or predetermined plane, and finally in the opposite case, particularly in the apex region of the pipe member 3. Since the sealing member 7 is strongly compressed only in a small area, the resulting force on the pipe wall will be less, so that the pipe wall will not collapse.

The sealing member 7 is compressed effectively in particular around the entire tube in the region 16 of the apex 12, the device 1 can again be formed by any combination of the oval shape of the cross-section in the tube end of fig. 5a and the deformation of the tube end of the tube member 3 with the shaping 14 in the region of the apex 12 of the upper and lower faces of fig. 4c to 4f, and the structural features of the tube member 3, and the provision of the ring member 17 in the region of the web 5-1 of the tube bottom 5.

The connection of the tube bottom 5 and the tube member 3 ensures that the tube member 3 is arranged in the exact position of the through openings 6, 8 and thus creates a reliable fluid-tight connection. In order to ensure a sufficient and reliable compression of the sealing member 7, the intentional enlargement is predetermined as the final extension of the tube member 3. In this case, the compression of the sealing member 7 ranges from 10% to 50%, in which case most of the compression is performed after the sealing member 7 and the tube bottom 5 are installed in the tube member 3.

Industrial applicability

Claims

1. A heat transfer device (1) for transferring heat between a first fluid and a second fluid, having an arrangement (2), said arrangement (2) comprising: a tube member (3, 3a, 3b, 3c) for passing a first fluid; at least one tube bottom (5) having a through opening (6); and at least one sealing member (7) having a through opening (8), the heat transfer device (1) being characterized in that,

the pipe members (3, 3a, 3b, 3c) are formed of flat pipes, each of which includes: a first region (10) having a first height (X) and a width (W); and at least one second region (11) having a support surface (13) arranged at one end of the tube member (3, 3a, 3b, 3c) and having a second height (Y),

the sealing members (7) are arranged between the outer peripheral edge of the through opening (6) of the tube bottom (5) and the support surface (13) and have a wall thickness (G),

the pipe members (3, 3a, 3b, 3c) having the wide sides are arranged in parallel with each other and aligned in a state of being spaced apart from each other by a space (F) in the first region (10),

webs (5-1) having a height (H) are respectively arranged between the through-openings (6) arranged adjacent to the tube bottom (5),

when viewed in the height direction (c), the extension within the first region (10) of the tube member (3, 3a, 3b, 3c) expressed by the value of the first height (X) of the tube member (3, 3a, 3b, 3c) added to the interval (F) corresponds to the extension within the second region (11) of the tube member (3, 3a, 3b, 3c) expressed by the value of the height (H) of the web (5-1) at the tube bottom (5) and the double wall thickness (G) of the sealing member (7) added to the second height (Y) of the tube member (3, 3a, 3b, 3c),

CM＝F-H＝Y-X+2·G，

in the above formula, CM represents the degree of deformation of the end portions of the pipe members (3, 3a, 3b, 3c) in the height direction (c), and is at a maximum value (CM)_max) And minimum value (CM)_min) Within the range therebetween, CM is equal to the height (X, Y) of the pipe member (3, 3a, 3b, 3c)_minWith CM_min2. G.

2. A heat transfer device (1) according to claim 1, characterized in that the tube member (3, 3a, 3b, 3c) is formed of metal.

3. A heat transfer device (1) according to claim 1, characterised in that the cross-section of the tube member (3, 3a, 3b, 3c) expands in the second region (11) in a plane aligned perpendicular to the longitudinal direction (a) of the tube member (3, 3a, 3b, 3 c).

4. A heat transfer device (1) according to claim 1, characterized in that the movement cross-section of the tube member (3, 3a, 3b) is limited by 2 sides facing each other, a narrow side or a longitudinal side of the movement cross-section being formed by a pair of the sides, respectively.

5. A heat transfer device (1) according to claim 4, characterised in that contact edges of side faces of the tube members (3, 3a) arranged adjacently, which extend in the longitudinal direction (a), are aligned at right angles to each other, at which contact edges rounded transitions having corner radii (R) are provided, respectively.

6. A heat transfer device (1) according to claim 5, characterized in that the first height (X) of the first area (10) of the tube member (3, 3a) is larger than the value of two times the corner radius (R) of the tube member (3, 3a), the maximum value (CM)_max) Represented by the formula:

in the above formula, a corresponds to the tube expansion capacity.

7. The heat transfer device (1) according to claim 4, characterized in that a plurality of side faces respectively arranged at the longitudinal sides of the movement cross section of the pipe members (3, 3b) are bent toward the outside in a semicircular hollow cylinder shape and connected by a side face of a narrow side having an outer radius (R).

8. Heat transfer device (1) according to claim 7, characterized in that the first height (X) of the first area (10) of the above-mentioned tube member (3, 3a) corresponds to twice the radius (R), the maximum value (CM), of the side of the narrow side of the tube member (3, 3b) bent towards the outside in the shape of a semi-circular hollow cylinder_max) Represented by the formula:

in the above formula, a corresponds to the tube expansion capacity.

9. A heat transfer device (1) according to claim 2, characterized in that the tube member (3, 3a, 3b) has a wall thickness of 0.22mm, a first height (X) of about 2.5mm and a width (W) of about 10.8mm in a first region (10) and a second height (Y) of about 4.69mm and a width (W) of about 10.95mm in a second region (11).

10. The heat transfer device (1) according to claim 2, characterized in that the tube members (3, 3a, 3b) at the tube ends are formed in a state of expanding from the front in the region of the apexes (12) on the longitudinal sides, and the walls of the tube members (3, 3a, 3b) are deformed outward in the height direction (c) so as to have the formed portions (14).

11. Heat transfer device (1) according to claim 10, characterised in that the tube elements (3, 3a, 3b) have an extension (Z) in the height direction (c) of about 7.6mm in the area of maximum expansion of the profile (14).

12. The heat transfer device (1) according to claim 1, characterised in that the tube bottom (5) has a ring element (17) in each case in the region (16) of the web (5-1), the ring element (17) being intended to at least partially reduce the open cross section of the through-opening (6) for accommodating the sealing element (7) and the tube element (3, 3a, 3b, 3 c).

13. Heat transfer device (1) according to claim 1, characterised in that the tube bottom (5) is formed as a side wall member of a collector (9) of the heat transfer device (1).

14. The heat transfer device (1) according to claim 13, wherein 2 tube bottom parts (5) having through openings (6) and 2 sealing members (7) having through openings (8) are formed, the tube bottom parts (5) being connected in a fluid-tight manner with the respective tube members (3, 3a, 3b, 3c), the through openings (6, 8) having the same shape as the outer shape of the tube members (3, 3a, 3b, 3c), respectively, the respective tube members (3, 3a, 3b, 3c) having a first end part passing through the through opening (6) formed in the respective first tube bottom parts (5) and a second end part passing through the through opening (6) formed in the second tube bottom part (5) being arranged.

15. A heat transfer device (1) according to claim 2, characterized in that the tube members (3, 3a, 3b, 3c) are formed of an aluminum alloy.

16. A heat transfer device (1) according to claim 1, characterized in that an array of tube members (3, 3a, 3b, 3c) of the heat transfer device (1) aligned alongside one another, parallel and with broad sides with respect to one another is arranged in such a way that a movement path for the second fluid is formed between the tube members (3, 3a, 3b, 3c) arranged directly next to one another, respectively.

17. The heat transfer device (1) according to claim 16, characterized in that in the movement path formed inside the first region (10) by the adjacently arranged tube members (3, 3a, 3b, 3c), a multifunctional tray (4) or a rib for changing the movement cross section and/or enlarging the heat transfer area is arranged, the multifunctional tray (4) having an extension in the height direction (c) corresponding to the interval (F) of the adjacently arranged tube members (3, 3a, 3b, 3 c).

18. The heat transfer device (1) according to claim 17, characterized in that the multifunctional disc (4) or the ribs are formed of an aluminum alloy.

19. Use of a heat transfer device (1), characterized in that the heat transfer device (1) according to any one of claims 1 to 18 is used as a heat exchanger between coolant and air in a coolant circulation system of a motor vehicle, in particular in an engine coolant circulation system.