EP3087337B1 - Échangeur de chaleur à joint périphérique - Google Patents

Échangeur de chaleur à joint périphérique Download PDF

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Publication number
EP3087337B1
EP3087337B1 EP14812156.9A EP14812156A EP3087337B1 EP 3087337 B1 EP3087337 B1 EP 3087337B1 EP 14812156 A EP14812156 A EP 14812156A EP 3087337 B1 EP3087337 B1 EP 3087337B1
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EP
European Patent Office
Prior art keywords
seal
heat exchanger
groove
passages
receiving groove
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.)
Active
Application number
EP14812156.9A
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German (de)
English (en)
Other versions
EP3087337A1 (fr
Inventor
Harald Bronner
Markus Gutjahr
Markus Hübsch
Claus Augenstein
Reinhard Kull
Stefan Weise
Jens Ruckwied
Jochen HÄUSSERMANN
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
Mahle Behr GmbH and Co KG
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Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP3087337A1 publication Critical patent/EP3087337A1/fr
Application granted granted Critical
Publication of EP3087337B1 publication Critical patent/EP3087337B1/fr
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Anticipated expiration legal-status Critical

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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
    • F28F9/0219—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
    • F28F9/0226—Header boxes formed by sealing end plates into covers with resilient gaskets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2230/00—Sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements

Definitions

  • the present invention relates to a heat exchanger having a base, a seal and a cover according to the preamble of claim 1.
  • connection of a cover to a base (tube sheet) of a heat exchanger requires a reliable seal between the two elements mentioned in order to reliably prevent the leakage of coolant and thus a possible failure of the heat exchanger or an assembly to be cooled by it.
  • a base of such a heat exchanger is often provided as a tube sheet with corresponding passages through which, for example, flat tubes are drawn.
  • Said cover can be designed, for example, as a coolant box and thus contain coolant.
  • a reliable seal between the cover and the base is usually achieved by means of a seal which is inserted into a corresponding receiving groove in the base.
  • the receiving groove actually consists of two parallel receiving grooves, which are arranged orthogonally to the passages in the base at the edge of the base and are also produced when the base is punched or reshaped.
  • the seal runs between the two receiving grooves orthogonally to the same, usually also at the edge of the base in a specially designed groove.
  • the present invention is concerned with the problem of addressing an alternative embodiment for a heat exchanger of the generic type, which in particular enables simplified manufacture.
  • the present invention is based on the general idea of creating a heat exchanger whose bottom (tube bottom) is to be manufactured by the meter and can therefore be used in a comparatively flexible manner for heat exchangers of different sizes.
  • the heat exchanger according to the invention comprises a base, a seal and a cover, the base, usually also called tube base, having two parallel spaced apart grooves extending in the longitudinal direction of the base, which are located on two opposite sides of the Arranged at the bottom and designed to receive side projections of the cover. Each of these grooves also has a groove base.
  • the base has at least three passages, ie openings for flat tubes, which are arranged parallel to one another and spaced apart from the receiving grooves in a plane and extend perpendicular to and between the receiving grooves.
  • An intermediate region is formed in one plane between two such passages, which is arranged at a height difference h parallel to the groove bases of the receiving grooves. Between each intermediate area and the groove bases, a ramp runs parallel to the longitudinal direction of the passages, the ramps being parallel to one another.
  • the seal itself is designed as a circumferential sealing cord.
  • the seal now runs in the receiving grooves and each with a sealing web over two ramps and an intermediate area in between, the ramps being inclined at an angle of 20 ° ⁇ ⁇ 65 ° with respect to the plane of the intermediate area, ie usually with respect to the horizontal, or have an S-shaped profile, a turning point W in the range of 10% to 80% of the height difference h being arranged starting from the groove bottom of the receiving groove.
  • the ramps are rounded at the transition to the receiving groove or at the transition to the intermediate area with a corresponding radius R1, R2, in particular to minimize tensile and compressive stress peaks on the seal caused by sharp kinks in this seal.
  • the ramp is rounded with a radius R1, whereas it is rounded at the transition to the intermediate area with a radius R2.
  • the seal is clamped in the assembled state without excessive surface pressure or deformation between the base and cover.
  • the heat exchanger according to the invention is thus on the one hand the use of a continuous sheet formed as a bottom possible, and on the other hand at the same time ensures an optimal sealing effect, since the surface pressure or the deformation of the built-in seal does not exceed or fall below critical limit values.
  • the angle ⁇ between 20 ° and 65 °, the sealing effect and the load on the seal can also be influenced.
  • an angle of ⁇ ⁇ 20 ° there would be disadvantages for the later forming process of the passage and disadvantages with regard to the lateral guidance of the seal along the receiving groove.
  • the contact pressure exerted by the cover on the seal may be too low, so that the sealing effect may not be guaranteed.
  • improved contact between the seal and the floor and thus an improved sealing function can be achieved.
  • radii R1 and R2 would result which would either have a disadvantageous effect on the subsequent forming process of the passage or unfavorably on the width of the floor and thus also on the required installation space.
  • the turning point W is in the range of ⁇ 10% of the height difference h
  • the result is an S-shaped ramp that either has a disadvantageous effect on the floor width and thus the installation space or has a disadvantageous effect on the seal with regard to the stress peaks.
  • the turning point W is in the range of> 80% of the height difference h, the result is an S-shaped ramp which has a disadvantageous effect on the subsequent forming process.
  • a ratio of the radius R1 or R2 to a radius R3 of the section of the sealing cord or seal in the receiving groove in the unpressed state is advantageously 0.3 ⁇ R1 / R3 ⁇ 3.0 or 0.3 ⁇ R2 / R3 ⁇ 3.0. Defining this range of the ratio between the radius of the curve of the ramp and the radius of the seal optimizes the sealing effect. Too low a ratio would in fact cause a leak due to insufficient surface pressure on the Cause the transition area between the receiving groove and the ramp, with too large a ratio causing too little contact pressure along the ramp and a disadvantage in terms of installation space due to a wider base.
  • a longitudinal end of a passage facing the receiving groove is expediently between 1 mm ⁇ a ⁇ 15 mm, in particular between 2 mm ⁇ a ⁇ 6 mm closer to the receiving groove than a transition from the ramp to the intermediate area.
  • At least one of the ramps is designed as a groove which extends parallel to the longitudinal direction of the passages and in which the seal runs in sections, the ratio of the degree of groove filling through the seal in the groove and the at least one ramp to the degree of groove filling through the seal in the receiving groove in the pressed state of the seal is between 1.0 and 1.4.
  • the degree of groove filling is defined as the ratio between the cross-section of the pressed seal and the free cross-sectional area.
  • the ratio specified above makes it possible to achieve that the seal can be optimally guided and fixed and, at the same time, a stronger compression can be achieved in the ramp area, which improves the sealing function.
  • the compression should be greater in the area of the ramp than along the receiving groove in order to be able to ensure an optimal sealing effect.
  • the ramps expediently have a width b1 and the intermediate regions a width b2, the ratio b1 to b2 being between 0.3 and 1.0.
  • the degree of groove filling should be between 70 and 100% at both points.
  • this can be done by varying the diameter of the seal along the ramp, in particular at the transition area, or by varying the free cross-sectional area along the ramp at the transition area.
  • the desired degree of slot filling can be achieved in a particularly simple constructive manner. It is particularly advantageous if the cross section of the seal is> 40%, in particular between 50% and 70% of the cross section of the unpressed seal along the receiving groove.
  • the seal has at least one prestressing web for reducing tensile stresses on the seal, the at least one prestressing web being arranged parallel to a sealing web.
  • the sealing web of the seal runs over two ramps as well as an intermediate region outside the prestressing web running parallel to it.
  • Prestressing webs can generally be components of the seal and ensure that it is under prestress along the receiving grooves, whereby tensile stress on the seal in the area of the transition between the passages can be reduced. This makes it possible to ensure the desired position of the seal both along the receiving groove and between the passages.
  • the cover is expediently designed as a box, which has longitudinal side projections on the outside of the box on two opposite sides, the side projections extending in the receiving grooves and having a protrusion protruding longitudinally beyond the seal.
  • the cover is advantageously designed as a box which has a box base, a projection for positioning the box on the floor being arranged on a longitudinal side on the outer area of the box base.
  • a projection for positioning the box on the floor can be arranged on the outer area of the side projection.
  • the side protrusion is, for example, the box foot. Due to the position of the seal between the passages in the area of a narrow side, it is advantageous for pressing the seal if the connection between the base and the cover or box extends along the receiving groove at least to the point where the seal is sufficient the receiving groove turns over the ramp into the intermediate area. It is particularly advantageous here if the side projection has a protrusion along the receiving groove, which results in an H-shaped design. The H-shape is brought about by the two protrusions of the side projection on both sides in combination with the web of the side projection between the passages. The overhangs of the side protrusion can either end flush with the receiving groove or protrude beyond it.
  • the heat exchanger has a side part that is inserted through a passage in the bottom, with a side part overhang s for closing the bottom with the cover, the averaged distance between the side part and an adjacent, outer flat tube having the value q and where the ratio s through q is between 0.3 and 0.7.
  • This ensures that an optimal sealing effect in the area of the sealing web, ie the intermediate area, can be ensured with minimal installation space.
  • the ratio s to q can also assume a value greater than 0.7, in particular if partial or complete blocking of the outer tube is desired in the case of heat exchangers subject to high thermal loads.
  • the cover geometry is to be designed in such a way that the outer wall of the cover completely prevents or at least reduces a flow through the outer tube or several of the outer tubes.
  • the cover geometry can also be selected in such a way that one or more guide elements restrict or completely prevent the flow against the outermost tube or tubes (flat tubes).
  • all passages have the same contour and the same area. This enables a simple production of the floor with an endless sheet.
  • At least the two outer passages arranged at the lateral ends of the base have a surface area that differs from the otherwise identical surface area of the other passages by a factor of 0.8 to 1.3. This means that side parts with different wall thicknesses can be used, which increases the strength of the component.
  • a heat exchanger 1 has a base 2, a seal 3 and a cover 4.
  • a heat exchanger 1 according to the prior art is shown
  • an inventive heat exchanger 1 is shown. If one now looks at the base 2, it can be seen that it has two parallel spaced apart grooves 5, 5 'extending in the longitudinal direction of the base 2, which are arranged on two opposite sides of the base 2 and for receiving side projections 6, the is the box foot 15, the lid 4 are formed.
  • Each of the receiving grooves 5, 5 ' has a groove base 7, 7'.
  • the base 2 has at least three passages 8, which are arranged parallel to one another and spaced apart from the receiving grooves 5, 5 'in a plane and extend perpendicular to and between the receiving grooves 5, 5' (see in particular also the Figures 2 , 7th , 9 and 11 ).
  • Flat tubes 9 are passed tightly through the passages 8, a side part 19 being inserted through each of the two outer passages.
  • an intermediate area 10 is formed, which is arranged parallel to the groove bases 7, 7 'of the receiving grooves 5, 5' by a height difference h (cf. Figures 3 and 5 ).
  • a ramp 11 runs between each intermediate area 10 and the groove bottoms 7, 7 ′ parallel to the longitudinal direction of the passages 8, the ramps 11 of adjacent intermediate areas 10 being spaced parallel to one another.
  • the seal 3 is designed as a circumferential sealing cord.
  • the seal 3 now runs in the receiving grooves 5, 5 'and each with a sealing web 12 (cf. Figure 10 ) over two ramps 11 and the intermediate area 10 in between, the ramps 11 are inclined according to the invention by an angle ⁇ between 20 and 65 ° with respect to the intermediate region 10 and usually also with respect to the horizontal (cf. Fig. 3 ), or have an S-shaped course (cf. Fig. 5 ), with a turning point W in the range of 10% to 80% of the height difference h starting from the groove bottom 7,7 'of the receiving groove 5,5'.
  • the bottom 2 is cut out to illustrate the radius R2, but of course has no opening in this area.
  • Each of the ramps 11 is rounded at the transition to the receiving groove 5, 5 'with a radius R1 and at the transition between area 10 with a radius R2.
  • the radii R1 and R2 can of course be of different sizes, larger radii helping to reduce the stress peaks acting on the seal 3. Due to an angle ⁇ of less than 20 °, on the one hand disadvantages for the later forming process of the passage 8 and on the other hand the lateral guidance of the seal 3 along the receiving groove 5, 5 'can be reduced. At an angle of ⁇ greater than 65 °, the contact pressure F D , which acts from the cover 4 on the seal 3, would be too low, which is clearly shown in FIG Figure 4 is shown.
  • a ratio of the height difference h to the diameter D of a section is Seal 3 in the receiving groove 5, 5 'in the unpressed state 0.7 ⁇ h / D ⁇ 2.5, preferably 1.0 ⁇ h / D ⁇ 2.0.
  • a ratio of the radius R1 or R2 to a radius R3 of the section of the seal 3 in the receiving groove 5, 5 'in the pressed state 0.3 ⁇ R1 / R3 ⁇ 3.0 or 0.3 ⁇ R2 / R3 is ⁇ 3.0.
  • a lower ratio could possibly cause a leak due to insufficient surface pressure in the transition area between the receiving groove 5, 5 ′ and the ramp 11. If the ratio is too large, there is insufficient contact pressure along the ramp 11 or a disadvantage in terms of installation space, since a wider base 2 is required.
  • the leakage (leakage L) is shown as a function of the mentioned radius ratio, whereby it can be clearly seen that with a radius ratio R1 / R3 or R2 / R3 between 0.3 and 3.0 the leakage, ie the leakage, is lowest.
  • At least one of the ramps 11 is also designed as a groove 13 which extends parallel to the longitudinal direction of the passages 8 and in which the Seal 3 runs in sections, the ratio of the degree of groove filling through the seal 3 in the groove 13 to the degree of groove filling through the seal 3 in the receiving groove 5, 5 'in the compressed state of the seal 3 should be between 1.0 and 1.4. If the ratio is in the range mentioned, the seal 3 can on the one hand be optimally guided and fixed and on the other hand an optimal sealing function can be achieved through a stronger compression in the ramp area 11 or in the transition area of the ramp 11 to the receiving groove 5, 5 'or to the intermediate area 10 will.
  • the ramps 11 have a width b1 and the intermediate regions 10 have a width b2, the ratio of the width b1 to b2 being between 0.3 and 1.0.
  • the cross section of the seal 3 in the area of the ramp 11 should be> 40% of the cross section of the seal 3 in the area of the receiving groove 5, 5 ', preferably between 50% and 70%. In this way, an optimized degree of slot filling can be achieved using simple structural means.
  • the seal 3 has at least one further prestressing web 14 in addition to the actual sealing web 12, which runs parallel to the sealing web 12 and which causes a reduction in tensile stress on the seal 3. This makes it possible to ensure the desired optimal position required for tightness both along the receiving groove 5, 5 ′ and between the passages 8.
  • the cover 4 has longitudinal side projections 6 or box feet 15 on two opposite sides, with only one of the two sides being shown in the case shown and with the side projections 6 extending into the receiving grooves 5, 5 ' and have a lengthwise overhang 16 protruding beyond the respective receiving groove 5, 5 '.
  • the supernatant 16 should over the Area where the seal 3 bends, protrude. It can also protrude beyond the receiving groove 5, 5 ', but can also terminate flush with it.
  • Figure 13 shows such a connection between the cover 4 and the base 2, the course of the seal 3 and the position of an outer closure 17, which extends beyond the course of the seal 3 between the passages 8 through the protrusion 16 also shown on the box foot 15. In this way, in particular, an improved sealing function is possible through greater contact pressure.
  • a projection 20 for positioning the cover 4 on the base 2 is arranged on the box base 15. Such a projection 20 is used to optimally position the cover 4 relative to the bottom 2 in the longitudinal direction and also enables the tolerances of the tolerance chain to be halved in the longitudinal direction.
  • the receiving groove 5, 5 'can also have a wall 18 which is at least partially bent over to connect the cover 4 to the base 2 in such a way that it engages behind part of the box foot 15 of the cover 4.
  • the wall 18 of the receiving groove 5, 5 'can have several regions and / or battlements that repeat themselves in their geometric shape are arranged symmetrically to the passages 8 of the bottom 2 and which can be bent or bent around the box foot 15 of the cover 4 (cf. Figure 1 ).
  • the heat exchanger 1 has a side part 19 with a side part overhang s for connecting the base 2 to the cover 4, the mean distance between the side part 19 and an adjacent, outer flat tube 9 being the value q and the ratio s / q between Should be 0.3 and 0.7 (compare Figures 11 and 12 ).
  • Figure 11 a combination with a side part overhang s is shown, the ratio s / q in this case being 0.7.
  • a ratio s / q 0.3, a smaller contact surface on the side projection 6 or box foot 15 is achieved.
  • All passages 8 of the base 2 can have the same contour and the same surface area for pipes 9 and side parts 19, which simplifies production. It is also possible that the outer passages 8, depending on the wall thickness of the side part 19, have a smaller or larger surface area than the other passages 8.
  • the shape of the transition areas in particular between the two outer passages 8, can differ from that of the other transition areas.
  • the ramp 11 can only be embossed between the outer three passages 8.
  • the shape of the transition areas can also differ in such a way that a repeating pattern results.
  • such a floor 2 can be produced as an endless sheet and can thus be used extremely flexibly with heat exchangers 1 of different sizes. At the same time, an optimal sealing effect can be achieved.

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

Claims (13)

  1. Échangeur de chaleur (1) avec un fond (2), un joint (3) et un couvercle (4),
    - dans lequel le fond (2) présente deux rainures de réception (5, 5') parallèles et espacées, s'étendant dans le sens longitudinal du fond (2), qui sont disposées sur deux côtés opposés du fond (2) et sont conçues pour recevoir des saillies latérales (6) du couvercle (4),
    - dans lequel chaque rainure de réception (5, 5') présente un fond de rainure (7, 7'),
    - dans lequel le fond (2) présente au moins trois passages (8) qui sont disposés parallèlement les uns aux autres et espacés des rainures de réception (5, 5') dans un plan et s'étendant perpendiculairement aux et entre les rainures de réception (5, 5'),
    - dans lequel une zone intermédiaire (10) est formée dans le plan entre deux passages (8), qui est disposée parallèlement aux fonds de rainures (7, 7') des rainures de réception (5, 5') d'une différence de hauteur h,
    - dans lequel une rampe (11) s'étend entre chaque zone intermédiaire (10) et les fonds de rainures (7, 7') parallèlement au sens longitudinal des passages (8) et les rampes (11) sont espacées parallèlement les unes aux autres,
    - dans lequel le joint (3) présente un cordon d'étanchéité circonférentiel,
    dans lequel
    - le joint (3) passe dans les rainures de réception (5, 5') et, respectivement avec une nervure d'étanchéité (12), sur deux rampes (11) et une zone intermédiaire (10) reposant entre les deux,
    - chaque rampe (11) est arrondie au niveau de la transition vers la rainure de réception (5, 5') avec un rayon R1 et au niveau de la transition vers la zone intermédiaire (10) avec un rayon R2,
    - les rampes (11) sont inclinées entre 20° < α < 65° par rapport à la zone intermédiaire (10), ou présentent un tracé en forme de S, un point de retournement W compris entre 10 % et 80 % de la différence de hauteur h étant disposé à partir du fond de rainure (7, 7') de la rainure de réception (5, 5'),
    caractérisé en ce
    qu'au moins l'une des rampes (11) est conçue comme une rainure (13) qui s'étend parallèlement au sens longitudinal des passages (8) et dans laquelle le joint (3) passe par des sections, le rapport du degré de remplissage de rainure à travers le joint (3) dans la rainure (13) de l'au moins une rampe (11) jusqu'au degré de remplissage de rainure à travers le joint (3) dans la rainure de réception (5, 5') à l'état pressé du joint (3) étant entre 1,0 et 1,4.
  2. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce
    qu'un rapport de la différence de hauteur h au diamètre D d'une section du joint (3) dans la rainure de réception (5, 5') à l'état non pressé est de 0,7 < h/D < 2,5, de préférence de 1,0 < h/D < 2,0.
  3. Échangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce
    qu'un rapport du rayon R1 ou R2 à un rayon R3 de la section du joint (3) dans la rainure de réception (5, 5') à l'état pressé est de 0,3 < R1/R3 < 3,0 ou 0,3 < R2/R3 < 3,0.
  4. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    qu'une extrémité longitudinale d'un passage (8) opposée à la rainure de réception (5, 5') est comprise entre 1 mm < a < 15 mm, en particulier entre 2 mm < a < 6 mm plus près de la rainure de réception (5, 5') qu'une transition de la rampe (11) à la zone intermédiaire (10).
  5. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les rampes (11) présentent une largeur b1 et les zones intermédiaires (10) présentent une largeur b2, le rapport étant de 0,3 < b1/b2 < 1,0.
  6. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que
    le joint (3) présente au moins une nervure de précontrainte (14) destinée à réduire les contraintes de traction sur le joint (3), l'au moins une nervure de précontrainte (4) étant disposée parallèlement à une nervure d'étanchéité (12).
  7. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le couvercle (4) est conçu comme une boîte, qui présente des saillies latérales (6) s'étendant longitudinalement sur la zone extérieure de la boîte sur deux côtés opposés, les saillies latérales (6) s'étendant dans les rainures de réception (5, 5') et présentant un surplomb (16) dépassant dans le sens longitudinal sur le joint (3).
  8. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le couvercle (4) est conçu comme une boîte qui présente un pied de boîte (15), une saillie (20) destinée au positionnement de la boîte sur le fond (2) étant disposée sur un côté longitudinal sur la zone extérieure du pied de boîte (15).
  9. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que
    la rainure de réception (5, 5') présente une paroi (18) qui est au moins partiellement rabattue de sorte qu'elle s'engage derrière au moins une partie de la saillie latérale (6) du couvercle (4).
  10. Échangeur de chaleur selon la revendication 9,
    caractérisé en ce que
    la paroi (18) de la rainure de réception (5, 5') présente plusieurs zones et/ou créneaux qui se répètent dans leur forme géométrique, qui sont disposés symétriquement aux passages (8) du fond (2) et peuvent être repliés ou rabattus autour de la saillie latérale (6) du couvercle (4).
  11. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'échangeur de chaleur (1) présente une partie latérale (19) qui est introduite à travers un passage du fond, avec un surplomb de partie latérale s destiné à connecter le fond (2) au couvercle (4), la distance moyenne entre la partie latérale (19) et un tube plat extérieur adjacent (9) ayant la valeur q et le rapport étant de 0,3 < s/q < 0,7.
  12. Échangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    tous les passages (8) présentent le même contour et la même superficie.
  13. Échangeur de chaleur selon l'une quelconque des revendications 1 à 11,
    caractérisé en ce
    qu'au moins les deux passages extérieurs (8) disposés aux extrémités latérales du fond présentent une superficie qui diffère de l'autrement même superficie des autres passages (8) par un facteur de 0,8 à 1,3.
EP14812156.9A 2013-12-23 2014-12-02 Échangeur de chaleur à joint périphérique Active EP3087337B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013227113.1A DE102013227113A1 (de) 2013-12-23 2013-12-23 Wärmetauscher mit umlaufender Dichtung
PCT/EP2014/076262 WO2015096956A1 (fr) 2013-12-23 2014-12-02 Échangeur de chaleur à joint périphérique

Publications (2)

Publication Number Publication Date
EP3087337A1 EP3087337A1 (fr) 2016-11-02
EP3087337B1 true EP3087337B1 (fr) 2020-11-11

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Application Number Title Priority Date Filing Date
EP14812156.9A Active EP3087337B1 (fr) 2013-12-23 2014-12-02 Échangeur de chaleur à joint périphérique

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US (1) US10436526B2 (fr)
EP (1) EP3087337B1 (fr)
JP (1) JP6577472B2 (fr)
CN (1) CN105829825B (fr)
BR (1) BR112016013657B1 (fr)
DE (1) DE102013227113A1 (fr)
RU (1) RU2666262C2 (fr)
WO (1) WO2015096956A1 (fr)

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EP3428567B1 (fr) * 2017-07-13 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
DE102017216639A1 (de) * 2017-09-20 2019-03-21 Mahle International Gmbh Wärmetauscher
DE102018214943A1 (de) * 2018-09-03 2020-03-05 Mahle International Gmbh Wärmeübertrager

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Also Published As

Publication number Publication date
EP3087337A1 (fr) 2016-11-02
RU2016121224A (ru) 2018-01-30
BR112016013657B1 (pt) 2020-12-01
JP6577472B2 (ja) 2019-09-18
US10436526B2 (en) 2019-10-08
RU2016121224A3 (fr) 2018-07-02
CN105829825A (zh) 2016-08-03
US20160320148A1 (en) 2016-11-03
RU2666262C2 (ru) 2018-09-06
DE102013227113A1 (de) 2015-07-09
WO2015096956A1 (fr) 2015-07-02
CN105829825B (zh) 2018-01-30
JP2017503992A (ja) 2017-02-02

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