EP3172516B1 - Heat exchanger such as an internal exchanger for a motor vehicle air-conditioning system and system including same - Google Patents

Heat exchanger such as an internal exchanger for a motor vehicle air-conditioning system and system including same Download PDF

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Publication number
EP3172516B1
EP3172516B1 EP14759243.0A EP14759243A EP3172516B1 EP 3172516 B1 EP3172516 B1 EP 3172516B1 EP 14759243 A EP14759243 A EP 14759243A EP 3172516 B1 EP3172516 B1 EP 3172516B1
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EP
European Patent Office
Prior art keywords
exchanger
pipe
outer tube
twisted
fluid
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EP14759243.0A
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German (de)
French (fr)
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EP3172516A1 (en
Inventor
Christophe Bernard
Frédéric LEDOUX
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Hutchinson SA
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Hutchinson SA
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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/06—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits having a single U-bend
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F2265/28—Safety or protection arrangements; Arrangements for preventing malfunction for preventing noise
    • 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
    • F28F2265/30—Safety or protection arrangements; Arrangements for preventing malfunction for preventing vibrations

Definitions

  • the present invention relates to a heat exchanger according to the preamble of claim 1.
  • Such an exchanger is known from DE 10 2008 036 601 A1 and proposes a solution to the problem of vibrations leading to acoustic genes.
  • such an internal heat exchanger is of metal type and is connected to the corresponding pipes of the air conditioning circuit which comprise in particular hoses, via connectors mounted at each end of the exchanger, which can be for example of the type plate, consisting of a stack of flat tubes and performing the heat exchange both by convection with the air outside the exchanger than by conduction, or of multitube type which in its simplest version is of type tubular coaxial against the current, then performing the heat exchange without the aforementioned convection.
  • said acoustic attenuation means may consist exclusively of said at least one conduit while being able to effectively attenuate these sound frequencies.
  • this non-coaxial arrangement of said or each multi-channel internal duct makes it possible to confer an increased compactness on the exchangers of the invention in comparison with the aforementioned internal heat exchangers of the prior art, thanks to the twisting and / or winding of the or each duct and the integration thereof of these channels which provides a much higher exchange surface than with the prior art coaxial tubular internal ducts .
  • said at least one duct is of flat type.
  • said at least one flat duct may have at least one partition separating said contiguous channels and extending substantially in a first transverse dimension of said at least one duct perpendicular to a second transverse dimension of said at least one duct, so that one of said first dimension and second dimension is smaller than the other.
  • said at least one flat duct may have a plurality of said partitions which delimit at least one row of said contiguous channels, said at least one flat duct having a thickness formed by said first dimension and a width formed by said second dimension said width being greater than at least 5 times and preferably at least 10 times said thickness.
  • the or each flat duct may have a cross section for example elliptical, oval, polygonal (eg rectangular) with rounded sides or corners, or any other shape at least partly oblong, without limitation, so that the or each flat duct has in cross section this thickness much smaller than its width in the manner of a hollow ribbon and partitioned.
  • this flat geometry of the or each multichannel duct according to the invention makes it possible to maximize the peripheral width of the or each duct (in terms of developed area) with respect to the passage section of the high-pressure fluid which is divided in this conduit, which provides an improved heat exchange in comparison with that provided by one or more non-flat cylindrical or prismatic conduits.
  • each inner duct may not be flat but tubular, for example of circular cross-section or shaped regular polygon such as a square (i.e. defining a generally cylindrical surface or prismatic flattened).
  • said at least one duct may be twisted and / or wound around and along said axis on at least 75% of the length of said outer tube between two radial closure walls respectively integral with two ends of said outer tube, said at least one duct may comprise two straight axial end portions which protrude axially from said closure walls and which are respectively fixed to two connection supports fluidic fluid comprising means for fluidic connection of the high-pressure fluid flowing in said channels within a closed circuit incorporating the exchanger.
  • At least one of said two fluidic connection supports may further comprise fluidic connection means within said low pressure fluid circuit circulating around said at least one conduit inside said outer tube.
  • the exchanger may be provided, near and below at least one of said closure walls, with at least one stitching attached to a fluidic connection flange of the fluid at low pressure within the circuit. flange being adjacent to one of said fluid connection supports.
  • said at least one conduit may be twisted and / or helically wound around and along said axis radially away from said outer tube.
  • this torsion and / or helical conformation of the or each duct according to the invention has the advantage of being easily shapeable, in particular in the case of a twisted duct.
  • said at least one duct is twisted at a torsion angle of between 10 ° and 80 ° around and along said axis by being inscribed in a cylindrical surface.
  • said at least one conduit is wound in a circular helix along said axis by forming non-contiguous turns inscribed in a cylindrical surface.
  • windings other than the circular helix are possible for said at least one conduit according to the invention, provided they form a convolution around and along said axis.
  • the outer tube may have a thermal conductivity lower than that of said at least one conduit.
  • the or each internal duct (for example made of a metallic material of high thermal conductivity, such as aluminum) may be provided more thermally conductive than the outer tube, which may be less generally thermally conductive because of of the material (typically metallic) which constitutes it and / or of a thermally insulating coating (for example of reinforced plastic material) of which this external tube (for example based on aluminum) can be provided.
  • the low-pressure fluid exchanges heat with the outside of the internal heat exchanger.
  • the exchanger may be an internal heat exchanger for a motor vehicle air-conditioning circuit comprising two low and high pressure portions traversed by a refrigerant circulating at high pressure in said at least one a conduit and, at low pressure, around said at least one conduit within the outer tube.
  • An air conditioning circuit for a motor vehicle comprises said internal heat exchanger and a thermoregulatory valve ("thermal expansion valve" in English) for adjusting the expansion of the low pressure fluid which circulates only in the gas phase in the exchanger (this low-pressure gas phase may nevertheless contain fine lubricant particles mixed with the refrigerant).
  • thermoregulatory valve in English
  • the circuit may be devoid of accumulator, said refrigerant being other than CO 2 and being for example R134a, R152 or R1234yf, non-limiting.
  • thermoregulatory valve which is an adjustable expansion device taking into account the evaporator outlet temperature that this circuit comprises.
  • capillary-type air conditioning circuits must have an accumulator for storing the liquid fluid and separating its liquid phase from its vapor phase returning to the suction of the compressor.
  • the air conditioning circuit 1 illustrated in the figure 1 is in known manner a closed circuit or "loop" which comprises, in addition to an internal heat exchanger E, several elements distributed inside the engine compartment of the vehicle, in particular a compressor 2, a cooler or condenser 3 and an evaporator 4, and wherein circulates a refrigerant under pressure, such as R134a, R1234yf or R152, without limitation. All these elements are interconnected by rigid or flexible lines consisting of rigid tubular portions and / or flexible, which have at each of their ends sealed connection means.
  • each duct 20A, 20B is twisted or wound along the X axis between two radial closure walls 14 mounted (for example by welding or brazing) against two circumferential ends 15 of the tube 10, and each end portion straight 22 of the conduit 20A, 20B axially passes through the corresponding closure wall 14 by being fixed (for example by welding or brazing).
  • Each end portion 22 thus terminates axially beyond the adjacent closure wall 14, and is attached to one of the two fluidic connection supports 23.
  • connection support 23 Fixing the conduit 20A, 20B to each connection support 23 is detailed in figures 5 and 7 , which show in this support 23 a female portion 24 for connecting the high-pressure fluid flowing in the channels 21 of the conduit 20A, 20B.
  • the female connection part HP 24 is formed in a non-through manner in the support 23, and it is arranged facing and radially around the ends of the channels 21 which open inside the support 23.
  • This support 23 is further provided with a through hole 25 for attachment to the remainder of the circuit 1.
  • each flange 13 has, like the support 23, a female part 16 with a non-throughgoing LP connection disposed facing the tubing 12 which opens inside the flange 13, and a through orifice 17 for its attachment to the rest of the circuit 1.
  • the variant of the figure 8 relating to a fluid connection support 33 for both high pressure and low pressure includes, in place of the closure wall 14 of the figure 7 and in addition to a female portion 34 for connecting the fluid HP, another female portion 36 which is intended to connect the LP fluid and which is accordingly arranged throughly through a male flange 37 which is provided with protrusion support 33 and facing the free space between the conduit 20A, 20B and the tube 10. Also visible at the figure 8 a fixing orifice 38 of the male flange 37 adjacent to the female portion 36 of BP connection and an attachment hole 39 of the support 33 adjacent to the female portion 34 HP connection.
  • FIG 9 To the figure 9 is illustrated another exchanger E i3 according to the invention, for which the fluidic connection of the HP fluid flowing in the channels 21 of three twisted internal ducts 20A or helically wound 20B, is similar to that described with reference to figures 5 and 7 .
  • the female part 24 of the support 23 for connecting the high-pressure fluid flowing in the channels 21 of the three ducts 20A is similar to that of the figure 7 , being disposed here opposite the adjacent ends of the channels 21 which open into the support 23 as at the figure 7 .
  • the conduit 20C forms a round-trip from one end 15a to the other 15b of the tube 10 via the vertical connecting portion 2 , from a section 20 1a of each twisted portion 20 1 which has a horizontal end adjacent the end 15a opening on a fluid connection support 43 and whose torsion over a quarter turn leads to a vertical section 1b 1b defining each wing of the U.
  • connection support 43 fixed to the tube 10 has in this embodiment two female portions 44 for connecting the fluid HP circulating in the conduit 20C, respectively to the two emergent sections 20 1a of the two parallel twisted portions 20 1 (respectively consisting of an upper section 20 1a and a lower section 20 1a ) of the conduit 20C.
  • the LP fluid it circulates as previously in the radially delimited space between the duct 20C and the tube 10.
  • channels 21 formed in the or each internal duct non-coaxial of the invention can vary and include eg channels of substantially polygonal passage section (eg, rectangular or square as Figures 6-9 ), substantially elliptical, oblong or other which are arranged in one or more rows of channels superimposed or not separated from each other by partitions 21a straight or not, and in a total number of channels at least 2 and advantageously at least equal to 5.
  • substantially polygonal passage section eg, rectangular or square as Figures 6-9
  • substantially elliptical, oblong or other which are arranged in one or more rows of channels superimposed or not separated from each other by partitions 21a straight or not, and in a total number of channels at least 2 and advantageously at least equal to 5.
  • the exchanger E ' operates with a low pressure fluid circulating in the conduit 20' and at high pressure in the annular space between the conduit 20 'and the tube 10', thus according to a principle opposite to that of the present invention .
  • the exchanger E ' is provided with two connection supports 23' to the fluid BP sealingly receiving the conduit 20 ', and two flanges 13' for connecting the fluid HP via two elbows 12 'communicating radially with the tube 10' ,
  • a second countercurrent “control” internal heat exchanger E for an air conditioning circuit illustrated schematically in FIG. figure 12 also tubular coaxial with an internal conduit 20 "cylindrical disposed inside an outer tube 10 "(both aluminum) of much greater diameter and length L of the tube 10" equal to 250 mm.
  • the exchanger E "operates with a high pressure fluid circulating in the conduit 20” and at low pressure in the annular space between the conduit 20 “and the tube 10", as in the present invention.
  • the exchanger E is provided with connection supports 23" to the fluid HP sealingly receiving the conduit 20 ", and flanges 13" for connecting the fluid HP via two elbows 12 “communicating radially with the tube 10",
  • an internal heat exchanger according to the invention was tested, such as the exchanger E i1 illustrated in FIGS. Figures 2-5 and 7 and described above, which was characterized by an outer tube length equal to 250 mm, and by the presence of a single multi-channel internal conduit 20 twisted at an angle of about 45) (both aluminum) ,
  • a "white” noise (ie formed of multifrequencies) has been generated downstream of the low-pressure connection of each exchanger E ', E “, E i1 , it being specified that the upstream end has been closed (ie plugged).
  • each exchanger E ', E “, Ei 1 By definition, "upstream” and “downstream” are determined with respect to the flow direction of the low pressure fluid. The direction opposite to that of the fluid has been chosen for acoustical sense, since it is the suction of the compressor 2 which generates noise upstream of the low-pressure line of the air-conditioning circuit, ie, the thermoregulator valve 5 of the evaporator 4.
  • the downstream acoustic pressure (ie input pressure Pe) was compared with the upstream acoustic pressure (ie output pressure Ps), and the three curves presented in the graph of the figure 10 correspond in ordered at the Ps / Pe ratio.
  • the lower the curve ie the reduced ordinate for a given frequency carried on the abscissa), the better is the measured acoustic attenuation of the exchanger E ', E ", E i1 .
  • This graph of the figure 10 shows that the acoustic transfer function Ps / Pe of the exchanger E i1 according to the invention is globally reduced compared with that of the "control" exchangers E 'and E " , which shows a generally reduced acoustic transmission and therefore a generally improved acoustic efficiency and in particular very significantly improved in the field of low frequencies typically below about 1100 Hz, with a compactness also increased for the exchanger E i1 compared to exchangers E and E ', for the same acoustic performance obtained.

Description

La présente invention concerne un échangeur thermique conforme au préambule de la revendication 1. Un tel échangeur est connu de DE 10 2008 036 601 A1 et propose une solution au problème de vibrations menant à des gênes acoustiques.The present invention relates to a heat exchanger according to the preamble of claim 1. Such an exchanger is known from DE 10 2008 036 601 A1 and proposes a solution to the problem of vibrations leading to acoustic genes.

Dans certains circuits de climatisation pour véhicules automobiles, il est nécessaire de réaliser un échange ou transfert thermique entre le fluide de la portion haute pression du circuit que l'on cherche à refroidir et le même fluide issu de la portion basse pression de ce circuit qui sert de source froide et qui est réchauffé en échange, pour améliorer le rendement du circuit. On utilise à cet effet un échangeur thermique dit interne, du fait qu'il ne recherche pas d'échange avec l'air extérieur au véhicule ni avec l'air de l'habitacle.In certain air conditioning circuits for motor vehicles, it is necessary to perform an exchange or heat transfer between the fluid of the high pressure portion of the circuit that is to be cooled and the same fluid from the low pressure portion of this circuit which serves as a cold source and is warmed in exchange, to improve the performance of the circuit. To this end, an internal heat exchanger is used, because it does not seek an exchange with the outside air of the vehicle or with the air of the passenger compartment.

De manière connue, un tel échangeur thermique interne est de type métallique et est connecté aux conduites correspondantes du circuit de climatisation qui comprennent en particulier des flexibles, via des connecteurs montés à chacune des extrémités de l'échangeur, lequel peut être par exemple de type à plaque, étant constitué d'un empilement de tubes plats et réalisant l'échange thermique tant par convection avec l'air extérieur à l'échangeur que par conduction, ou bien de type à multitubes qui dans sa version la plus simple est de type tubulaire coaxial à contre-courant, réalisant alors l'échange thermique sans la convection précitée.In known manner, such an internal heat exchanger is of metal type and is connected to the corresponding pipes of the air conditioning circuit which comprise in particular hoses, via connectors mounted at each end of the exchanger, which can be for example of the type plate, consisting of a stack of flat tubes and performing the heat exchange both by convection with the air outside the exchanger than by conduction, or of multitube type which in its simplest version is of type tubular coaxial against the current, then performing the heat exchange without the aforementioned convection.

Dans ce dernier cas et notamment avec des fluides tels que le R134a ou le R152, cet échangeur tubulaire coaxial définit généralement :

  • à l'intérieur d'un tube interne de l'échangeur, au moins un canal radialement interne destiné à véhiculer le fluide issu de la portion basse pression du circuit, et
  • radialement entre ce tube interne et un tube externe formant enveloppe pour l'échangeur, un canal radialement externe usuellement pourvu d'ailettes longitudinales conçues pour optimiser le transfert thermique entre les fluides circulant dans les canaux interne(s) et externe qui sont réparties sur sa circonférence et qui peuvent être solidaires des tubes interne et/ou externe ou encore rapportées entre ces deux tubes, comme illustré par exemple dans le document US-A-6 434 972 .
In the latter case and in particular with fluids such as R134a or R152, this coaxial tubular exchanger generally defines:
  • inside an inner tube of the exchanger, at least one radially internal channel intended to convey the fluid coming from the low pressure portion of the circuit, and
  • radially between this inner tube and an outer tube forming a shell for the exchanger, a radially outer channel usually provided with longitudinal fins designed to optimize the heat transfer between the fluids circulating in the internal (s) and external channels which are distributed over its circumference and which may be integral with the inner and / or outer tubes or reported between these two tubes, as illustrated for example in the document US-A-6,434,972 .

Il est par ailleurs connu du document KR-A-2007/0097609 de prévoir, à l'intérieur d'une enveloppe externe d'un échangeur thermique interne utilisant du CO2 comme fluide frigorigène, un conduit interne qui n'est pas de type tubulaire coaxial mais de forme plate et formant des allers-retours en zigzag dans la direction longitudinale de l'enveloppe, ce conduit plat intégrant une rangée de canaux longitudinaux adjacents séparés par des cloisons. Plus précisément, le circuit de climatisation présenté dans ce document utilise un capillaire (« orifice tube » en anglais) permettant le retour du CO2 à l'état liquide vers l'aspiration du compresseur, en utilisant un accumulateur pour séparer les phases liquide et vapeur et récupérer la seule partie gazeuse à comprimer par ce compresseur.It is also known from the document KR-A-2007/0097609 to provide, within an outer casing of an internal heat exchanger using CO 2 as a refrigerant, an internal duct which is not of the coaxial tubular type but of flat shape and forming zigzag back-and-forth movements in the longitudinal direction of the casing, this flat duct incorporating a row of adjacent longitudinal channels separated by partitions. More specifically, the air conditioning circuit presented in this document uses a capillary ("orifice tube" in English) for the return of CO 2 in the liquid state to the suction of the compressor, using a battery to separate the liquid phase and vapor and recover the only gaseous part to be compressed by this compressor.

Ces échangeurs thermiques internes connus présentent notamment comme inconvénients, pour l'obtention d'une efficacité d'échange thermique satisfaisante, de transmettre un niveau de bruit relativement élevé en fonctionnement et de devoir présenter une longueur et donc un encombrement importants.These known internal heat exchangers have particular disadvantages, for obtaining a satisfactory heat exchange efficiency, to transmit a relatively high noise level in operation and have to have a length and therefore a large footprint.

Un but de la présente invention est de proposer un échangeur thermique qui remèdie à ces inconvénients, l'échangeur comportant :

  • un tube externe présentant un axe longitudinal de symétrie, une longueur mesurée le long dudit axe et étant adapté pour véhiculer un fluide à basse pression, et
  • au moins un conduit qui est monté radialement à l'intérieur dudit tube externe et qui présente une pluralité de canaux longitudinaux adaptés pour véhiculer un fluide à haute pression,
l'échangeur comprenant des moyens d'atténuation acoustique aptes à atténuer des bruits transmis par le fluide à basse pression.An object of the present invention is to provide a heat exchanger which overcomes these disadvantages, the exchanger comprising:
  • an outer tube having a longitudinal axis of symmetry, a length measured along said axis and being adapted to convey a fluid at low pressure, and
  • at least one duct which is mounted radially inside said outer tube and which has a plurality of longitudinal channels adapted to convey a fluid at high pressure,
the exchanger comprising acoustic attenuation means capable of attenuating noises transmitted by the fluid at low pressure.

A cet effet, un échangeur selon l'invention est conforme à la revendication 1.For this purpose, an exchanger according to the invention is in accordance with claim 1.

On notera que cet agencement tordu et/ou enroulé du ou de chaque conduit interne multicanaux autour de l'axe longitudinal de symétrie de l'échangeur sur la majeure partie de la longueur du tube externe permet de manière inattendue de procurer une atténuation acoustique significative des fréquences sonores transmises par le fluide à basse pression comprenant en particulier une atténuation efficace des basses fréquences, en comparaison des échangeurs coaxiaux de l'art antérieur.It will be noted that this twisted and / or wound arrangement of the or each multichannel internal duct around the longitudinal axis of symmetry of the exchanger over most of the length of the outer tube makes it possible, unexpectedly, to provide a significant acoustic attenuation of the sound frequencies transmitted by the low-pressure fluid including in particular an effective attenuation of the low frequencies, in comparison with the coaxial exchangers of the prior art.

Avantageusement, lesdits moyens d'atténuation acoustique peuvent être exclusivement constitués dudit au moins un conduit tout en étant aptes à atténuer efficacement ces fréquences sonores.Advantageously, said acoustic attenuation means may consist exclusively of said at least one conduit while being able to effectively attenuate these sound frequencies.

On notera également que pour une même efficacité d'échange thermique obtenue, cet agencement non coaxial dudit ou de chaque conduit interne multicanaux permet de conférer une compacité accrue aux échangeurs de l'invention en comparaison des échangeurs thermiques internes précités de l'art antérieur, grâce à la torsion et/ou à l'enroulement du ou de chaque conduit et à l'intégration à ce dernier de ces canaux qui procure une surface d'échange beaucoup plus élevée qu'avec les conduits internes tubulaires coaxiaux de l'art antérieur.It will also be noted that for the same heat exchange efficiency obtained, this non-coaxial arrangement of said or each multi-channel internal duct makes it possible to confer an increased compactness on the exchangers of the invention in comparison with the aforementioned internal heat exchangers of the prior art, thanks to the twisting and / or winding of the or each duct and the integration thereof of these channels which provides a much higher exchange surface than with the prior art coaxial tubular internal ducts .

Selon une autre caractéristique préférentielle de l'invention, ledit au moins un conduit est de type plat.According to another preferred feature of the invention, said at least one duct is of flat type.

Dans ce mode particulièrement avantageux de l'invention, ledit au moins un conduit plat peut présenter au moins une cloison qui sépare des dits canaux contigus et qui s'étend sensiblement suivant une première dimension transversale dudit au moins un conduit perpendiculairement à une seconde dimension transversale dudit au moins un conduit, de sorte que l'une desdites première dimension et seconde dimension soit inférieure à l'autre.In this particularly advantageous embodiment of the invention, said at least one flat duct may have at least one partition separating said contiguous channels and extending substantially in a first transverse dimension of said at least one duct perpendicular to a second transverse dimension of said at least one duct, so that one of said first dimension and second dimension is smaller than the other.

Encore plus avantageusement, ledit au moins un conduit plat peut présenter une pluralité de dites cloisons qui délimitent au moins une rangée de dits canaux contigus, ledit au moins un conduit plat présentant une épaisseur formée par ladite première dimension et une largeur formée par ladite seconde dimension, ladite largeur étant supérieure à au moins 5 fois et de préférence à au moins 10 fois ladite épaisseur.Even more advantageously, said at least one flat duct may have a plurality of said partitions which delimit at least one row of said contiguous channels, said at least one flat duct having a thickness formed by said first dimension and a width formed by said second dimension said width being greater than at least 5 times and preferably at least 10 times said thickness.

Le ou chaque conduit plat peut présenter une section transversale par exemple de forme elliptique, ovale, polygonale (e.g. rectangulaire) à côtés ou à coins pouvant être arrondis, ou toute autre forme au moins en partie oblongue, à titre non limitatif, de sorte que le ou chaque conduit plat présente en section transversale cette épaisseur très inférieure à sa largeur à la manière d'un ruban creux et cloisonné.The or each flat duct may have a cross section for example elliptical, oval, polygonal (eg rectangular) with rounded sides or corners, or any other shape at least partly oblong, without limitation, so that the or each flat duct has in cross section this thickness much smaller than its width in the manner of a hollow ribbon and partitioned.

On notera que cette géométrie plate du ou de chaque conduit multicanaux selon l'invention permet de maximiser la largeur périphérique du ou de chaque conduit (en termes de surface développée) par rapport à la section de passage du fluide à haute pression qui est divisé dans ce conduit, ce qui procure un échange thermique amélioré en comparaison de celui procuré par un ou des conduits cylindriques ou prismatiques non plats.It will be noted that this flat geometry of the or each multichannel duct according to the invention makes it possible to maximize the peripheral width of the or each duct (in terms of developed area) with respect to the passage section of the high-pressure fluid which is divided in this conduit, which provides an improved heat exchange in comparison with that provided by one or more non-flat cylindrical or prismatic conduits.

On notera cependant qu'en variante le ou chaque conduit interne pourrait ne pas être plat mais tubulaire, par exemple de section transversale circulaire ou en forme de polygone régulier tel qu'un carré (i.e. définissant une surface globalement cylindrique ou prismatique non aplatie).Note however that alternatively the or each inner duct may not be flat but tubular, for example of circular cross-section or shaped regular polygon such as a square (i.e. defining a generally cylindrical surface or prismatic flattened).

Selon un mode particulier de réalisation de invention, ledit au moins un conduit peut être tordu et/ou enroulé autour et le long dudit axe sur au moins 75 % de la longueur dudit tube externe entre deux parois de fermeture radiales respectivement solidaires de deux extrémités dudit tube externe, ledit au moins un conduit pouvant comporter deux portions d'extrémité axiales droites qui dépassent axialement desdites parois de fermeture et qui sont respectivement fixées à deux supports de connexion fluidique comportant des moyens de connexion fluidique du fluide à haute pression circulant dans lesdits canaux au sein d'un circuit fermé incorporant l'échangeur.According to a particular embodiment of the invention, said at least one duct may be twisted and / or wound around and along said axis on at least 75% of the length of said outer tube between two radial closure walls respectively integral with two ends of said outer tube, said at least one duct may comprise two straight axial end portions which protrude axially from said closure walls and which are respectively fixed to two connection supports fluidic fluid comprising means for fluidic connection of the high-pressure fluid flowing in said channels within a closed circuit incorporating the exchanger.

Conformément à ce mode de réalisation, l'un au moins desdits deux supports de connexion fluidique peut comporter en outre des moyens de connexion fluidique au sein dudit circuit du fluide à basse pression circulant autour dudit au moins un conduit à l'intérieur dudit tube externe.According to this embodiment, at least one of said two fluidic connection supports may further comprise fluidic connection means within said low pressure fluid circuit circulating around said at least one conduit inside said outer tube. .

En variante, l'échangeur peut être pourvu, à proximité et en deçà de l'une au moins desdites parois de fermeture, d'au moins un piquage fixé à une bride de connexion fluidique du fluide à basse pression au sein du circuit, la bride étant adjacente à l'un desdits supports de connexion fluidique.Alternatively, the exchanger may be provided, near and below at least one of said closure walls, with at least one stitching attached to a fluidic connection flange of the fluid at low pressure within the circuit. flange being adjacent to one of said fluid connection supports.

Selon une autre caractéristique de l'invention, ledit au moins un conduit peut être torsadé et/ou enroulé en hélice autour et le long dudit axe radialement à distance dudit tube externe.According to another characteristic of the invention, said at least one conduit may be twisted and / or helically wound around and along said axis radially away from said outer tube.

On notera que cette conformation en torsade et/ou en hélice du ou de chaque conduit selon l'invention sur quasiment toute la longueur du tube externe (i.e. sur avantageusement 90 à 100 % de ladite longueur) permet de conférer une longueur nettement réduite et donc une compacité accrue de manière significative aux échangeurs selon l'invention en comparaison d'un échangeur à conduit(s) interne(s) droit(s), pour une même performance thermique donnée.It will be noted that this conformation in twist and / or helix of the or each duct according to the invention over almost the entire length of the outer tube (ie advantageously 90 to 100% of said length) makes it possible to confer a significantly reduced length and therefore a significantly increased compactness to the exchangers according to the invention in comparison with an exchanger with internal duct (s) right (s), for the same thermal performance.

On notera également que cette conformation en torsade et/ou en hélice du ou de chaque conduit selon l'invention présente l'avantage d'être aisément façonnable, en particulier dans le cas d'un conduit torsadé.It should also be noted that this torsion and / or helical conformation of the or each duct according to the invention has the advantage of being easily shapeable, in particular in the case of a twisted duct.

Selon un premier exemple de réalisation de l'invention, ledit au moins un conduit est torsadé suivant un angle de torsion compris entre 10° et 80° autour et le long dudit axe en étant inscrit dans une surface cylindrique.According to a first exemplary embodiment of the invention, said at least one duct is twisted at a torsion angle of between 10 ° and 80 ° around and along said axis by being inscribed in a cylindrical surface.

Selon un second exemple de réalisation de l'invention, ledit au moins un conduit est enroulé en hélice circulaire le long dudit axe en formant des spires non jointives inscrites dans une surface cylindrique.According to a second embodiment of the invention, said at least one conduit is wound in a circular helix along said axis by forming non-contiguous turns inscribed in a cylindrical surface.

Selon un troisième exemple de réalisation de l'invention, ledit au moins un conduit comprend :

  • deux portions torsadées qui s'étendent en étant mutuellement espacées à partir d'une première extrémité du tube externe en étant chacune torsadées autour et le long dudit axe suivant un angle de torsion de préférence égal à 90° (i.e. suivant un quart de tour), et
  • une portion de raccordement qui s'étend au voisinage d'une seconde extrémité du tube externe perpendiculairement audit axe et qui raccorde les portions torsadées entre elles à la manière de l'âme d'un « U » dont les ailes sont formées par ces portions torsadées.
According to a third embodiment of the invention, said at least one conduit comprises:
  • two twisted portions which extend mutually spaced from a first end of the outer tube each being twisted around and along said axis at a twist angle preferably equal to 90 ° (ie following a quarter turn) , and
  • a connecting portion which extends in the vicinity of a second end of the outer tube perpendicular to said axis and which connects the twisted portions together in the manner of the soul of a "U" whose wings are formed by these portions twisted.

On notera que des enroulements autres que l'hélice circulaire sont envisageables pour ledit au moins un conduit selon l'invention, pourvu qu'ils forment une circonvolution autour et le long dudit axe.Note that windings other than the circular helix are possible for said at least one conduit according to the invention, provided they form a convolution around and along said axis.

Avantageusement, le tube externe peut présenter une conductibilité thermique inférieure à celle dudit au moins un conduit. En d'autres termes, le ou chaque conduit interne (par exemple réalisé en un matériau métallique de conductibilité thermique élevée, tel que l'aluminium) peut être prévu plus thermiquement conducteur que le tube externe, lequel peut être globalement moins thermiquement conducteur du fait du matériau (typiquement métallique) qui le constitue et/ou d'un revêtement thermiquement isolant (par exemple en matière plastique renforcée) dont ce tube externe (par exemple à base d'aluminium) peut être pourvu. En effet, on cherche à éviter dans la présente invention que le fluide à basse pression échange de la chaleur avec l'extérieur de l'échangeur thermique interne.Advantageously, the outer tube may have a thermal conductivity lower than that of said at least one conduit. In other words, the or each internal duct (for example made of a metallic material of high thermal conductivity, such as aluminum) may be provided more thermally conductive than the outer tube, which may be less generally thermally conductive because of of the material (typically metallic) which constitutes it and / or of a thermally insulating coating (for example of reinforced plastic material) of which this external tube (for example based on aluminum) can be provided. Indeed, it is sought to avoid in the present invention that the low-pressure fluid exchanges heat with the outside of the internal heat exchanger.

Selon une autre caractéristique de l'invention, l'échangeur peut être un échangeur thermique interne pour un circuit de climatisation de véhicule automobile comportant deux portions de basse et haute pression parcourues par un fluide frigorigène qui circule, à haute pression, dans ledit au moins un conduit et, à basse pression, autour dudit au moins un conduit à l'intérieur du tube externe.According to another characteristic of the invention, the exchanger may be an internal heat exchanger for a motor vehicle air-conditioning circuit comprising two low and high pressure portions traversed by a refrigerant circulating at high pressure in said at least one a conduit and, at low pressure, around said at least one conduit within the outer tube.

Un circuit de climatisation pour véhicule automobile selon l'invention comporte ledit échangeur thermique interne et une valve thermorégulatrice (« thermal expansion valve » en anglais) pour régler la détente du fluide à basse pression qui circule uniquement en phase gazeuse dans l'échangeur (cette phase basse pression gazeuse pouvant néanmoins comporter de fines particules de lubrifiant mélangées au fluide frigorigène).An air conditioning circuit for a motor vehicle according to the invention comprises said internal heat exchanger and a thermoregulatory valve ("thermal expansion valve" in English) for adjusting the expansion of the low pressure fluid which circulates only in the gas phase in the exchanger (this low-pressure gas phase may nevertheless contain fine lubricant particles mixed with the refrigerant).

Avantageusement, le circuit peut être dépourvu d'accumulateur, ledit fluide frigorigène étant autre que le CO2 et étant par exemple le R134a, le R152 ou le R1234yf, à titre non limitatif.Advantageously, the circuit may be devoid of accumulator, said refrigerant being other than CO 2 and being for example R134a, R152 or R1234yf, non-limiting.

On notera que la détente du fluide frigorigène à basse pression est réalisée dans le circuit de l'invention par cette valve thermorégulatrice qui est un dispositif réglable de détente tenant compte de la température de sortie de l'évaporateur que comporte ce circuit. Contrairement à cela, les circuits de climatisation précités de type à capillaire doivent comporter un accumulateur pour stocker le fluide liquide et séparer sa phase liquide de sa phase vapeur retournant vers l'aspiration du compresseur.It will be noted that the expansion of the refrigerant at low pressure is carried out in the circuit of the invention by this thermoregulatory valve which is an adjustable expansion device taking into account the evaporator outlet temperature that this circuit comprises. In contrast, the above-mentioned capillary-type air conditioning circuits must have an accumulator for storing the liquid fluid and separating its liquid phase from its vapor phase returning to the suction of the compressor.

D'autres caractéristiques, avantages et détails de l'invention ressortiront à la lecture de la description suivante de plusieurs exemples de réalisation de l'invention, donnés à titre illustratif et non limitatif, la description étant réalisée en référence avec les dessins joints, parmi lesquels :

  • la figure 1 est une vue schématique d'un circuit de climatisation pour véhicule automobile selon l'invention incorporant un échangeur thermique interne égaiement selon l'invention,
  • la figure 2 est une vue latérale en perspective d'un échangeur thermique interne selon un mode de réalisation de l'invention, qui est représenté pourvu de supports de connexion fluidique pour la haute pression et de tubulures et brides pour la basse pression à raccorder à ce circuit,
  • la figure 3 est une vue latérale de dessus et en perspective d'un échangeur selon l'invention, représenté avec lesdits supports de connexion pour la haute pression mais sans les tubulures et brides de la figure 2,
  • la figure 4 est une vue en perspective de détail de l'intérieur d'une extrémité de l'échangeur de la figure 3, montrant un conduit interne multicanaux torsadé selon le premier exemple de l'invention,
  • la figure 5 est une vue schématique partielle à la fois en coupe axiale et en vue latérale d'une extrémité d'un échangeur selon ce premier exemple montrant la géométrie torsadée du conduit multicanaux et les raccordements haute et basse pression de l'échangeur,
  • la figure 5a est une vue schématique en perspective avec arrachements partiels d'un échangeur selon un autre exemple de l'invention montrant une autre géométrie torsadée du conduit multicanaux et son raccordement à la ligne haute pression par un support de connexion fluidlque,
  • la figure 6 est une vue en perspective d'une extrémité d'un échangeur selon un autre exemple de l'invention en cours de fabrication, montrant l'insertion dans le tube externe d'un conduit multicanaux enroulé en hélice,
  • la figure 7 est une vue schématique en perspective avec arrachements partiels d'une extrémité d'un échangeur selon l'invention détaillant le raccordement à la ligne haute pression par le support de connexion fluidique fixé à un conduit multicanaux,
  • la figure 8 est une vue schématique en perspective avec arrachements partiels d'une extrémité d'un autre échangeur de l'invention détaillant le raccordement aux lignes haute et basse pression par un autre support de connexion fluidique fixé à un conduit multicanaux,
  • la figure 9 est une vue schématique en perspective avec arrachements partiels analogue à la figure 7 d'une extrémité d'un autre échangeur selon l'invention détaillant le raccordement à la ligne haute pression par le support de connexion fluidique fixé à plusieurs conduits internes multicanaux,
  • la figure 10 est un graphique illustrant en termes de fonction de transfert acoustique l'atténuation acoustique améliorée obtenue pour un échangeur selon le premier exemple de l'invention illustré à la figure 5, en comparaison de deux échangeurs « témoin » à conduit interne tubulaire coaxial respectivement illustrés aux figures 11 et 12, et
  • les figures 11 et 12 sont des vues schématiques en coupe axiale des deux échangeurs « témoin » coaxiaux testés à la figure 10.
Other features, advantages and details of the invention will emerge on reading the following description of several examples of embodiments of the invention, given by way of illustration and not limitation, the description being made with reference to the accompanying drawings, among which :
  • the figure 1 is a schematic view of an air conditioning circuit for a motor vehicle according to the invention incorporating an internal heat exchanger also according to the invention,
  • the figure 2 is a perspective side view of an internal heat exchanger according to an embodiment of the invention, which is shown provided with fluidic connection supports for the high pressure and tubings and flanges for the low pressure to be connected to this circuit,
  • the figure 3 is a side view from above and in perspective of an exchanger according to the invention, shown with said connection supports for the high pressure but without the tubes and flanges of the figure 2 ,
  • the figure 4 is a detail perspective view of the inside of one end of the heat exchanger of the figure 3 , showing a twisted multichannel internal conduit according to the first example of the invention,
  • the figure 5 is a partial schematic view both in axial section and in lateral view of an end of an exchanger according to this first example showing the twisted geometry of the multichannel duct and the high and low pressure connections of the exchanger,
  • the figure 5a is a diagrammatic perspective view with partial detachment of an exchanger according to another example of the invention showing another twisted geometry of the multi-channel duct and its connection to the high pressure line by a fluidlque connection support,
  • the figure 6 is a perspective view of an end of an exchanger according to another example of the invention being manufactured, showing the insertion into the outer tube of a multichannel duct wound in a helix,
  • the figure 7 is a schematic perspective view with partial cutaway of an end of an exchanger according to the invention detailing the connection to the high pressure line by the fluidic connection support fixed to a multichannel duct,
  • the figure 8 is a schematic perspective view with partial cutaway of one end of another exchanger of the invention detailing the connection to the high and low pressure lines by another fluidic connection support attached to a multichannel conduit,
  • the figure 9 is a schematic perspective view with partial cut-away similar to the figure 7 at one end of another exchanger according to the invention detailing the connection to the high pressure line by the fluidic connection support fixed to several multi-channel internal ducts,
  • the figure 10 is a graph illustrating in terms of acoustic transfer function the improved acoustic attenuation obtained for an exchanger according to the first example of the invention illustrated in FIG. figure 5 , compared with two "control" exchangers with coaxial tubular internal duct respectively illustrated in FIGS. Figures 11 and 12 , and
  • the Figures 11 and 12 are schematic views in axial section of the two coaxial "control" heat exchangers tested at the figure 10 .

Le circuit de climatisation 1 illustré à la figure 1 est de manière connue un circuit fermé ou « boucle » qui comprend, outre un échangeur thermique interne E, plusieurs éléments répartis à l'intérieur du compartiment moteur du véhicule, notamment un compresseur 2, un refroidisseur ou condenseur 3 et un évaporateur 4, et dans lequel circule un fluide frigorigène sous pression, tel que du R134a, du R1234yf ou du R152, à titre non limitatif. Tous ces éléments sont reliés entre eux par des lignes rigides ou flexibles constitués par des portions tubulaires rigides et/ou souples, qui présentent en chacune de leurs extrémités des moyens de raccordement étanches.The air conditioning circuit 1 illustrated in the figure 1 is in known manner a closed circuit or "loop" which comprises, in addition to an internal heat exchanger E, several elements distributed inside the engine compartment of the vehicle, in particular a compressor 2, a cooler or condenser 3 and an evaporator 4, and wherein circulates a refrigerant under pressure, such as R134a, R1234yf or R152, without limitation. All these elements are interconnected by rigid or flexible lines consisting of rigid tubular portions and / or flexible, which have at each of their ends sealed connection means.

Plus précisément, le circuit 1 comporte :

  • une ligne basse pression BP destinée à véhiculer le fluide frigorigène entre le l'évaporateur 4 et le compresseur 2, à travers l'échangeur E via une entrée eBP de fluide basse pression à réchauffer et une sortie sBP de ce fluide ainsi réchauffé, et
  • une ligne haute pression HP destinée à véhiculer ce même fluide en aval du compresseur 2 et du refroidisseur 3 via une entrée eHP de fluide haute pression à refroidir et une sortie sHP de ce fluide ainsi refroidi, une valve de détente 5 thermorégulatrice étant agencée en aval de cette sortie sHP et en amont de l'évaporateur 4.
More specifically, the circuit 1 comprises:
  • a low-pressure line BP for conveying the refrigerant between the evaporator 4 and the compressor 2, through the exchanger E via a low pressure fluid inlet e BP to be heated and a BP output of the fluid thus heated, and
  • a high pressure line HP for conveying the same fluid downstream of the compressor 2 and the cooler 3 via an inlet e HP of high pressure fluid to be cooled and an output s HP of the fluid thus cooled, a thermoregulatory expansion valve 5 being arranged downstream of this outlet s HP and upstream of the evaporator 4.

L'échangeur E est de type à contre-courant, et il est destiné à refroidir le fluide issu de la ligne HP par conduction au contact du même fluide issu de la ligne BP qui est réchauffé en échange. A cet effet et comme illustré aux figures 2 et 3, cet échangeur E comprend essentiellement :

  • un tube externe 10 formant enveloppe cylindrique qui est pourvu, à proximité immédiate de chacune de ses deux extrémités, de piquages radiaux 11 se prolongeant par des tubulures 12 coudées à angle droit axialement vers l'extérieur et se terminant par des brides 13 pour le raccordement étanche du flux basse pression circulant à l'intérieur du tube 10 à la ligne BP du circuit 1, et
  • au moins un conduit 20A, 20B (voir la figure 5 pour le conduit 20A et la figure 6 pour le conduit 20B) radialement interne au tube 10 qui est plat dans l'exemple illustré, intègre des canaux longitudinaux 21 contigus véhiculant le fluide à haute pression à l'état liquide (visibles aux figures 6 à 9) et qui est tordu et/ou enroulé autour et le long de l'axe longitudinal de symétrie X du tube 10 (voir figure 5), le ou chaque conduit 20A, 20B comportant deux portions d'extrémités droites 22 (i.e. ni tordues, ni enroulées) respectivement montées dans deux supports de connexion fluidique 23 pour le raccordement étanche du flux haute pression divisé dans les canaux 21 à la ligne HP du circuit.
The exchanger E is of counter-current type, and is intended to cool the fluid from the HP line by conduction in contact with the same fluid from the BP line which is heated in exchange. For this purpose and as illustrated in Figures 2 and 3 this exchanger E essentially comprises:
  • an outer tube 10 forming a cylindrical envelope which is provided, in the immediate vicinity of each of its two ends, with radial taps 11 extending through tubes 12 bent at right angles axially outwards and terminating in flanges 13 for connection sealing of the low-pressure flow circulating inside the tube 10 at the BP line of the circuit 1, and
  • at least one conduit 20A, 20B (see figure 5 for the conduit 20A and the figure 6 for the conduit 20B) radially internal to the tube 10 which is flat in the illustrated example, integrates contiguous longitudinal channels 21 conveying the fluid at high pressure in the liquid state (visible at Figures 6 to 9 ) and which is twisted and / or wound around and along the longitudinal axis of symmetry X of the tube 10 (see figure 5 ), the or each duct 20A, 20B having two portions of straight ends 22 (ie neither bent nor wound) respectively mounted in two fluidic connection supports 23 for the sealed connection of the high pressure flow divided in the channels 21 to the line HP of the circuit.

Comme illustré aux figures 5 et 6 montrant respectivement un échangeur Ei1 à conduit torsadé 20A selon un angle α par exemple compris entre 30° et 60° et un échangeur Ei2 à conduit 20B enroulé en hélice circulaire autour et le long de l'axe X (avec des spires S non jointives), le flux basse pression circule dans l'espace radialement délimité entre le conduit 20A, 20B et le tube 10.As illustrated in figures 5 and 6 respectively showing an exchanger E i1 twisted conduit 20A at an angle α for example between 30 ° and 60 ° and an exchanger E i2 20B conduit wound in a circular helix around and along the X axis (with turns S no joined), the low pressure flow circulates in the radially delimited space between the duct 20A, 20B and the tube 10.

Plus précisément et comme notamment illustré aux figures 4 et 5, le ou chaque conduit 20A, 20B est torsadé ou enroulé le long de l'axe X entre deux parois de fermeture radiales 14 montées (par exemple par soudage ou brasage) contre deux extrémités circonférentielles 15 du tube 10, et chaque portion d'extrémité droite 22 du conduit 20A, 20B traverse axialement la paroi de fermeture 14 correspondante en y étant fixée (par exemple par soudage ou brasage). Chaque portion d'extrémité 22 se termine ainsi axialement au-delà de la paroi de fermeture 14 adjacente, et elle est fixée à l'un des deux supports de connexion fluidique 23.More precisely and as illustrated in particular Figures 4 and 5 the or each duct 20A, 20B is twisted or wound along the X axis between two radial closure walls 14 mounted (for example by welding or brazing) against two circumferential ends 15 of the tube 10, and each end portion straight 22 of the conduit 20A, 20B axially passes through the corresponding closure wall 14 by being fixed (for example by welding or brazing). Each end portion 22 thus terminates axially beyond the adjacent closure wall 14, and is attached to one of the two fluidic connection supports 23.

La fixation du conduit 20A, 20B à chaque support de connexion 23 est détaillée aux figures 5 et 7, qui montrent dans ce support 23 une partie femelle 24 pour le raccordement du fluide à haute pression circulant dans les canaux 21 du conduit 20A, 20B. La partie femelle de connexion HP 24 est formée de manière non traversante dans le support 23, et elle est disposée en regard et radialement autour des extrémités des canaux 21 qui débouchent à l'intérieur du support 23. Ce support 23 est en outre pourvu d'un orifice traversant 25 pour sa fixation au reste du circuit 1.Fixing the conduit 20A, 20B to each connection support 23 is detailed in figures 5 and 7 , which show in this support 23 a female portion 24 for connecting the high-pressure fluid flowing in the channels 21 of the conduit 20A, 20B. The female connection part HP 24 is formed in a non-through manner in the support 23, and it is arranged facing and radially around the ends of the channels 21 which open inside the support 23. This support 23 is further provided with a through hole 25 for attachment to the remainder of the circuit 1.

La figure 5 détaille par ailleurs la fixation (par exemple par soudage ou brasage) à la bride 13 correspondante de chaque tubulure 12 coudée issue du piquage 11 soudé ou brasé autour du tube 10, pour le raccordement BP. On voit que chaque bride 13 présente à l'instar du support 23 une partie femelle 16 de connexion BP non traversante disposée en regard de la tubulure 12 qui débouche à l'intérieur de la bride 13, et un orifice traversant 17 pour sa fixation au reste du circuit 1.The figure 5 further details the attachment (for example by welding or brazing) to the corresponding flange 13 of each pipe 12 bent from the stitching 11 welded or brazed around the tube 10 for the BP connection. It can be seen that each flange 13 has, like the support 23, a female part 16 with a non-throughgoing LP connection disposed facing the tubing 12 which opens inside the flange 13, and a through orifice 17 for its attachment to the rest of the circuit 1.

La variante de la figure 8 concernant un support de connexion fluidique 33 à la fois pour la haute pression et la basse pression inclut, à la place de la paroi de fermeture 14 de la figure 7 et en plus d'une partie femelle 34 destinée à connecter le fluide HP, une autre partie femelle 36 qui est destinée à connecter le fluide BP et qui est agencée en conséquence de manière traversante à travers une bride mâle 37 dont est pourvu en saillie le support 33 et en regard de l'espace libre entre le conduit 20A, 20B et le tube 10. Sont également visibles à la figure 8 un orifice de fixation 38 de la bride mâle 37 adjacent à la partie femelle 36 de connexion BP et un orifice de fixation 39 du support 33 adjacent à la partie femelle 34 de connexion HP.The variant of the figure 8 relating to a fluid connection support 33 for both high pressure and low pressure includes, in place of the closure wall 14 of the figure 7 and in addition to a female portion 34 for connecting the fluid HP, another female portion 36 which is intended to connect the LP fluid and which is accordingly arranged throughly through a male flange 37 which is provided with protrusion support 33 and facing the free space between the conduit 20A, 20B and the tube 10. Also visible at the figure 8 a fixing orifice 38 of the male flange 37 adjacent to the female portion 36 of BP connection and an attachment hole 39 of the support 33 adjacent to the female portion 34 HP connection.

A la figure 9 est illustré un autre échangeur Ei3 selon l'invention, pour lequel la connexion fluidique du fluide HP circulant dans les canaux 21 de trois conduits internes torsadés 20A ou enroulés en hélice 20B, est analogue à celle décrite en référence aux figures 5 et 7. Dans cette variante à plusieurs conduits 20A, on voit notamment que la partie femelle 24 du support 23 pour le raccordement du fluide à haute pression circulant dans les canaux 21 des trois conduits 20A est analogue à celle de la figure 7, étant disposée ici en vis-à-vis des extrémités adjacentes des canaux 21 qui débouchent à l'intérieur du support 23 comme à la figure 7.To the figure 9 is illustrated another exchanger E i3 according to the invention, for which the fluidic connection of the HP fluid flowing in the channels 21 of three twisted internal ducts 20A or helically wound 20B, is similar to that described with reference to figures 5 and 7 . In this variant with several ducts 20A, it is seen in particular that the female part 24 of the support 23 for connecting the high-pressure fluid flowing in the channels 21 of the three ducts 20A is similar to that of the figure 7 , being disposed here opposite the adjacent ends of the channels 21 which open into the support 23 as at the figure 7 .

A la figure 5a est illustré un autre échangeur Ei4 selon l'invention, qui comporte un unique conduit interne 20C présentant une pluralité de canaux longitudinaux 21 et comprenant :

  • deux portions torsadées 201 qui s'étendent en étant mutuellement espacées à partir d'une première extrémité 15a du tube externe 10 en étant chacune torsadées autour et le long de l'axe X du tube 10 suivant un angle de torsion d'un quart de tour, et
  • une portion de raccordement 202 qui s'étend au voisinage de l'extrémité opposée 15b du tube 10 perpendiculairement à l'axe X et qui raccorde les portions torsadées 201 entre elles à la manière de l'âme d'un «U» dont les ailes sont formées par ces portions 201.
To the figure 5a is illustrated another exchanger E i4 according to the invention, which comprises a single inner conduit 20C having a plurality of longitudinal channels 21 and comprising:
  • two twisted portions 20 1 extending mutually spaced from a first end 15a of the outer tube Each being twisted around and along the X axis of the tube 10 at a twist angle of a quarter of a turn, and
  • a connecting portion 2 which extends in the vicinity of the opposite end 15b of the tube 10 perpendicular to the X axis and which connects the twisted portions 1 to one another in the manner of the core of a "U" whose wings are formed by these portions 20 1 .

Plus précisément on voit à la figure 5a que le conduit 20C forme un aller-retour d'une extrémité 15a à l'autre 15b du tube 10 via la portion de raccordement 202 verticale, à partir d'un tronçon 201a de chaque portion torsadée 201 qui présente une extrémité horizontale adjacente à l'extrémité 15a débouchant sur un support de connexion fluidique 43 et dont la torsion sur un quart de tour aboutit à un tronçon vertical 201b définissant chaque aile du U.More precisely, we see at the figure 5a that the conduit 20C forms a round-trip from one end 15a to the other 15b of the tube 10 via the vertical connecting portion 2 , from a section 20 1a of each twisted portion 20 1 which has a horizontal end adjacent the end 15a opening on a fluid connection support 43 and whose torsion over a quarter turn leads to a vertical section 1b 1b defining each wing of the U.

Ce support de connexion 43 fixé au tube 10 présente dans cet exemple de réalisation deux parties femelles 44 pour le raccordement du fluide HP circulant dans le conduit 20C, respectivement aux deux tronçons débouchants 201a des deux portions torsadées parallèles 201 (respectivement constitués d'un tronçon supérieur 201a et d'un tronçon inférieur 201a) du conduit 20C. Quant au fluide BP, il circule comme précédemment dans l'espace radialement délimité entre le conduit 20C et le tube 10.This connection support 43 fixed to the tube 10 has in this embodiment two female portions 44 for connecting the fluid HP circulating in the conduit 20C, respectively to the two emergent sections 20 1a of the two parallel twisted portions 20 1 (respectively consisting of an upper section 20 1a and a lower section 20 1a ) of the conduit 20C. As for the LP fluid, it circulates as previously in the radially delimited space between the duct 20C and the tube 10.

D'une manière générale en référence à l'ensemble des modes et exemples de réalisation de l'invention qui viennent d'être décrits, on notera que la géométrie, l'agencement et le nombre des canaux 21 formés dans le ou chaque conduit interne non coaxial de l'invention peuvent varier et englobent par exemple des canaux de section de passage sensiblement polygonale (e.g, rectangulaire ou carrée comme aux figures 6-9), sensiblement elliptique, oblongue ou autre qui sont agencés suivant une ou plusieurs rangées à canaux superposés ou non séparés entre eux par des cloisons 21a droites ou non, et suivant un nombre total de canaux au moins égal à 2 et avantageusement au moins égal à 5.In general with reference to all the embodiments and embodiments of the invention which have just been described, it will be noted that the geometry, the arrangement and the number of channels 21 formed in the or each internal duct non-coaxial of the invention can vary and include eg channels of substantially polygonal passage section (eg, rectangular or square as Figures 6-9 ), substantially elliptical, oblong or other which are arranged in one or more rows of channels superimposed or not separated from each other by partitions 21a straight or not, and in a total number of channels at least 2 and advantageously at least equal to 5.

Concernant les dimensions des échangeurs selon l'invention, tels que par exemple les échangeurs thermiques internes Ei1 et Ei2 précités, elles peuvent notamment inclure, à titre exemplatif et nullement limitatif :

  • une longueur totale L de tube externe 10 inférieure ou égale à 250 mm et avantageusement de seulement 200 mm, en comparaison des longueurs usuelles d'échangeurs thermiques internes qui pour la même performance thermique présentent une longueur de tube externe typiquement d'environ 500 mm, soit le double de cette longueur L selon l'invention,
  • un diamètre D de tube 10 compris entre 20 mm et 30 mm,
  • une épaisseur e de conduit(s) 20A, 20B comprise entre 2 mm et 5 mm, et
  • une largeur l de conduit(s) 20A, 20B comprise entre 20 mm et 60 mm.
As regards the dimensions of the exchangers according to the invention, such as for example the internal heat exchangers E i1 and E i2 mentioned above, they may in particular include, by way of example and in no way limitative:
  • a total length L of external tube 10 less than or equal to 250 mm and advantageously only 200 mm, in comparison with the usual lengths of internal heat exchangers which for the same thermal performance have an external tube length typically of about 500 mm, twice this length L according to the invention,
  • a diameter D of tube 10 between 20 mm and 30 mm,
  • a thickness e of conduit (s) 20A, 20B of between 2 mm and 5 mm, and
  • a width l of conduit (s) 20A, 20B between 20 mm and 60 mm.

Essais d'atténuation acoustique d'échangeurs «témoin» E' et E" et d'un échangeur Ei1 selon l'invention : Acoustic attenuation tests of "control" exchangers E 'and E "and an exchanger Ei1 according to the invention :

On a testé un premier échangeur thermique interne « témoin » E' à contre-courant pour circuit de climatisation illustré schématiquement à la figure 11, qui est de manière classique de type tabulaire coaxial avec un conduit interne 20' cylindrique disposé à l'intérieur d'un tube externe 10' (tous deux en aluminium) de diamètre réduit et de longueur L du tube 10' égale à 500 mm. L'échangeur E' fonctionne avec un fluide à basse pression circulant dans le conduit 20' et à haute pression dans l'espace annulaire compris entre le conduit 20' et le tube 10', donc suivant un principe inverse à celui de la présente invention. L'échangeur E' est pourvu de deux supports de connexion 23' au fluide BP recevant de manière étanche le conduit 20', et de deux brides 13' de connexion au fluide HP via deux tubulures coudées 12' communiquant radialement avec le tube 10',A first counter-current "control" internal heat exchanger E 'for an air conditioning circuit schematically illustrated at figure 11 which is conventionally tabular type coaxial with a cylindrical internal conduit 20 'disposed inside an outer tube 10' (both of aluminum) of reduced diameter and length L of the tube 10 'equal to 500 mm . The exchanger E 'operates with a low pressure fluid circulating in the conduit 20' and at high pressure in the annular space between the conduit 20 'and the tube 10', thus according to a principle opposite to that of the present invention . The exchanger E 'is provided with two connection supports 23' to the fluid BP sealingly receiving the conduit 20 ', and two flanges 13' for connecting the fluid HP via two elbows 12 'communicating radially with the tube 10' ,

On a testé un second échangeur thermique interne «témoin » E" à contre-courant pour circuit de climatisation illustré schématiquement à la figure 12, également tubulaire coaxial avec un conduit interne 20" cylindrique disposé à l'intérieur d'un tube externe 10" (tous deux en aluminium) de diamètre beaucoup plus élevé et de longueur L du tube 10" égale à 250 mm. L'échangeur E" fonctionne avec un fluide à haute pression circulant dans le conduit 20" et à basse pression dans l'espace annulaire entre le conduit 20" et le tube 10", soit comme dans la présente invention. L'échangeur E" est pourvu de supports de connexion 23" au fluide HP recevant de manière étanche le conduit 20", et de brides 13" de connexion au fluide HP via deux tubulures coudées 12" communiquant radialement avec le tube 10",A second countercurrent "control" internal heat exchanger E for an air conditioning circuit illustrated schematically in FIG. figure 12 , also tubular coaxial with an internal conduit 20 "cylindrical disposed inside an outer tube 10 "(both aluminum) of much greater diameter and length L of the tube 10" equal to 250 mm. The exchanger E "operates with a high pressure fluid circulating in the conduit 20" and at low pressure in the annular space between the conduit 20 "and the tube 10", as in the present invention. The exchanger E "is provided with connection supports 23" to the fluid HP sealingly receiving the conduit 20 ", and flanges 13" for connecting the fluid HP via two elbows 12 "communicating radially with the tube 10",

On a enfin testé un échangeur thermique interne selon l'invention tel que l'échangeur Ei1 illustré aux figures 2-5 et 7 et décrit ci-dessus, qui était caractérisé par une longueur de tube externe 10 égale à 250 mm, et par la présence d'un unique conduit interne multicanaux 20 de type torsadé selon un angle d'environ 45) (tous deux en aluminium),Finally, an internal heat exchanger according to the invention was tested, such as the exchanger E i1 illustrated in FIGS. Figures 2-5 and 7 and described above, which was characterized by an outer tube length equal to 250 mm, and by the presence of a single multi-channel internal conduit 20 twisted at an angle of about 45) (both aluminum) ,

On a mesure les fonctions de transfert acoustiques pour chacun de ces trois échangeurs E', E" et Ei1 en utilisant comme fluide de l'air à la place du fluide frigorigène et dans des conditions normales de température (ambiante) et de pression (atmosphérique), étant précisé qu'un autre gaz produirait les mêmes courbes de fonctions de transfert que celles de la figure 10 avec simplement une homothétie de l'échelle des fréquences dans le rapport des célérités des ondes acoustiques, en raison de la compressibilité volumique du gaz. On a utilisé le principe de mesure suivant.The acoustic transfer functions for each of these three exchangers E ', E "and E i1 were measured using air instead of refrigerant under normal conditions of temperature (ambient) and pressure ( other gas would produce the same transfer function curves as the figure 10 with simply a scaling of the frequency scale in the ratio of the celestialities of the acoustic waves, due to the compressibility volume of the gas. The following measurement principle was used.

On a généré un bruit « blanc » (i.e. formé de multifréquences) en aval de la connexion basse pression de chaque échangeur E', E", Ei1, étant précisé que l'on a fermé (i.e. bouché) l'extrémité amont de chaque échangeur E', E", Ei1. Par définition, « amont » et « aval » sont déterminés par rapport au sens d'écoulement du fluide basse pression. On a choisi pour sens acoustique le sens opposé à celui du fluide, car c'est l'aspiration du compresseur 2 qui génère du bruit vers l'amont de la ligne basse pression du circuit de climatisation, i.e, la valve thermorégulatrice 5 de l'évaporateur 4.A "white" noise (ie formed of multifrequencies) has been generated downstream of the low-pressure connection of each exchanger E ', E ", E i1 , it being specified that the upstream end has been closed (ie plugged). each exchanger E ', E ", Ei 1 . By definition, "upstream" and "downstream" are determined with respect to the flow direction of the low pressure fluid. The direction opposite to that of the fluid has been chosen for acoustical sense, since it is the suction of the compressor 2 which generates noise upstream of the low-pressure line of the air-conditioning circuit, ie, the thermoregulator valve 5 of the evaporator 4.

On a comparé la pression acoustique aval (i.e. pression d'entrée Pe) à la pression acoustique amont (i.e. pression de sortie Ps), et les trois courbes présentées au graphique de la figure 10 correspondent en ordonnée au ratio Ps/Pe. Plus la courbe est basse (i.e. d'ordonnée réduite pour une fréquence donnée portée en abscisse), meilleure est l'atténuation acoustique mesurée de l'échangeur E', E", Ei1.The downstream acoustic pressure (ie input pressure Pe) was compared with the upstream acoustic pressure (ie output pressure Ps), and the three curves presented in the graph of the figure 10 correspond in ordered at the Ps / Pe ratio. The lower the curve (ie the reduced ordinate for a given frequency carried on the abscissa), the better is the measured acoustic attenuation of the exchanger E ', E ", E i1 .

Ce graphique de la figure 10 (dont les courbes ont subi un lissage pour plus de lisibilité) montre que la fonction de transfert acoustique Ps/Pe de l'échangeur Ei1 selon l'invention est globalement réduite par rapport à celle des échangeurs « témoin » E' et E", ce qui témoigne d'une transmission acoustique globalement réduite et donc d'une efficacité acoustique globalement améliorée et en particulier très nettement améliorée dans le domaine des basses fréquences typiquement inférieures à 1100 Hz environ, avec une compacité également accrue pour l'échangeur Ei1 comparé aux échangeurs E et E', pour une même performance acoustique obtenue.This graph of the figure 10 (whose curves have undergone a smoothing for greater readability) shows that the acoustic transfer function Ps / Pe of the exchanger E i1 according to the invention is globally reduced compared with that of the "control" exchangers E 'and E " , which shows a generally reduced acoustic transmission and therefore a generally improved acoustic efficiency and in particular very significantly improved in the field of low frequencies typically below about 1100 Hz, with a compactness also increased for the exchanger E i1 compared to exchangers E and E ', for the same acoustic performance obtained.

Claims (16)

  1. A heat exchanger (E, Ei1, Ei2, Ei3, Ei4) including:
    - an outer tube (10) having a longitudinal axis of symmetry (X), a length (L) measured along said axis and being suitable for carrying a low-pressure fluid (BP), and
    - at least one pipe (20A, 20B, 20C) that is mounted radially inside said outer tube for carrying a high-pressure fluid (HP),
    the exchanger comprising soundproofing means capable of attenuating the noise transmitted by the low-pressure fluid,
    characterized in that the pipe (20A, 20B, 20C) has a plurality of longitudinal channels (21) and in that said soundproofing means are formed at least partially by said at least one pipe, which is twisted and/or wound around and along said axis over more than 50% of said length.
  2. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to claim 1, characterized in that said at least one pipe (20A, 20B, 20C) is of the flat type.
  3. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to claim 2, characterized in that said at least one flat pipe (20A, 20B, 20C) has at least one partition (21a) that separates said adjacent channels (21) and extends substantially along a first transverse dimension (e) of said at least one pipe perpendicular to a second transverse dimension (I) of said at least one pipe, such that one of said first dimension and second dimension is smaller than the other.
  4. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to claim 3, characterized in that said at least one flat pipe (20A, 20B, 20C) has a plurality of said partitions (21a) that define at least one row of said adjacent channels (21), said at least one flat pipe having a thickness (e) formed by said first dimension and a width (I) formed by said second dimension, said width being greater than at least 5 times, and preferably at least 10 times, said thickness.
  5. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to one of the preceding claims, characterized in that said soundproofing means are exclusively made up of said at least one pipe (20A, 20B, 20C) and are able to effectively attenuate the noise frequencies transmitted by the low-pressure fluid (BP) in particular comprising low frequencies.
  6. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to one of the preceding claims, characterized in that said at least one pipe (20A, 20B, 20C) is twisted and/or wound around and along said axis (X) over at least 75% of said length (L) between two radial closing walls (14) respectively secured to the two ends (15, 15a, 15b) of said outer tube (10), said at least one pipe including two straight axial end portions (22) that axially protrude past said closing walls and that are respectively fastened to two fluid connection supports (23, 33, 43) including fluid connection means (24, 34, 44) for the high-pressure fluid (HP) circulating in said channels (21) within a closed circuit (1) incorporating the exchanger.
  7. The exchanger according to claim 6, characterized in that at least one of said two fluid connection supports (33) further includes fluid connection means (36) within said circuit (1) for the low-pressure fluid (BP) circulating around said at least one pipe (20A) inside said outer tube (10).
  8. The exchanger (E, Ei1) according to claim 6, characterized in that the exchanger is provided, near and below at least one of said closing walls (14), with at least one branch connection (11, 12) fastened to a fluid connection flange (13) for the low-pressure fluid (BP) within said circuit (1), the flange being adjacent to one of said fluid connection supports (23).
  9. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to one of the preceding claims, characterized in that said at least one pipe (20A, 20B, 20C) is twisted and/or wound in a spiral around and along said axis (X) radially at a distance from said outer tube (10) and over 90 to 100% of said length (L).
  10. The exchanger (E, Ei1, Ei3) according to claim 9, characterized in that said at least one pipe (20A) is twisted by a twisting angle (α) comprised between 10° and 80° around and along said axis (X), while being fitted in a cylindrical surface.
  11. The exchanger (Ei2) according to claim 9, characterized in that said at least one pipe (20B) is wound in a circular spiral along said axis (X) while forming non-adjacent turns (S) fitted into a cylindrical surface.
  12. The exchanger (Ei4) according to claim 9, characterized in that said at least one pipe (20C) comprises:
    - two twisted portions (201) that extend while being spaced apart from one another from a first end (15a) of the outer tube (10) while each being twisted around and along said axis (X) with a twisting angle (α) preferably equal to 90°, and
    - a connecting portion (202) that extends near a second end (15b) of said outer tube perpendicular to said axis (X) and that connects the twisted portions to one another like the core of a "U", the wings of which are formed by these twisted portions.
  13. The exchanger (E, Ei1, Ei2, Ei3) according to one of the preceding claims, characterized in that said outer tube (10) has a heat conductivity lower than that of said at least one pipe (20A, 20B).
  14. The exchanger (E, Ei1, Ei2, Ei3, Ei4) according to one of the preceding claims, characterized in that the exchanger is an inner heat exchanger for a motor vehicle air-conditioning circuit (1) including two high- and low-pressure portions (BP and HP) traveled by a coolant that circulates, at high pressure, in said at least one pipe (20A, 20B, 20C), and at low pressure, around said at least one pipe inside said outer tube (10).
  15. A motor vehicle air-conditioning circuit (1), characterized in that it includes said inner heat exchanger (E, Ei1, Ei2, Ei3, Ei4) according to claim 14 and a thermal expansion valve (5) to adjust the expansion of the low-pressure fluid (BP) that circulates only in the gaseous phase in the exchanger.
  16. The air-conditioning circuit (1) according to claim 15, characterized in that said circuit is provided without an accumulator, said coolant fluid being other than CO2 and for example being R134a, R152 or R1234yf.
EP14759243.0A 2014-07-25 2014-07-25 Heat exchanger such as an internal exchanger for a motor vehicle air-conditioning system and system including same Active EP3172516B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FR2014/051942 WO2016012664A1 (en) 2014-07-25 2014-07-25 Heat exchanger such as an internal exchanger for a motor vehicle air-conditioning system and system including same

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EP3172516A1 EP3172516A1 (en) 2017-05-31
EP3172516B1 true EP3172516B1 (en) 2018-05-30

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CN (1) CN106574824B (en)
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Publication number Priority date Publication date Assignee Title
FR3088994B1 (en) * 2018-11-28 2020-12-25 Liebherr Aerospace Toulouse Sas HEAT EXCHANGER AND FLUID COOLING SYSTEM INCLUDING SUCH A HEAT EXCHANGER
EP3964372A1 (en) * 2020-09-03 2022-03-09 TI Automotive Technology Center GmbH Tube assembly for transporting temperature control media

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3486489A (en) * 1968-02-12 1969-12-30 Modine Mfg Co Oil cooler
DE2209325C3 (en) * 1970-05-18 1978-08-03 Noranda Metal Industries Inc., Bellingham, Wash. (V.St.A.) Heat exchange tube
EP0112366A1 (en) * 1982-06-29 1984-07-04 AB Zander & Ingestrom Tube heat exchanger
JP2009041798A (en) * 2007-08-07 2009-02-26 Showa Denko Kk Heat exchanger
EP2340405B1 (en) * 2008-10-29 2018-06-13 MAHLE International GmbH Internal heat exchanger assembly having an internal bleed valve assembly
GB0909221D0 (en) * 2009-04-30 2009-07-15 Eaton Fluid Power Gmbh Heat exchanger
AU2012200524B2 (en) * 2009-07-06 2014-01-16 Frederick Mark Webb Heat Exchanger
FR2953917B1 (en) * 2009-12-10 2012-01-20 Hutchinson INTERNAL THERMAL EXCHANGER FOR AIR CONDITIONING CIRCUIT OF MOTOR VEHICLE AND SUCH CIRCUIT
KR101600296B1 (en) * 2010-08-18 2016-03-07 한온시스템 주식회사 Double pipe heat exchanger and manufacturing method the same
DE102013201313A1 (en) * 2012-02-23 2013-08-29 Ford Global Technologies, Llc Internal heat exchanger for air conditioner of motor vehicle, has high pressure side and low pressure side, where heat exchanger is formed in spatial-bodily manner so that pulsations of passed through refrigerants are predominantly damped

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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CN106574824A (en) 2017-04-19
BR112017001575A2 (en) 2018-01-30
EP3172516A1 (en) 2017-05-31
WO2016012664A1 (en) 2016-01-28
CN106574824B (en) 2019-05-17

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