EP2122290A1 - Échangeur de chaleur pour l'échange de chaleur entre un premier fluide et un deuxième fluide - Google Patents

Échangeur de chaleur pour l'échange de chaleur entre un premier fluide et un deuxième fluide

Info

Publication number
EP2122290A1
EP2122290A1 EP07856501A EP07856501A EP2122290A1 EP 2122290 A1 EP2122290 A1 EP 2122290A1 EP 07856501 A EP07856501 A EP 07856501A EP 07856501 A EP07856501 A EP 07856501A EP 2122290 A1 EP2122290 A1 EP 2122290A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
pipe
exchanger according
region
distance value
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.)
Granted
Application number
EP07856501A
Other languages
German (de)
English (en)
Other versions
EP2122290B1 (fr
Inventor
Hermann Knaus
Christian Saumweber
Markus Reck
Claus Augenstein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2122290A1 publication Critical patent/EP2122290A1/fr
Application granted granted Critical
Publication of EP2122290B1 publication Critical patent/EP2122290B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • 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
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases

Definitions

  • Heat exchanger for heat exchange between a first fluid and a second fluid
  • the invention relates to a heat exchanger for heat exchange between a first fluid, in particular a charge air or an exhaust gas, and a second fluid, in particular a coolant, comprising: a block for separate and heat exchanging guidance of the first and second fluid, the one or more Having flowed through the first fluid flow channels; at least one box associated with the block, which is in fluid communication with the flow channels; and at least one bottom provided with one or more through holes for passage of the flow channels between the block and the box; wherein at least one flow channel in the form of a flat tube is formed with a narrow pipe side and a pipe broadside.
  • the invention further relates to the use of such a heat exchanger as a charge air cooler for the direct or indirect cooling of charge air in a charge air supply system for an internal combustion engine of a motor vehicle.
  • Heat exchangers are usually constructed, in particular in the case of the mobile application mentioned at the outset, as pipe-corrugated fin systems and, in particular, in the case mentioned of a particularly high stochastic pressure and pressure Exposed to thermal cycling.
  • the mentioned alternating stresses are decisive for the life of a heat exchanger.
  • the thermal cycling is in a heat exchanger of the type mentioned above due to the resulting in the region of the tube ends particularly high mechanical stress amplitudes dominating the load. It has been shown that within the block there is practically always an inhomogeneous temperature distribution with one of these directly associated inhomogeneous distribution of thermal expansions; the latter results in a tension of the BIOCK. In this case, thermal expansion differences within the block can not only occur in a tube longitudinal direction, but generally also exist transversely thereto.
  • GB 169,855 discloses a passage with a collar, which has a tooth-shaped contour formed by tongues at its end facing away from a bottom plate, in which a pipe end is held flexible and resilient.
  • the tongues mentioned serve a local extension of the passage in order to take into account any sudden change in cross section of a pipe.
  • the invention begins, whose object is to provide a heat exchanger in which the durability is improved.
  • a distance value at least at a transition between the tube narrow side and the tube broad side is so smaller than a distance value at the tube broad side, that stresses in the region of the transition are reduced.
  • a change in the distance value is continuous.
  • the stresses in the region of the transition can be reduced in particular by the fact that the distance value in the entire transition region between the pipe narrow side and the pipe broadside is minimal.
  • the distance value is at most minimal in partial regions of the transition between the smallest and largest diameter of the oval passage opening.
  • the distance value increases, so that the passages there have higher stiffnesses and accordingly induce stresses in the oval tubes, which impair their durability.
  • the invention is based on the consideration that the bending deformations caused by expansion differences in the block are particularly strong in the area of a pipe-to-floor connection or a pipe-box connection and correspondingly lead to high mechanical stresses there.
  • the invention has recognized that it is possible to determine the highest stresses along the pipe circumference, specifically in the region of the transition between the pipe narrow side and the pipe broad side.
  • the invention is based on the recognition that a reduction, in particular minimization, of the stresses, especially in the region of the transition, leads to an increase in the service life of the heat exchanger.
  • the concept of the invention provides that a distance value at least at a transition between the tube narrow side and the tube broad side is so smaller than a distance value at the tube broad side, that stresses in the region of the transition are reduced.
  • a change in the distance value is continuous, so that stress concentrations are reduced or avoided by notch effects.
  • One according to the knowledge of the invention especially In the transition region occurring stress is taken into account by the targeted reduction of the distance value at the transition according to the concept of the invention.
  • the concept of the invention rather provides, in a controlled manner, for reducing the load on the transition as a region of particularly high tension. Above all, it is achieved by the concept of the invention that said high voltage is displaced into a region of low stress, for example in the side region of a pipe.
  • a floor or a box according to the concept of the invention can also be produced at a much reduced cost in comparison with the prior art and substantially improve the process reliability when collecting radiator networks.
  • the durability of a heat exchanger is improved according to the concept of the invention.
  • the advantages mentioned have resulted in particular in brazed heat exchangers. Nevertheless, the concept of the invention has proven to be effective also in welded, glued or advantageously joined heat exchangers.
  • the concept has proven particularly advantageous in the case of a block in which the flow channels are accommodated by a chamber through which the second fluid can flow.
  • the concept according to the invention can be applied with regard to a box having a lid, the lid being fixed to the floor.
  • the Concept of the invention is also advantageous with respect to a floor integrally formed with the box. In such an integral, in particular one-piece construction of floor and box, shaping of the unit in the course of production can be carried out particularly advantageously by means of a hydroforming process.
  • a passage opening is formed as a passage, in particular as a passage with a collar, preferably with a collar oriented towards the block.
  • This type of soil has proven to be particularly easy to produce.
  • the floor is substantially flat and / or said plane substantially indicates the floor level.
  • it has the passage opening at least one, from a to Rohrachchsraum substantially vertical ground plane arched away and at a distance from said bottom plane extending boundary contour.
  • the distance value can be represented as required with regard to the expected stresses in the region of the transition according to the concept of the invention.
  • the distance value is also lower in the region of the pipe narrow side, in particular constant, than in the region of the pipe broadside. This leads to a particularly effective displacement of the stresses occurring at the transition in the region of a pipe broadside.
  • a contour curve of the limiting contour is a function of a circumferential dimension of the passage opening.
  • a dimension of a passage opening in particular a length of a passage opening-corresponding to the pipe width side-and / or a width of a passage opening-corresponding to a pipe narrow side-can serve.
  • the concept of the invention provides that the polynomial function is formed in such a way that stresses in the region of the transition are reduced, preferably minimized. It has been found that a course curve in the form of a polar function of at least the second degree is advantageous. Thus, at the transition, a change in the distance value according to the concept of the invention may be continuous.
  • the degree of polynomial function is less than 5, that is, the polynomial function has no more than 4 extremes.
  • the distance value in the region of the pipe width side preferably exactly, assumes a maximum value, preferably in the middle of the pipe broadside. This results in a particularly large voltage displacement moment.
  • exactly one minimum value can be assumed by a distance value in the region of a pipe width side, in particular in the middle of the pipe broadside.
  • the distance value in this case has exactly two maxima on one side, in particular between the middle of the page and the transition to the pipe narrow side.
  • the maximum value of the distance value can be determined depending on the expected voltage load.
  • Maximum values in the range of 0.5 to 1, 0 times the clear width are particularly advantageous here.
  • different variants of limiting contours can be combined in a through opening.
  • a first variant of a boundary contour can have exactly one maximum value of a distance value
  • a second variant of a boundary contour has exactly one minimum value of a distance value or a constant value of a distance value.
  • a first variant of a limiting contour can have exactly one minimum value of a distance value
  • the second variant of a limiting contour can have a constant value of a distance value
  • the concept of the invention is particularly effective for corner tubes and / or for tubes arranged in an edge area of a block.
  • a flow channel preferably has a heat-conducting element in the form of an inner rib mounted on a channel inside, in particular a soldered one, and / or a heat-conducting element in the form of an outer rib attached to a channel outside, in particular a soldered outer rib.
  • the ribs are also called corrugated ribs.
  • the block may further comprise a flow guide, in particular a turbulence device.
  • the invention leads in a particularly preferred manner to a heat exchanger in the form of a direct or indirect charge air heat exchanger, in particular special cooler or in the form of an exhaust gas heat exchanger, in particular radiator.
  • the concept of the present invention can be used within the scope of the use of the heat exchanger of the type described above for an internal combustion engine of a motor vehicle, that is quite generally in the mobile sector.
  • An overall boundary contour of the passage opening or passage openings is preferably kink-free at least in the entire transitional area between a pipe narrow side and a pipe broadside. This avoids that stresses are increased by notch effects.
  • the overall boundary contour in the region of the tube broadside can be substantially trapezoidal.
  • Such passage openings are particularly easy to manufacture.
  • corresponding heat exchangers have a high durability and good Kassetier Kings.
  • Flanks with a pitch angle in the range of 5 ° to 75 °, in particular in the range of 10 ° to 60 ° and especially in the range of 15 ° to 45 °, have proved to be particularly favorable. They represent an optimal compromise between a sufficient support of the flow channels and a reduction of the induced voltages in these.
  • the distance value of the total boundary contour to a plane substantially perpendicular to the tube axis direction along the circumference of the passage opening generally represents a function y (x) of a coordinate x in the circumferential direction of the passage opening. Both for manufacturing and strength-theoretical reasons, it has proven to be particularly favorable if this function y (x) is defined in sections, wherein for each section k:
  • these orders may differ in the different sections. For example, straight or oblique sections that correspond to polynomials zero and first degree, respectively, can alternate with sections of higher degree. Conversely, it has proved to be favorable that the polynomials each have at most the fifth degree, since otherwise the boundary contour becomes wavy.
  • the functions defined in sections proceed continuously at the section boundaries, preferably one or more times continuously differentiable into one another, as is the case, for example, with cubic or B-splines.
  • x 'de notes in the usual way the ite power of x, Xo k the coordinate at the beginning of a section k and Xi k the coordinate at the end of the section k.
  • the coefficients a, k , b ik , c ⁇ j k , ⁇ ik are constant and predetermined for each section k.
  • some or all of the coefficients of the polynomial or Fourier component in one or more sections may be identically zero, that is to say in particular that the function may also be a pure polynomial function or pure Fourier series at least in sections.
  • Flat tubes of a heat exchanger may for example have a substantially rectangular or oval cross-section.
  • the narrow sides of the tube can be curved and the tube broad sides straight.
  • a corner or a corner radius where the narrow side of the tube and the broad side of the tube meet, is referred to as the transition region between the narrow side of the tube and the broad side of the tube.
  • the transition region may in particular denote the region in which the pipe narrow side and pipe wide side approach one another perpendicular to their respective extent direction.
  • essentially the area between the smallest and the largest diameter or, preferably, the area can be regarded as a transitional area in which the diameter is less than 80% of the largest and greater than 120% of the smallest diameter is.
  • an insertion bevel for simplified insertion of the flat tube is provided in the region of the boundary contour.
  • a contact surface for surface soldering to the flat tube is provided in the region of the boundary contour. This will be the Total soldering improved and significantly reduced by defective solder joints.
  • a draft having the boundary contour projects inwardly toward the box from the ground.
  • Such orientation of the passage is particularly well suited to be combined in the sense of a simple production with an integrated or one-piece design of floor and box.
  • Fig. 1 the example of a floor with a passage in a heat exchanger according to the prior art
  • Fig. 2 the example of a floor with a passage according to the concept of the invention in a particularly preferred embodiment of a heat exchanger
  • FIG. 3 is a perspective view of a box with bottom and inserted flat tubes in a heat exchanger according to the particularly preferred embodiment shown in Figure 2.
  • FIG. 4A shows the example of a comparison calculation of a stress distribution in a passage according to FIG. 1 (view A) in comparison with FIG. 2 (view B), wherein the passages are shown;
  • Fig. 4B the example of Fig. 4A without passages.
  • FIG. 5 shows another example of a floor with a modified embodiment of a pull-through according to a further preferred embodiment of a heat exchanger
  • FIG. 6 shows another example of a floor with a modified embodiment of a pull-through in a further preferred embodiment of a heat exchanger
  • Fig. 7 an example of a curved bottom in a heat exchanger according to an alternative preferred embodiment of the invention.
  • Fig. 8 is another example of a curved bottom which is presently integral with a box in an alternative preferred embodiment of a heat exchanger
  • FIG. 9 shows another example of a floor with a modified embodiment of a pull-through according to another preferred embodiment
  • FIG. 10 shows a further example of a floor according to a further embodiment of a heat exchanger according to the invention.
  • FIG. 11 shows a further example of a floor according to a further embodiment of a heat exchanger according to the invention.
  • a heat exchanger according to the concept of the invention is realized according to a preferred embodiment in the form of a charge air cooler for direct charge air cooling and serves for heat exchange between a charge air and a coolant, preferably air.
  • the heat exchanger comprises a block comprising a radiator network for the separate heat exchanging guidance of the charge air and the coolant.
  • the block has a number of flow channels through which charge air can flow, which additionally have a heat-conducting element in the form of an inner rib attached to a channel inside and a heat-conducting element in the form of an outer rib attached to a channel outside.
  • Such usually consisting of an alternating superposition of pipes and heat-transmitting corrugated fins arrangement is also referred to as a radiator network.
  • a box fluidly connected to the flow channels is associated with the block, and a bottom between the block and the box is provided with one or more through holes for passage of the flow channels between the block and the box.
  • a so-called passage with the cooler net oriented collar 17 '- as shown in Fig. 1 - can be used especially for mobile applications such as the discussed intercooler for commercial vehicles.
  • Bodenüberstandes - given as half the difference between tube depth t and depth T - are advantageously used to increase the internal pressure cycle resistance.
  • One possibility for reducing the stresses in the region of the transition 27 'from the narrow pipe side 13 to the pipe broadside 15 can be achieved according to the concept of the invention by exemplifying at the transition 27' - as illustrated by way of example in FIG FIG.
  • 4B demonstrates that, between the narrow side 13 of the pipe and the width of the pipe broadside 15, a distance value is selected that is less than a distance value 25 on the pipe broadside 15, that (4A, 4B, view A) in the region of the transition 27 ', 27 are reduced (see in comparison Fig. 4A, Fig. 4B, view B).
  • FIG. 3 shows the lid 5 of the box 3, wherein the lid 5 is fixed to the said bottom 1.
  • the bottom provides a plurality of through openings 7, which are designated in more detail in FIG. 2, and which are provided for the passage of the flow channels between the block 9 and the box 3 which are not illustrated.
  • flow channels in the form of flat tubes 11 are formed, wherein a flat tube 11 has a narrow side tube 13 and a pipe broad side 15.
  • a base 1 with a plurality of passage openings 7, each in the form of a passage for receiving a tube 11, which houses the block 9 with the collection boxes 3 arranged on both sides of the block 9 - of which only one is shown here - connect.
  • FIG. 7 An alternative embodiment of a tube sheet is shown in Fig. 7 and a box is shown in Fig. 8, which will be described below.
  • a flat tube 11 is formed as a rectangular tube.
  • the cross-section of a tube may be varied.
  • a cross section may be approximately rectangular, approximately oval or, for example, a rectangular cross section with a curved narrow side.
  • the tube bottom 1 shown again in FIG. 2 in view A in perspective and in view B as a section has the passage opening 7 in the form of a passage with a collar 17 oriented toward the block 9.
  • the collar 17 of the passage opening 7 is toward the block 9 through a limiting contour 19 is limited, wherein the limiting contour 19 is curved away from a direction substantially perpendicular to the Rohrachscardi 21 level 23 and extends at a distance 25 to said plane 23.
  • the distance 25 is the maximum distance formed corresponding to the passage opening length t in the middle of the pipe broad side 15. In the embodiment shown in FIG. 2, the distance 25 thus assumes exactly one maximum value as the maximum distance 25 in the area of the pipe broadside 15.
  • the distance value at the transition 27 between the narrow side 13 of the pipe and the broad side 15 of the pipe is so smaller than a distance value 25 on the pipe broad side 15 that stresses in the region of the transition 27 are reduced.
  • a change in the distance value 25 runs continuously on the tube broad side 15 and in the transition 27.
  • the pipe run in the form of the collar present locally, starting from the transition 27, is continuously increased in such a way that the maximum stress at the transition 27 is minimized.
  • FIG. 2 results in the stress distribution shown in view B of FIGS. 4A, 4B graphically as a result of a finite element calculation for the lower tube section.
  • Fig. 4A shows the result with bottom 1, 1 ', Fig. 4B without.
  • the stress distribution in view B is the result of the contour curve of the limiting contour 19 designed for minimizing the stress distribution, specifically the minimization of the stress in the region of the transition 27.
  • FIGS. 4A, 4B clearly show that the stresses in FIG Area of the transition 27 - there around the trajectory of the boundary contour 19 around - prevail, while they are comparatively small in the range of the maximum distance 25. Above all, FIGS.
  • FIG. 4A, 4B show in view B that, by a design of the contour curve of the limiting contour 19, the stress distribution in comparison to a prior art embodiment in view A, as shown in FIG. 1, minimize.
  • this is achieved by a circular arc-like boundary contour 19, the - or the distance values - at the transition 27 continuously decreasing in the peripheral region along the narrow pipe side 13 - ie the region of the width of the through hole 7 - enters.
  • a contour progression adapted to the specific stress distribution can be achieved by an overall circumferential change of the distance values, thereby minimizing the stress.
  • FIG. 2 view A, that a distance value along the width of the passage opening 7 is likewise smaller than a distance value 25 on the tube broad side 15. This circumstance was included in the calculations as shown in Figs. 4A, 4B, View B.
  • y a nk . X 01 Va n R -1 . x ⁇ k "1 ... + ai. x + b.
  • the mentioned parameters are adapted such that the maximum distance 25 between the course of the distance contour 19 and the ground plane 23 is in the range between 0.2 times to 1.5 times the clear width of the passage opening 7 ,
  • the width h is shown by way of example in FIG. 1, view A.
  • Fig. 5 shows a varied embodiment according to the concept of the present invention.
  • a through opening 7 on opposite sides 31, 33 has different variants of limiting contours 19A, 19B.
  • a first variant of a limiting contour 19A corresponds to that discussed in FIG. 2, which has exactly one maximum value of a distance value 25.
  • a second variant of a limiting contour 19B has a constant value of a deviation. current value, which is below that of the distance value 25 and substantially corresponds to that of the pipe narrow side 13.
  • At the transition 27 between the narrow pipe side 13 and the pipe broad side 15 of the distance value 25 is again such a smaller than a distance value on the pipe broadside 15 that stresses in the region of the transition 27 are reduced.
  • a change in the distance value 25 on the tube broad side 15 and at the transition 27 is continuous.
  • FIG. 6 shows yet another variant embodiment of a base 1 with a passage opening 7, in which different variants of limiting contours 19C, 19D are provided on opposite sides 31, 33.
  • the first variant 19C is similar to that described in FIG. 2, but has no continuous change of the distance value 25 at the junction 27.
  • the second variant of the limiting contour 19D has exactly one minimum value of a distance value, namely in the center 35 of the tube broadside 15.
  • the second variant of the limiting contour 19D has exactly two maxima 37A, 37B on one side 33, namely between the center of the page 35 and the transition 27. This also allows a significant reduction in the distribution of stress can be achieved.
  • a limiting contour 19A, 19D thus has a one-sided design of a limiting contour 19A, 19D according to the concept of the invention.
  • the limiting contour 19B shown in Fig. 5 could also be replaced by a limiting contour 19D in another embodiment.
  • the limiting contour 19C shown in Fig. 6 could also be replaced by a limiting contour 19a.
  • FIGS. 1, 2, 3, 5 and 6 have a passage with collar 17 oriented toward the block 9.
  • the draft is also referred to as an "inverted draft".
  • Characteristic of the geometry of the passage is that a collar 17 "outwards", that is oriented towards the block 9 out.
  • an arched boundary contour 19, 19A, 19B, 19C, 19D is provided here, ie a boundary contour which does not run parallel to the ground plane 23. Rather, a distance value 25 of the boundary contour 19 of the respective passage 17 from the floor plane of the floor 1 is a function of a circumferential coordinate X, in the present case the longitudinal coordinate of the tube broadside 15.
  • the curve of the limiting contour 19 is in turn a function of the longitudinal coordinate X (FIG ). Characteristic of the passage 17 is further that the distance 25 of the collar 17 from the ground plane 23 between the passages in the region of the transition 27 between the narrow pipe side 13 and pipe broadside 15, ie continuously decreasing in the region of the "corner radii" of the passages is and the maximum distance 25 along the broad side 15, in the present case in the middle of the same, but generally anywhere along the broad side 15 - depending on the voltage field to be reduced - comes to rest. The middle of the broad side 15 is generally advantageous.
  • the curve shape of the limiting contour 19 shown in the exemplary embodiment of FIG. 2 is characterized by a local maximum of the distance 25 from the ground plane 23 between the passages.
  • FIG. 7 shows an alternative realization of the concept of the invention in the context of an embodiment which provides a curved bottom 41 for a flat tube 11.
  • the through-opening 7 has a limiting contour 19E, 19F curved away from a plane 23 substantially perpendicular to the tube axis direction 21 and extending at a distance from said plane 23, which faces on opposite sides 31, 33 a tube longitudinal side 15 is identical as a contour of the total circularly formed tube sheet.
  • FIG. 8 shows a further embodiment of a base 51 which is particularly easy to produce and which is presently formed integrally with an air box 53 for a flat tube 11.
  • Varying embodiments as in FIG. 5 or FIG. 6, can therefore also be provided only along a single tube broad side 15 with a passage in the form of a collar according to the concept of the invention.
  • a passage can be seen in FIG. 6, in which the contour curve characterizing the boundary contour has more than one local maximum.
  • Fig. 7 shows a, as explained, curved bottom 1, in which the previously described with respect to bending load advantageous curve in the ground itself is realized.
  • the embodiment shown in FIG. 8, in which a box 53 and a bottom 51 form an integral component also acts.
  • FIG. 9 shows, in a corresponding manner, another variant of a bottom 1 with through-opening 7, which is shown in FIG Design corresponding features are designated by the same reference numerals, so that will be discussed below only on the differences from this embodiment.
  • FIG. 9 has an overall boundary contour 19, which, as clearly visible in view B of FIG. 9, is essentially trapezoidal in the region of the tube broad side 15.
  • the contour 19 runs essentially parallel to the plane 23 perpendicular to the pipe axis direction 21, so that a distance y (x) between the contour 19 and the boundary line in this section is represented by a zero-degree polynomial Coordinate x is described in the circumferential direction.
  • the contour 19 in each case continuously differentiable merges into a sinusoidal course and runs out of this again continuously differentiable into a likewise substantially parallel to the plane 23 section extending over a part of a pipe broadside, the whole adjoining pipe narrow side and a part of the opposite other pipe broad side, so that the distance value y (x) in this entire section and so that it is minimal, especially in the entire transitional area between the pipe narrow side and the pipe wide side.
  • a continuously differentiable transition is understood to mean a transition between functions with the same pitch angle.
  • the flanks 100 of the essentially trapezoidal boundary contour 19 formed by the sinusoidal sections have, on average, a lead angle ⁇ of approximately 20 °.
  • the distance 101 between the Transition region 27 and the maximum value of the distance value 25 corresponds in the embodiment of the clear height h of the passage.
  • Fig. 10 shows another embodiment which is a modification of the embodiment of Fig. 9.
  • the boundary contour 19 is not visible, but shown as a dashed line.
  • the bordering in the lateral plan view of the passage and the boundary contour 19 slightly projecting edge 102 is not a limiting contour in the context of the invention, but an outer edge of an insertion bevel 103, which is provided for better replaceability of the exchanger tubes in the course of production of the heat exchanger.
  • the insertion bevel 103 has the boundary contour 19 as the lower boundary in the direction of insertion of the tubes and forms a surface or phase inclined outwardly away from the tube, the outer boundary of which is the edge 102.
  • Such an insertion bevel 103 may be conveniently provided in any of the above and below described embodiments of the invention in the form shown or similar.
  • the contact line of the passage is to be understood, with which the passage abuts against the pipe wall and is soldered.
  • this boundary contour 19 which touches the exchanger tube, the introduction of force from the exchanger tube into the ground, for example due to thermal expansion, is thus decisively influenced.
  • a contact surface 104 of the limiting contour 19 as it is generally known from the design of conventional passages for heat exchangers.
  • Such a contact surface 104 may be provided as required in each of the embodiments described above and below.
  • a width of the contact surface 104 may be expedient over the course of the limiting contour 19 vary, depending on which local forces are to be expected in the soldered state during operation at the respective position.
  • the width of the contact surface can be designed differently depending on the position, in order to ensure a reliable distribution of the solder during the soldering process, even at critical points.
  • the reference plane 23 oriented perpendicular to the tube axis is positioned at the level of the end of the exchanger tube 15 inserted into the passage.
  • the geometric shape of the limiting contour 19 of the embodiment of FIG. 10 corresponds to that of the embodiment of FIG. 9 described above.
  • Fig. 11 shows a further embodiment of the invention, in which a bottom 1 has a passage 105 projecting inwardly away from the block.
  • the passage initially has an insertion bevel 103, which is particularly wide in order to simplify the introduction of the exchanger tubes, in particular in the regions of the short sides.
  • the end of the insertion bevel 103 is formed by a delimiting contour 19, which contacts the tube wall of an inserted exchanger tube in a contacting manner.
  • the boundary contour has an area 27 in the vicinity of the Ü Transition from the long sides of the passage to the short sides, in which a distance value from a reference plane (not shown) is steadily monotonically smaller.
  • the reference plane is perpendicular to the tube axis through the end of the tube inserted into the passage.
  • the boundary contour 19 is adjoined by a contact surface 104, which extends from the limiting contour 19 in the direction of the tube end and enables improved surface soldering of the passage to the tube.
  • the floor shown in Fig. 11 may be a section of an integrated, in particular one-piece design of floor and box.
  • the integrated unit can be made of box and floor by means of a hydroforming process.
  • a blank in a first step, a blank can be processed by means of hydroforming, after which the passages 105 are injected from the outside in a second step.
  • the passages project inwardly.
  • FIG. 12 shows a modification of the embodiment from FIG. 11, in which there is likewise an inwardly directed passage 105 with an insertion bevel 103, a boundary contour 19 formed according to the invention and a contact surface 104 adjoining the boundary contour 19.
  • the passage is not arranged in a flat region of the base 1, but extends through two bends 107.
  • the bends 107 of the base cover the inclined regions 27 of the limiting contour 19 and also correspond in their direction Angle these areas.27.
  • the bends 107 support the rigidity and compressive strength of the soil.
  • the bottom of the example of Fig. 12 is particularly suitable for being formed as an integral one-piece unit with a box and can be made in the same manner as described above.
  • a heat exchanger for heat exchange between a first fluid, in particular a charge air or an exhaust gas, and a second fluid, in particular a coolant, specified, comprising: a block 9 for the separate and heat exchanging leadership of the first and second fluid, which block 9 has a number of flow channels through which the first fluid can flow; at least one box 3 associated with the block 9, which is fluidly connected to the flow channels; and at least one floor 1 provided with one or more through holes 7 for passage of the flow channels between the block 9 and the box 3; wherein a flow channel in the form of a flat tube 11 is formed with a pipe narrow side 13 and a pipe broadside 15, and wherein the through hole 7 at least one, of a pipe axis 21 substantially perpendicular to the plane 23 curved away and at a distance 25 to said plane extending boundary contour 19th having.
  • the invention provides a distance value at least at a transition 27 between the pipe narrow side 13 and the pipe broadside 15 is such that a distance at the pipe broadside 15 is such that stresses in the region of the transition 27 are reduced, at least at the pipe broad side 15) and at the transition 27 a change of the distance value is continuous.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur pour l'échange de chaleur entre un premier fluide, en particulier l'air de suralimentation ou les gaz d'échappement, et un deuxième fluide, en particulier un fluide de refroidissement. Ledit échangeur de chaleur présente un bloc (9) qui amène le premier et le deuxième fluide séparément l'un de l'autre à l'échange de chaleur, lequel bloc (9) présente plusieurs canaux d'écoulement qui peuvent être traversés par le premier fluide, au moins un caisson (3) associé au bloc (9) et relié à écoulement aux canaux d'écoulement, et au moins un fond (1) doté d'une ou de plusieurs ouvertures de passage (7) qui prolongent les canaux d'écoulement entre le bloc (9) et le caisson (3). Un canal d'écoulement qui présente la forme d'un tube plat (11) doté d'un côté étroit (13) et d'un côté large (15) est formé et l'ouverture de passage (7) présente au moins un contour frontière (19) bombé de manière à s'éloigner de l'axe du tube dans un plan (23) essentiellement perpendiculaire à la direction (21) de l'axe du tube et qui s'étend à une distance (25) dudit plan. Pour minimiser les contraintes dans la zone de la transition entre le côté étroit (17) du tube et le côté large (15) du tube, l'invention propose qu'au moins à la transition (27) entre le côté étroit (13) du tube et le côté large (15) du tube, une valeur de la distance soit inférieure à la valeur de la distance sur le côté large (15) du tube de manière à diminuer les contraintes dans la zone de la transition (27). La variation de la valeur de la distance est continue au moins sur le côté large (15) du tube et dans la transition (27).
EP07856501.7A 2006-12-13 2007-12-10 Échangeur de chaleur pour l'échange de chaleur entre un premier fluide et un deuxième fluide Active EP2122290B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102006059288 2006-12-13
DE102007014437 2007-03-22
DE102007035441 2007-07-26
PCT/EP2007/010725 WO2008071362A1 (fr) 2006-12-13 2007-12-10 Échangeur de chaleur pour l'échange de chaleur entre un premier fluide et un deuxième fluide

Publications (2)

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EP2122290A1 true EP2122290A1 (fr) 2009-11-25
EP2122290B1 EP2122290B1 (fr) 2017-07-19

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EP07856501.7A Active EP2122290B1 (fr) 2006-12-13 2007-12-10 Échangeur de chaleur pour l'échange de chaleur entre un premier fluide et un deuxième fluide

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Country Link
EP (1) EP2122290B1 (fr)
DE (1) DE102007059673A1 (fr)
WO (1) WO2008071362A1 (fr)

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EP2151655B1 (fr) 2008-08-08 2017-11-01 MAHLE Behr GmbH & Co. KG Echangeur thermique, utilisation et procédé de fabrication d'un échangeur thermique
DE102008059737A1 (de) * 2008-12-01 2010-06-02 Behr Gmbh & Co. Kg Kreuzstrom-Wärmetauscher
FR2951259B1 (fr) * 2009-10-08 2014-02-28 Valeo Systemes Thermiques Plaque collectrice pour un echangeur de chaleur et echangeur de chaleur correspondant
DE102009057175A1 (de) * 2009-12-05 2011-06-09 Volkswagen Ag Wärmetauscher
DE102011075071A1 (de) 2011-05-02 2012-11-08 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Ladeluftkühler
DE102011076225A1 (de) * 2011-05-20 2012-11-22 Behr Gmbh & Co. Kg Wärmetauscher
DE102012219268A1 (de) * 2012-10-22 2014-04-24 Mahle International Gmbh Wärmetauscher
DE102013208424A1 (de) * 2013-05-07 2014-11-13 Behr Gmbh & Co. Kg Boden für einen Wärmetauscher, insbesondere für ein Kraftfahrzeug und Verfahren zur Herstellung des Bodens
DE102014213758A1 (de) * 2014-07-15 2016-01-21 Mahle International Gmbh Rohrboden und Wärmeübertrager
DE102015209130A1 (de) 2015-05-19 2016-11-24 Mahle International Gmbh Wärmeübertrager
US10371464B2 (en) 2015-07-07 2019-08-06 Mahle International Gmbh Tube header for heat exchanger
DE202017103235U1 (de) * 2017-05-30 2018-08-31 Autokühler GmbH & Co KG Wärmeaustauscher
FR3089609A1 (fr) * 2018-12-10 2020-06-12 Valeo Systemes Thermiques Boîte collectrice pour echangeur de chaleur et echangeur de chaleur comprenant une telle boîte collectrice
US20220333873A1 (en) * 2019-09-20 2022-10-20 T.Rad Co., Ltd. Brazing structure for flat tube and header plate of heat exchanger
JP7552026B2 (ja) 2020-02-14 2024-09-18 株式会社デンソー 熱交換器

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AU650221B2 (en) * 1989-08-25 1994-06-09 Showa Denko Kabushiki Kaisha A method of making a brazeable metal pipe having tube-insertion apertures formed with guide lugs
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Also Published As

Publication number Publication date
WO2008071362A9 (fr) 2009-08-27
DE102007059673A1 (de) 2008-08-07
WO2008071362A1 (fr) 2008-06-19
EP2122290B1 (fr) 2017-07-19

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