US20070000657A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- US20070000657A1 US20070000657A1 US10/572,482 US57248206A US2007000657A1 US 20070000657 A1 US20070000657 A1 US 20070000657A1 US 57248206 A US57248206 A US 57248206A US 2007000657 A1 US2007000657 A1 US 2007000657A1
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- US
- United States
- Prior art keywords
- heat exchanger
- rims
- flanks
- tube
- tubes
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/04—Arrangements for sealing elements into header boxes or end plates
- F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
- F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
- F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
- B21D39/06—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes in openings, e.g. rolling-in
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0082—Charged air coolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2225/00—Reinforcing means
- F28F2225/08—Reinforcing means for header boxes
Definitions
- the present invention relates to a heat exchanger, in particular a charge-air cooler for a motor vehicle.
- a charge-air cooler is described, for example, in DE 197 57 034 A1.
- the hot air is introduced into a first header passage of the heat exchanger, where it is distributed and flows into flat tubes which open out into the header passage.
- the flat tubes are arranged next to one another and with the side faces which include the long sides of their cross section parallel to one another, forming a flow path through which cooling air is routed.
- Cooling fins which are responsible for effective heat exchange between the flat tubes and the cooling air stream, are arranged between the flat tubes in the flow path. After the cooling air stream has passed through, the flat tubes open out into a second header passage, which feeds the cooled, compressed charge air flowing into it for combustion in the engine.
- the tubes are usually fitted into openings in a tube plate and are soldered in place in a fluid-tight manner.
- this soldered join is subject to high mechanical loads on account of rapid pressure changes.
- the narrow sides of flat tubes do not satisfy the increasing demands on strength, which can result in leaks in particular in regions of tube-plate joins of this type which face the sides of the tube plate.
- a simple way of increasing the strength of tube-plate joins is to use tubes and/or tube plates with a greater wall thickness or external and/or internal fins with a greater material thickness.
- the increased mechanical stability is useful in both cases, but the increased outlay that is required on material costs and weight is very high.
- the object of the invention is to provide a heat exchanger, in particular a charge-air cooler, in which mechanical loads on tube-plate joins are reduced without an increased outlay on material.
- a heat exchanger has tubes which are suitable to have a first medium flowing through them and a second medium flowing around them, so that heat can be transferred from the first medium to the second medium or vice versa.
- At least one header box which is in communication with the tubes comprises at least one tube plate, the tube plate being of essentially flat design and having rims into which the tubes can be fitted in order to form the communicating connection to the header box.
- the basic concept of the invention is to geometrically configure those regions of the tube plate which surround the rims in the form of depressions or elevations in such a manner that the rims are in each case arranged on the “base” of a depression or on the “summit” of an elevation.
- the rims are enclosed peripherally by flanks, namely the flanks of the depressions or elevations.
- a geometrical configuration of this type, particularly the peripheral configuration of the flanks increases the flexural rigidity of the tube plate in a plurality of directions in comparison to a flat tube plate, thus reducing deformations that occur due to a compressive load on the header box, as a result of which joins of tubes to the tube plate are mechanically relieved of load.
- the depressions or elevations are preferably of such a width that the flanks of in each case two adjacent rims border each other with a reinforcing bead being formed.
- the configuration of the heat exchanger according to the invention increases its mechanical strength and therefore also its service life without requiring an increased outlay on material or number of parts.
- the flanks each have an essentially constant width over the circumference of a rim. This essentially uniformly increases the flexural rigidity of the tube plate in all directions.
- the tubes are designed as flat tubes and are arranged in one or more rows.
- the rims and the beads which are situated in between and are formed by the flanks are then of elongate design corresponding to the tube cross sections.
- the flanks preferably each have a rounded portion with an approximately constant radius of curvature or a plurality of rounded portions with different radii of curvature. This achieves a particularly good approximation to a semicircular cross section of the beads situated between the rims, thus resulting in particularly high flexural rigidity.
- the flanks each comprise one or more planar regions, so that the flanks or the beads have a faceted form between the rims. This allows reliable production with low manufacturing tolerances.
- the at least one planar region particularly preferably forms an obtuse angle with the respective rim. This means that the rim itself brings about an additional increase in the flexural rigidity of the tube plate, since the rim faces in the same direction as the depression or elevation on the “base” of which or on the “summit” of which the rim is situated.
- the angle between the planar region of the flank and the rim is preferably between 300 and 600, particularly preferably approximately 45°.
- a width of the flank is, under some circumstances, approximately equal to a height of the flank, thus resulting in particularly high stability of the tube plate to deformations.
- the rims face out of the at least one header box. This has, if appropriate, the advantage that in each case one region of the flanks, which region is adjacent to an edge of the tube plate, merges into an edge of the tube plate, which edge is raised under some circumstances, thus resulting in a further increase in strength of the tube plate.
- the heat exchanger according to the invention is designed as a charge-air cooler which can particularly preferably be used in motor vehicles.
- the charge-air cooler has two header boxes, a first of which is provided to distribute charge air and a second of which is provided to collect charge air.
- each of the header boxes has precisely one tube plate, which is provided with a row of tube openings.
- the cooling medium used is preferably air, although other cooling media, such as water or coolant, are also conceivable.
- a tube plate is produced by one or more edge regions of a planar metal sheet being raised by means of a forming process and depressions, which border one another, being placed into the metal sheet.
- the depressions each have an essentially planar base surface and a flank enclosing and encircling the base surface. Subsequently, the base surfaces of the depressions are pierced with the aid of a draw-through process with rims being formed. If tubes are to be fitted into the tube plate from the side of the depressions, it is particularly preferable for introductory slopes to be impressed therein in order to facilitate a fitting of tubes in this way into the rims.
- An embodiment of a tube plate with one or more rows of identical flanks and/or rims is advantageous in terms of manufacturing.
- FIG. 1 shows an oblique view of a tube plate
- FIG. 2 shows a side view of a tube plate with a tube inserted
- FIG. 3 shows a longitudinal section through a tube plate with tubes inserted
- FIG. 4 shows a longitudinal section through an excerpt of a tube plate with a tube inserted
- FIG. 5 shows a longitudinal section through an excerpt of a tube plate with a tube inserted.
- FIG. 1 shows an excerpt from a heat exchanger 10 in the form of a perspective illustration.
- a header box 20 for distributing a first medium comprises a tube plate 30 and a box cover (not shown), which are welded to each other at a common contact surface 50 .
- the box cover is fitted into the tube plate 30 .
- the box cover it is also conceivable for the box cover to be fitted onto the tube plate 30 or attached to the tube plate 30 in some other way.
- a tube plate and a box cover are joined to one another by soldering, adhesive bonding or a positive lock or are formed as a single part or integrally with one another, i.e., for example from a deformed plate.
- the tube plate 30 has a tube opening 60 , the edge 70 of which is deformed out of the header box as what is described as a rim.
- An essentially rectangular flat tube can be fitted into the tube opening 60 and can be soldered or welded to the tube plate 30 .
- Corrugated fins which adjoin the flat tube (not shown) on both sides and are soldered to said flat tube, so that heat transfer from a medium flowing through the tube to a medium flowing around the tube and the fins or vice versa is increased, are not shown.
- the heat exchanger 10 comprises an entire row of alternating flat tubes and corrugated fins, which form what is known as a tube-fin block.
- the header box 20 is acted upon by a medium under pressure, the header box 20 is under certain circumstances deformed in such a manner that its cross-sectional shape approximates a circular shape.
- the rim 70 is enclosed by an encircling flank 90 which adjoins the rim at an obtuse angle.
- the flank has a width which is essentially constant all the way around the rim 70 . This results in a uniform stiffening of the tube plate 30 both in the longitudinal direction of the tube plate, by means of the flank regions 91 , 92 on the end sides of the rim 70 , and also in the transverse direction of the tube plate, by means of the flank regions 93 , 94 on the longitudinal sides of the rim 70 .
- This reduced deformation of the tube plate 30 involves a reduction in the mechanical load on the tube or on the tube-plate join.
- the end sides of the flat tube which in mechanical terms are under the highest loads in the event of such pressure-induced deformations, are relieved of load as a result.
- the tube 120 is fitted into the tube opening 160 sufficiently far for an upper edge region 121 of the tube 120 to project beyond the tube plate 130 .
- This ensures good utilization of an inner surface (not visible), which faces the tube 120 , of the rim 170 as a bearing surface for a tube-plate join. This serves, for example, to ensure sealed soldering.
- the tube opening 160 is situated in an essentially planar central region 131 of the tube plate 130 .
- the rim 170 is enclosed by a flank 190 , the end sides 191 , 192 of which, firstly, merge into the rim 170 at an obtuse angle and, secondly, likewise at an obtuse angle, merge into a raised edge region 132 of the tube plate 130 .
- An additional reduction in load on the tube 120 and/or the tube-plate join is brought about on account of the associated S-shaped cross section of the tube plate 130 in the region of the cover connection surface 150 —edge region 132 —flank region 191 / 192 —rim 170 .
- FIG. 3 shows a further exemplary embodiment of part of a heat exchanger 210 in a longitudinal section.
- Tubes 220 , 221 , 222 are fitted in rims 270 , 271 , 272 of a tube plate 230 .
- the rims 270 , 271 , 272 face out of the header box (otherwise not shown) and the tubes 220 , 221 , 222 do not protrude over the tube plate 230 or the rims 270 , 271 , 272 thereof.
- flanks 290 which each have a planar subregion 295 .
- the planar subregion 295 encloses an obtuse angle with the rim 270 , as a result of which the reinforcing effect of the depression, which is formed by the flank 290 , in the tube plate 230 is additionally increased.
- the flanks 290 are directly adjacent to one another here, so that beads 299 are formed, which can be seen in cross section in FIG. 3 . As is clearly shown in this cross section, the beads 299 do not have any horizontal regions situated between the flanks 290 .
- the width b is advantageously similar to the height h of the flanks 290 , particularly preferably is approximately the same. For this reason, the angle between the planar subregion 295 of the flank 290 and the rim 270 is approximately 45°. For the beads 299 , this results in a bead angle ⁇ of approximately 90°, which is associated with a particularly high stiffening effect of the beads 299 .
- FIG. 4 shows the excerpt of a modified configuration of the heat exchanger from FIG. 3 .
- the tube 320 protrudes here over the rim 370 , but ends below a surface 335 of the tube plate 330 .
- a soldered join is improved by a soldering gap 376 to be additionally added to the soldering gap 375 .
- the soldering gap serves here at the same time as an introductory slope for facilitating the fitting of the tube 320 into the tube plate 330 .
- the tube 420 protrudes beyond the rim 470 and beyond a surface 435 of the tube plate 430 . Owing to the associated, relatively large tolerances with respect to the length of the tube 420 , a further increase in the manufacturing reliability results.
Abstract
Disclosed is a heat exchanger comprising pipes and at least one receptacle (20). Said receptacle encompasses at least one pipe bottom (30) that is provided with passages (70), said passages (70) being surrounded by flanks (91-94).
Description
- The present invention relates to a heat exchanger, in particular a charge-air cooler for a motor vehicle.
- In order to increase the power of an internal combustion engine, it is possible for the air which is to be fed for combustion to be compressed, for example using a turbocharger, before it is fed to the combustion chambers of the internal combustion engine. However, compressing the air at the same time also heats it, which is disadvantageous for an optimum sequence of the combustion process. By way of example, this can cause premature ignition or increased emissions of nitrogen oxide. To avoid the disadvantageous consequences of combustion of superheated air supplied, a heat exchanger designed as a charge-air cooler, which can be used to cool the compressed air to an acceptable temperature before its combustion, is connected downstream of a turbocharger.
- A charge-air cooler is described, for example, in DE 197 57 034 A1. In the heat exchanger disclosed therein, the hot air is introduced into a first header passage of the heat exchanger, where it is distributed and flows into flat tubes which open out into the header passage. The flat tubes are arranged next to one another and with the side faces which include the long sides of their cross section parallel to one another, forming a flow path through which cooling air is routed. Cooling fins, which are responsible for effective heat exchange between the flat tubes and the cooling air stream, are arranged between the flat tubes in the flow path. After the cooling air stream has passed through, the flat tubes open out into a second header passage, which feeds the cooled, compressed charge air flowing into it for combustion in the engine.
- In heat exchangers, such as in particular charge-air coolers of this type, the tubes are usually fitted into openings in a tube plate and are soldered in place in a fluid-tight manner. Each time that compressed air is applied, this soldered join is subject to high mechanical loads on account of rapid pressure changes. In particular the narrow sides of flat tubes do not satisfy the increasing demands on strength, which can result in leaks in particular in regions of tube-plate joins of this type which face the sides of the tube plate.
- A simple way of increasing the strength of tube-plate joins is to use tubes and/or tube plates with a greater wall thickness or external and/or internal fins with a greater material thickness. The increased mechanical stability is useful in both cases, but the increased outlay that is required on material costs and weight is very high.
- Other proposed solutions deal with a reduction in the mechanical loading on the tube-plate joins by the use of tie rods in the charge-air boxes. These tie rods stabilize the charge-air boxes and thereby relieve the load on the tube-plate joins, but also increase the outlay on material and the pressure loss caused by the charge-air cooler.
- The object of the invention is to provide a heat exchanger, in particular a charge-air cooler, in which mechanical loads on tube-plate joins are reduced without an increased outlay on material.
- This object is achieved by a heat exchanger having the features of claim 1.
- According to claim 1, a heat exchanger has tubes which are suitable to have a first medium flowing through them and a second medium flowing around them, so that heat can be transferred from the first medium to the second medium or vice versa. At least one header box which is in communication with the tubes comprises at least one tube plate, the tube plate being of essentially flat design and having rims into which the tubes can be fitted in order to form the communicating connection to the header box.
- The basic concept of the invention is to geometrically configure those regions of the tube plate which surround the rims in the form of depressions or elevations in such a manner that the rims are in each case arranged on the “base” of a depression or on the “summit” of an elevation. As a result of this, the rims are enclosed peripherally by flanks, namely the flanks of the depressions or elevations. A geometrical configuration of this type, particularly the peripheral configuration of the flanks, increases the flexural rigidity of the tube plate in a plurality of directions in comparison to a flat tube plate, thus reducing deformations that occur due to a compressive load on the header box, as a result of which joins of tubes to the tube plate are mechanically relieved of load. The depressions or elevations are preferably of such a width that the flanks of in each case two adjacent rims border each other with a reinforcing bead being formed.
- The configuration of the heat exchanger according to the invention increases its mechanical strength and therefore also its service life without requiring an increased outlay on material or number of parts.
- Advantageous embodiments of the invention are the subject matter of the subclaims.
- According to a preferred embodiment, the flanks each have an essentially constant width over the circumference of a rim. This essentially uniformly increases the flexural rigidity of the tube plate in all directions.
- According to an advantageous embodiment, the tubes are designed as flat tubes and are arranged in one or more rows. The rims and the beads which are situated in between and are formed by the flanks are then of elongate design corresponding to the tube cross sections.
- The flanks preferably each have a rounded portion with an approximately constant radius of curvature or a plurality of rounded portions with different radii of curvature. This achieves a particularly good approximation to a semicircular cross section of the beads situated between the rims, thus resulting in particularly high flexural rigidity.
- According to another embodiment, the flanks each comprise one or more planar regions, so that the flanks or the beads have a faceted form between the rims. This allows reliable production with low manufacturing tolerances.
- The at least one planar region particularly preferably forms an obtuse angle with the respective rim. This means that the rim itself brings about an additional increase in the flexural rigidity of the tube plate, since the rim faces in the same direction as the depression or elevation on the “base” of which or on the “summit” of which the rim is situated.
- The angle between the planar region of the flank and the rim is preferably between 300 and 600, particularly preferably approximately 45°. In this case, a width of the flank is, under some circumstances, approximately equal to a height of the flank, thus resulting in particularly high stability of the tube plate to deformations.
- According to an advantageous configuration, the rims face out of the at least one header box. This has, if appropriate, the advantage that in each case one region of the flanks, which region is adjacent to an edge of the tube plate, merges into an edge of the tube plate, which edge is raised under some circumstances, thus resulting in a further increase in strength of the tube plate.
- According to a preferred development, the heat exchanger according to the invention is designed as a charge-air cooler which can particularly preferably be used in motor vehicles. In particular, the charge-air cooler has two header boxes, a first of which is provided to distribute charge air and a second of which is provided to collect charge air. It is advantageous for each of the header boxes to have precisely one tube plate, which is provided with a row of tube openings. It is also advantageous to use a row of flat tubes with in particular soldered corrugated fins between them, since this increases the heat-transfer surface area. The cooling medium used is preferably air, although other cooling media, such as water or coolant, are also conceivable.
- According to an advantageous embodiment of the invention, a tube plate is produced by one or more edge regions of a planar metal sheet being raised by means of a forming process and depressions, which border one another, being placed into the metal sheet. In this case, the depressions each have an essentially planar base surface and a flank enclosing and encircling the base surface. Subsequently, the base surfaces of the depressions are pierced with the aid of a draw-through process with rims being formed. If tubes are to be fitted into the tube plate from the side of the depressions, it is particularly preferable for introductory slopes to be impressed therein in order to facilitate a fitting of tubes in this way into the rims.
- An embodiment of a tube plate with one or more rows of identical flanks and/or rims is advantageous in terms of manufacturing.
- The invention is explained below on the basis of exemplary embodiments and with reference to the drawings, in which
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FIG. 1 shows an oblique view of a tube plate, -
FIG. 2 shows a side view of a tube plate with a tube inserted, -
FIG. 3 shows a longitudinal section through a tube plate with tubes inserted, -
FIG. 4 shows a longitudinal section through an excerpt of a tube plate with a tube inserted, and -
FIG. 5 shows a longitudinal section through an excerpt of a tube plate with a tube inserted. -
FIG. 1 shows an excerpt from aheat exchanger 10 in the form of a perspective illustration. Aheader box 20 for distributing a first medium comprises atube plate 30 and a box cover (not shown), which are welded to each other at acommon contact surface 50. In this case, the box cover is fitted into thetube plate 30. However, it is also conceivable for the box cover to be fitted onto thetube plate 30 or attached to thetube plate 30 in some other way. In other exemplary embodiments (not shown), a tube plate and a box cover are joined to one another by soldering, adhesive bonding or a positive lock or are formed as a single part or integrally with one another, i.e., for example from a deformed plate. - The
tube plate 30 has a tube opening 60, theedge 70 of which is deformed out of the header box as what is described as a rim. An essentially rectangular flat tube can be fitted into the tube opening 60 and can be soldered or welded to thetube plate 30. Corrugated fins which adjoin the flat tube (not shown) on both sides and are soldered to said flat tube, so that heat transfer from a medium flowing through the tube to a medium flowing around the tube and the fins or vice versa is increased, are not shown. In total, theheat exchanger 10 comprises an entire row of alternating flat tubes and corrugated fins, which form what is known as a tube-fin block. - If the
header box 20 is acted upon by a medium under pressure, theheader box 20 is under certain circumstances deformed in such a manner that its cross-sectional shape approximates a circular shape. To oppose a deformation of this type, therim 70 is enclosed by an encirclingflank 90 which adjoins the rim at an obtuse angle. The flank has a width which is essentially constant all the way around therim 70. This results in a uniform stiffening of thetube plate 30 both in the longitudinal direction of the tube plate, by means of theflank regions rim 70, and also in the transverse direction of the tube plate, by means of theflank regions rim 70. - This results in reduced deformation of the
tube plate 30 when theheader box 20 is under compressive load. This reduced deformation of thetube plate 30 involves a reduction in the mechanical load on the tube or on the tube-plate join. In particular, the end sides of the flat tube, which in mechanical terms are under the highest loads in the event of such pressure-induced deformations, are relieved of load as a result. - As can be seen in the side view of the
heat exchanger 110 inFIG. 2 , thetube 120 is fitted into thetube opening 160 sufficiently far for anupper edge region 121 of thetube 120 to project beyond thetube plate 130. This ensures good utilization of an inner surface (not visible), which faces thetube 120, of therim 170 as a bearing surface for a tube-plate join. This serves, for example, to ensure sealed soldering. To avoid an unnecessarily high pressure drop of the first medium across the heat exchanger, the extent to which thetube 120 projects above thetube plate 130 is to be minimized. For this reason, thetube opening 160 is situated in an essentially planar central region 131 of thetube plate 130. Therim 170 is enclosed by aflank 190, the end sides 191, 192 of which, firstly, merge into therim 170 at an obtuse angle and, secondly, likewise at an obtuse angle, merge into a raisededge region 132 of thetube plate 130. An additional reduction in load on thetube 120 and/or the tube-plate join is brought about on account of the associated S-shaped cross section of thetube plate 130 in the region of thecover connection surface 150—edge region 132—flank region 191/192—rim 170. -
FIG. 3 shows a further exemplary embodiment of part of aheat exchanger 210 in a longitudinal section.Tubes rims heat exchanger 210 of a medium flowing through theheat exchanger 210 and, inter alia, through thetubes rims tubes rims - The
rims flanks 290 which each have aplanar subregion 295. Theplanar subregion 295 encloses an obtuse angle with therim 270, as a result of which the reinforcing effect of the depression, which is formed by theflank 290, in the tube plate 230 is additionally increased. Theflanks 290 are directly adjacent to one another here, so thatbeads 299 are formed, which can be seen in cross section inFIG. 3 . As is clearly shown in this cross section, thebeads 299 do not have any horizontal regions situated between theflanks 290. - The width b is advantageously similar to the height h of the
flanks 290, particularly preferably is approximately the same. For this reason, the angle between theplanar subregion 295 of theflank 290 and therim 270 is approximately 45°. For thebeads 299, this results in a bead angle α of approximately 90°, which is associated with a particularly high stiffening effect of thebeads 299. -
FIG. 4 shows the excerpt of a modified configuration of the heat exchanger fromFIG. 3 . Thetube 320 protrudes here over the rim 370, but ends below asurface 335 of thetube plate 330. This results in increased manufacturing reliability with regard to a fluid-tight connection between thetube plate 330 and thetube 320. For example, a soldered join is improved by asoldering gap 376 to be additionally added to thesoldering gap 375. The soldering gap serves here at the same time as an introductory slope for facilitating the fitting of thetube 320 into thetube plate 330. - In contrast thereto, in the exemplary embodiment illustrated in
FIG. 5 , thetube 420 protrudes beyond therim 470 and beyond asurface 435 of the tube plate 430. Owing to the associated, relatively large tolerances with respect to the length of thetube 420, a further increase in the manufacturing reliability results.
Claims (10)
1. A heat exchanger having tubes and at least one header box, the header box comprising at least one tube plate, the tube plate having rims into which the tubes can be fitted, wherein the rims are enclosed by a respective peripheral flank, the flanks of two adjacent rims bordering each other with a bead being formed.
2. The heat exchanger as claimed in claim 1 , wherein the flanks each have an essentially constant width over the circumference of a rim.
3. The heat exchanger as claimed in claim 1 , wherein the tubes are flat tubes arranged in at least one row, in that the rims are of elongate design corresponding to the tube cross sections, and in that the flanks of the rims border one another with elongate beads being formed.
4. The heat exchanger as claimed in claim 1 , wherein the flanks each have a rounded portion with an approximately constant radius of curvature.
5. The heat exchanger as claimed in claim 4 , wherein the flanks each have a plurality of rounded portions with different radii of curvature.
6. The heat exchanger as claimed in claim 1 , wherein the flanks each have at least one planar region.
7. The heat exchanger as claimed in claim 6 , the at least one planar region forms an obtuse angle, in particular an angle of between 30° and 60°, with the respective rim.
8. The heat exchanger as claimed in claim 1 , wherein the rims face out of the at least one header box.
9. A charge-air cooler, in particular for a motor vehicle, characterized by the features of claim 1 .
10. A method for producing a tube plate, comprising:
a) providing a planar metal sheet,
b) raising one or more edge regions of the planar metal sheet by means of a forming process,
c) placing depressions, which border one another, into the metal sheet by means of a forming process, the depressions each having an essentially planar base surface and a flank enclosing and encircling the base surface,
d) piercing the base surfaces by means of a draw-through process and, in particular, and
e) impressing introductory slopes therein in order to facilitate an introduction of tubes into the rims produced in step d).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10343239.6A DE10343239B4 (en) | 2003-09-17 | 2003-09-17 | Heat exchanger |
DE10343239.6 | 2003-09-17 | ||
PCT/EP2004/010069 WO2005028990A1 (en) | 2003-09-17 | 2004-09-09 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
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US20070000657A1 true US20070000657A1 (en) | 2007-01-04 |
Family
ID=34305890
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/572,482 Abandoned US20070000657A1 (en) | 2003-09-17 | 2004-09-09 | Heat exchanger |
Country Status (9)
Country | Link |
---|---|
US (1) | US20070000657A1 (en) |
EP (1) | EP1664658A1 (en) |
JP (1) | JP2007506061A (en) |
CN (1) | CN100472169C (en) |
BR (1) | BRPI0414439B1 (en) |
DE (1) | DE10343239B4 (en) |
RU (1) | RU2380642C2 (en) |
WO (1) | WO2005028990A1 (en) |
ZA (1) | ZA200602221B (en) |
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US20070235175A1 (en) * | 2006-04-06 | 2007-10-11 | Degroot Robert J | Header plate for use in a heat exchanger |
US20080135220A1 (en) * | 2005-02-03 | 2008-06-12 | Behr Gmbh & Co., Kg | Heat Exchanger |
EP1967809A1 (en) * | 2007-03-07 | 2008-09-10 | Behr America, Inc | Weld bead reinforcement of charge air cooler headers and method of making same |
US20090145590A1 (en) * | 2005-11-02 | 2009-06-11 | Christian Riondet | Reinforced Collector For The Collecting Box Of A Heat Exchanger and Collecting Box Comprising One Such Collector |
US20100038063A1 (en) * | 2008-08-08 | 2010-02-18 | Christian Saumweber | Heat exchanger, use, and manufacturing process for a heat exchanger |
US20100199955A1 (en) * | 2009-02-06 | 2010-08-12 | Paccar Inc | Charge air cooler |
US20110139424A1 (en) * | 2008-06-10 | 2011-06-16 | Thomas Bensel | Heat exchanger |
US20110139418A1 (en) * | 2008-06-03 | 2011-06-16 | Philipp Pustelnik | Plate Cooler for Fluids |
US20120018135A1 (en) * | 2010-07-20 | 2012-01-26 | Denso Marston Ltd. | Header plate, a heat exchanger, a method of making a header plate and a method of making a heat exchanger |
US20120199332A1 (en) * | 2011-02-04 | 2012-08-09 | Ken Cornell | Heat exchanger header plate |
US8322407B2 (en) | 2008-04-29 | 2012-12-04 | Honda Motor Co., Ltd. | Heat exchanger with pressure reduction |
US8851157B2 (en) | 2010-05-13 | 2014-10-07 | Adams Thermal Systems, Inc. | Partial reverse ferrule header for a heat exchanger |
US20160003548A1 (en) * | 2014-07-07 | 2016-01-07 | Keihin Thermal Technology Corporation | Heat exchanger and method of manufacturing the same |
US9599413B2 (en) | 2011-05-02 | 2017-03-21 | Mahle International Gmbh | Heat exchanger, in particular intercooler |
US20180135921A1 (en) * | 2015-06-12 | 2018-05-17 | Valeo Systemes Thermiques | Fin of a heat exchanger, notably for a motor vehicle, and corresponding heat exchanger |
US20190186431A1 (en) * | 2017-12-14 | 2019-06-20 | Hanon Systems | Tube, in particular a flat tube for an exhaust gas cooler and exhaust gas cooler |
US10371464B2 (en) | 2015-07-07 | 2019-08-06 | Mahle International Gmbh | Tube header for heat exchanger |
US11029101B2 (en) * | 2019-02-11 | 2021-06-08 | Hanon Systems | Reverse header design for thermal cycle |
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DE102006048484A1 (en) * | 2006-10-11 | 2008-04-17 | Behr Gmbh & Co. Kg | Heat exchanger with flat tubes and method for producing such a heat exchanger |
DE102007005392A1 (en) | 2007-02-03 | 2008-08-07 | Behr Gmbh & Co. Kg | Collection box and heat exchanger with such a collection box |
DE102008011579A1 (en) | 2008-02-28 | 2009-09-03 | Behr Gmbh & Co. Kg | Base plate of a collecting tank for cooling water and heat exchanger for motor vehicles |
DE102014213758A1 (en) * | 2014-07-15 | 2016-01-21 | Mahle International Gmbh | Tube bottom and heat exchanger |
FR3036469B1 (en) * | 2015-05-22 | 2017-06-09 | Valeo Systemes Thermiques | COLLECTOR PLATE FOR HEAT EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE |
FR3060726B1 (en) * | 2016-12-19 | 2019-10-25 | Valeo Systemes Thermiques | HEAT EXCHANGER WITH REINFORCING PLATE. |
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- 2004-09-09 EP EP04786925A patent/EP1664658A1/en not_active Ceased
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- 2004-09-09 CN CNB2004800264288A patent/CN100472169C/en active Active
- 2004-09-09 RU RU2006112557/06A patent/RU2380642C2/en not_active IP Right Cessation
- 2004-09-09 WO PCT/EP2004/010069 patent/WO2005028990A1/en active Application Filing
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US4400965A (en) * | 1980-03-27 | 1983-08-30 | Modine Manufacturing Company | Forming integral flanges in a sheet apparatus therefore |
US4582127A (en) * | 1982-12-22 | 1986-04-15 | Societe Anonyme Des Usines Chausson | Tube end plate for heat exchanger with tubes and water boxes |
US5297624A (en) * | 1991-07-02 | 1994-03-29 | Thermal-Werke Warme-, Kalte-, Klimatechnik Gmbh | Header for a flat tube liquefier |
US5417277A (en) * | 1991-10-01 | 1995-05-23 | Valeo Thermique Moteur | Fluid manifold having a tubular wall, for a heat exchanger |
US5676200A (en) * | 1995-10-06 | 1997-10-14 | Valeo Thermique Moteur | Heat exchanger, in particular a booster air radiator for a motor vehicle |
US5816316A (en) * | 1996-02-20 | 1998-10-06 | Valeo Thermique Moteur | Heat exchanger with a brazed header, in particular for a motor vehicle |
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US6651333B2 (en) * | 1996-08-29 | 2003-11-25 | Valeo Thermique Moteur | Aluminum based collared header plate for a heat exchanger, especially for a motor vehicle |
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Cited By (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080135220A1 (en) * | 2005-02-03 | 2008-06-12 | Behr Gmbh & Co., Kg | Heat Exchanger |
US20090145590A1 (en) * | 2005-11-02 | 2009-06-11 | Christian Riondet | Reinforced Collector For The Collecting Box Of A Heat Exchanger and Collecting Box Comprising One Such Collector |
US8997844B2 (en) | 2005-11-02 | 2015-04-07 | Valeo Systemes Themiques | Reinforced collector for the collecting box of a heat exchanger and collecting box comprising one such collector |
US7413006B2 (en) * | 2006-04-06 | 2008-08-19 | Modine Manufacturing Company | Header plate for use in a heat exchanger |
US20070235175A1 (en) * | 2006-04-06 | 2007-10-11 | Degroot Robert J | Header plate for use in a heat exchanger |
EP1967809A1 (en) * | 2007-03-07 | 2008-09-10 | Behr America, Inc | Weld bead reinforcement of charge air cooler headers and method of making same |
US20080216989A1 (en) * | 2007-03-07 | 2008-09-11 | Behr America Inc. | Weld bead reinforcement of charge air cooler headers and method of making same |
US8322407B2 (en) | 2008-04-29 | 2012-12-04 | Honda Motor Co., Ltd. | Heat exchanger with pressure reduction |
US9587887B2 (en) * | 2008-06-03 | 2017-03-07 | Alpver Vermoegens—Und Liegenschaftsverwaltungs GmbH | Plate cooler for fluids |
US20110139418A1 (en) * | 2008-06-03 | 2011-06-16 | Philipp Pustelnik | Plate Cooler for Fluids |
US20110139424A1 (en) * | 2008-06-10 | 2011-06-16 | Thomas Bensel | Heat exchanger |
US8720535B2 (en) * | 2008-08-08 | 2014-05-13 | Behr Gmbh & Co. Kg | Heat exchanger, use, and manufacturing process for a heat exchanger |
US20100038063A1 (en) * | 2008-08-08 | 2010-02-18 | Christian Saumweber | Heat exchanger, use, and manufacturing process for a heat exchanger |
US20100199955A1 (en) * | 2009-02-06 | 2010-08-12 | Paccar Inc | Charge air cooler |
US8851157B2 (en) | 2010-05-13 | 2014-10-07 | Adams Thermal Systems, Inc. | Partial reverse ferrule header for a heat exchanger |
US20120018135A1 (en) * | 2010-07-20 | 2012-01-26 | Denso Marston Ltd. | Header plate, a heat exchanger, a method of making a header plate and a method of making a heat exchanger |
US20120199332A1 (en) * | 2011-02-04 | 2012-08-09 | Ken Cornell | Heat exchanger header plate |
US8978746B2 (en) * | 2011-02-04 | 2015-03-17 | Modine Manufacturing Company | Heat exchanger header plate |
US9599413B2 (en) | 2011-05-02 | 2017-03-21 | Mahle International Gmbh | Heat exchanger, in particular intercooler |
US20160003548A1 (en) * | 2014-07-07 | 2016-01-07 | Keihin Thermal Technology Corporation | Heat exchanger and method of manufacturing the same |
US9827638B2 (en) * | 2014-07-07 | 2017-11-28 | Keihin Thermal Technology Corporation | Heat exchanger and method of manufacturing the same |
US20180135921A1 (en) * | 2015-06-12 | 2018-05-17 | Valeo Systemes Thermiques | Fin of a heat exchanger, notably for a motor vehicle, and corresponding heat exchanger |
US10371464B2 (en) | 2015-07-07 | 2019-08-06 | Mahle International Gmbh | Tube header for heat exchanger |
US20190186431A1 (en) * | 2017-12-14 | 2019-06-20 | Hanon Systems | Tube, in particular a flat tube for an exhaust gas cooler and exhaust gas cooler |
US11029101B2 (en) * | 2019-02-11 | 2021-06-08 | Hanon Systems | Reverse header design for thermal cycle |
Also Published As
Publication number | Publication date |
---|---|
EP1664658A1 (en) | 2006-06-07 |
BRPI0414439A (en) | 2006-11-14 |
CN100472169C (en) | 2009-03-25 |
JP2007506061A (en) | 2007-03-15 |
RU2380642C2 (en) | 2010-01-27 |
RU2006112557A (en) | 2007-10-27 |
CN1853083A (en) | 2006-10-25 |
WO2005028990A1 (en) | 2005-03-31 |
BRPI0414439B1 (en) | 2018-05-29 |
ZA200602221B (en) | 2007-05-30 |
DE10343239B4 (en) | 2021-09-09 |
DE10343239A1 (en) | 2005-04-14 |
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Legal Events
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Owner name: BEHR GMBH & CO. KG, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:EMRICH, KARSTEN;HELMES, WERNER;RECK, MARKUS;AND OTHERS;REEL/FRAME:018134/0324;SIGNING DATES FROM 20060508 TO 20060719 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |