WO2021136896A1 - Tube heat exchanger having spacers - Google Patents

Tube heat exchanger having spacers Download PDF

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Publication number
WO2021136896A1
WO2021136896A1 PCT/FR2020/052481 FR2020052481W WO2021136896A1 WO 2021136896 A1 WO2021136896 A1 WO 2021136896A1 FR 2020052481 W FR2020052481 W FR 2020052481W WO 2021136896 A1 WO2021136896 A1 WO 2021136896A1
Authority
WO
WIPO (PCT)
Prior art keywords
tubes
heat exchanger
corrugations
spacers
ridges
Prior art date
Application number
PCT/FR2020/052481
Other languages
French (fr)
Inventor
Gaël DURBECQ
Véronique WESTERMANN
Marian PERROTIN
Original Assignee
Valeo Systemes Thermiques
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Systemes Thermiques filed Critical Valeo Systemes Thermiques
Priority to CN202080095530.2A priority Critical patent/CN115038924A/en
Priority to US17/790,595 priority patent/US20230042424A1/en
Publication of WO2021136896A1 publication Critical patent/WO2021136896A1/en

Links

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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates to a heat exchanger and more particularly to a tube heat exchanger comprising spacers in the automotive field.
  • Tube heat exchangers generally have a bundle of tubes arranged parallel to each other and within which circulates a first coolant.
  • a second heat transfer fluid is intended to pass through the tube bundle passing between the tubes.
  • spacers are placed between the tubes in the passage of the second heat transfer fluid.
  • One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to provide an improved heat exchanger in which the risks of frost formation on its surface are reduced.
  • the present invention therefore relates to a heat exchanger comprising a bundle of tubes arranged parallel to each other and inside which a first heat transfer fluid is intended to circulate, a second fluid being intended to pass through the bundle of tubes between said tubes, said bundle of tubes comprising spacers disposed between said tubes, said spacers comprising corrugations extending in the direction of the length of the tubes, said corrugations comprising ridges in contact with said tubes and sidewalls connecting said ridges, the spacers comprising a first portion and a second portion, the first portion being disposed upstream of the second portion in the direction of passage of the second heat transfer fluid, the first portion protruding from the portion before the tubes, the ridges of the first portion having a profile having a flat and the ridges of the second portion having a rounded profile so that the corrugations have a sinusoidal profile.
  • the first portion of the spacers protrudes from the front edge of the tubes and that its ridges have a flat surface makes it possible to prevent the formation of frost.
  • the ridges with a flat part together with the protrusion allow better evacuation of water condensates on the front face of the heat exchanger, that is to say the face of the heat exchanger through which the second heat transfer fluid enters. Frost is therefore less likely to form.
  • the second portion extends from 100% to 66% of the width of the tubes.
  • the first and second portions are made from the same part.
  • the first and second portions are made from two separate pieces.
  • the pitch of the corrugations of the first portion and the pitch of the corrugations of the second portion are different.
  • the pitch of the corrugations of the first portion is greater than the pitch of the corrugations of the second portion.
  • the thickness of the first portion is greater than the thickness of the second portion.
  • the first portion comprises, in the direction of the width of the tubes, at least two series of slots offset from one another. According to another aspect of the invention, the first portion extends in a rectilinear profile in the direction of the width of the tubes.
  • the first portion extends in a corrugated profile in the direction of the width of the tubes.
  • FIG. 1 is a schematic representation of a heat exchanger
  • FIG. 2 is a partial schematic representation in perspective of a bundle of tubes of a heat exchanger
  • Figure 3 is a partial schematic sectional representation of a first insert portion
  • Figure 4 is a partial schematic sectional representation of a second insert portion
  • Figure 5 is a partial schematic representation in perspective of a spacer according to a first embodiment
  • Figure 6 is a partial schematic representation in perspective of a spacer according to a second embodiment
  • Figure 7 is a partial schematic representation in perspective of a spacer according to a third embodiment
  • Figure 8 is a partial schematic representation in perspective of a spacer according to a fourth embodiment.
  • first element or second element As well as first parameter and second parameter or even first criterion and second criterion, etc.
  • first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc.
  • indexing does not imply a priority of one element, parameter or criterion over another and such names can easily be interchanged without departing from the scope of the present description.
  • FIG. 1 shows a heat exchanger 1, generally of parallelepiped shape, comprising a bundle formed by a multitude of tubes 2 inside which is intended to circulate a first coolant, for example a refrigerant circulating in a circuit of reversible cooling.
  • the tubes 2 are of oblong section, defined by a major axis and a minor axis and are arranged parallel to each other.
  • the tubes 2 are flat tubes, that is to say they have two large sides of flat surface and parallel to the large axis as well as two small sides of curved surface forming the edge of the tubes 2 and connecting the edges of the large ones. sides. Between the tubes 2, there are spacers 6 connecting the long sides of two adjacent tubes 2. These spacers 6 act as a disturbance and increase the heat exchange surface with a second heat transfer fluid intended to pass through the tube bundle 2 passing between the tubes 2.
  • This second heat transfer fluid can for example be an air flow.
  • the spacers 6 are for example corrugated or crenellated strips, placed between the tubes 2 and fixed to said tubes 2.
  • the tubes 2 and the spacers 6 are generally made of metal, for example aluminum or aluminum alloy.
  • the tubes 2 and the spacers 6 forming the bundle are then generally fixed together by brazing. This is called a brazed bundle.
  • the heat exchanger 1 also comprises two collectors 3 or water boxes, a collector 3 being arranged at each end of the tubes 2. These collectors 3 each comprise a collector plate 4 and a cover 8 covering the collector plate 4 and close the collector 3. These collectors 3 allow the collection and / or distribution of the first heat transfer fluid so that it circulates in the tubes 2.
  • the collector plate 4 makes the connection in a sealed manner between the collector 3 and the bundle of tubes 2.
  • the collector plate 4 may be of generally rectangular shape.
  • the collector plate 4 also has a multitude of orifices having a shape corresponding to the shape of the cross section of the tubes 2 and capable of receiving the ends of the tubes 2.
  • the tubes 2 are fixed to the collector plate 4 in a sealed manner.
  • the tubes 2, the spacers 6 as well as the collector plates 4 being brazed, the latter can be made of a metallic material, in particular aluminum or aluminum alloy. This is called a brazed 1 heat exchanger.
  • the spacers 6 have corrugations 60 extending in the length direction of the tubes 2.
  • the length of the tubes 2 here means the axis connecting the ends of the tubes 2 on which the tubes are fixed.
  • collectors 3 The corrugations 60 comprise ridges 61 (visible in Figures 3 and 4) in contact with the tubes 2, more precisely with the flat surfaces of the tubes 2, and of the sidewalls 62 (visible in FIGS. 3 and 4) connecting said ridges 61.
  • These ridges 61 and these sidewalls 62 are arranged perpendicular to the axis of the length of the tubes 2.
  • the spacers 6 include in particular a first portion 6A and a second portion 6B.
  • the first portion 6A is disposed upstream of the second portion 6B in the direction of passage of the second heat transfer fluid represented by an arrow 100 in FIG. 2.
  • the first portion 6A protrudes from the tubes 2, more particularly from the front section of the tubes 2
  • the term “front edge of the tubes 2” here means the edge of the tubes 2 which faces the flow of the second heat transfer fluid.
  • the second portion 6B stops at the rear edge of the tubes 2.
  • the rear edge of the tubes 2 here means the edge of the tubes 2 opposite the front edge.
  • the ridges 61 of the first portion 6A have a profile having a flat 64 and the ridges 61 of the second portion 6B have a rounded profile 65 so that the corrugations 60 have a sinusoidal profile.
  • first portion 6A of the spacers 6 protrudes from the front edge of the tubes 2 and that its ridges 61 include a flat 64 makes it possible to prevent the formation of frost.
  • the ridges 61 with a flat 64 together with the protrusion allow better evacuation of the water condensates on the front face of the heat exchanger 1, that is to say the face of the heat exchanger. heat through which the second coolant enters. Frost is therefore less likely to form.
  • the second portion 6B can in particular extend over 100% to 66% of the width of the tubes 2.
  • width is meant here the distance between the front edge and the rear edge of the tubes 2.
  • the first portion 6A preferably comprises smooth sides 62. These smooth sides 62 also allow good evacuation of condensates.
  • the second portion 6B may for its part include louvers 63 on its sides 62.
  • louver 63 is meant here a deflecting wall integral with the side 62, inclined relative to said side 62 and projecting on either side. of the sidewall 62. Said deflector wall defines an opening on either side of the sidewall 62 so that the second heat transfer fluid can pass from one side of the sidewall 62 to the other.
  • louvers 63 of the same side 62 can all be oriented in the same direction. By this is meant that their openings on the same side of the same flank 62 all face in the same direction. Such an arrangement allows good mixing of the second heat transfer fluid and improves heat exchange.
  • the same side 62 of corrugations 60 may include louvers 63 oriented in different directions.
  • the same sidewall 62 has on the same side a first series of louvers 63 oriented towards the front edge of the tubes 2 and a second series of louvers 63 oriented towards the rear edge of the tubes 2.
  • the louvers 63 of the two sides 62 can be oriented identically. It is also possible to imagine that the orientation of the louvers 63 is reversed from one side 62 to the other.
  • the first 6A and second 6B portions are made from two separate parts.
  • the first 6A and second 6B portions then correspond to two corrugated strips arranged side by side in the direction of the length of the tubes 2.
  • the corrugations 60 having ridges 61 with flats 64 are more difficult to produce than the corrugations 60 comprising ridges 61 with a rounded profile 65 and it is more difficult to control the pitch of the corrugations 60. Thus, it is possible to limit these corrugations. 60 comprising ridges 61 with flats 64 at the first portion 6A to limit the production costs of the heat exchanger 1.
  • the first 6A and second 6B portions are arranged edge to edge and do not fit into each other.
  • the corrugations 60 of the first 6A and second 6B are preferably offset with respect to each other.
  • the pitch of the corrugations 60 of the first portion 6A and the pitch of the corrugations 60 of the second portion 6B can be different. More particularly, the pitch of the corrugations 60 of the first portion 6A can be greater than the pitch of the corrugations 60 of the second portion 6B.
  • the thickness e of the first portion 6A (visible in FIG. 3) can also be greater than the thickness e 'of the second portion 6B (visible in FIG. 4). This also allows the two portions not to fit into each other but it also allows increased protection of the heat exchanger 1 against impacts. Indeed, the fact that the first portion 6 A protrudes from the front section of the tubes 2, the latter is more likely to receive impacts from elements such as chippings, especially if it is an evapo / condenser arranged on the front of the motor vehicle. A thickness e more important thus makes it possible to absorb these shocks more effectively and makes it possible to protect the heat exchanger 1, in particular its tubes 2.
  • first 6A and second 6B portions are separate pieces also makes it possible to vary their shape from each other in order to limit the risk of frost forming.
  • the first portion 6A can extend in a rectilinear profile in the direction of the width of the tubes 2.
  • the first portion 6A can s '' extend according to a corrugated profile in the direction of the width of the tubes 2.
  • the first portion 6A can thus comprise, in the direction of the width of the tubes 2, at least two series of slots 601, 602, 603, 604 offset from one another.
  • the first portion 6A comprises four series of slots 601, 602, 603, 604.
  • the first 6A and second 6B portions of the spacers 6 can thus be produced separately, for example by shaping two separate metal plates by means of rollers having different patterns in order to form distinct ridges 61 between the first 6A and second 6B portion.
  • the two portions 6A, 6B are then placed side by side during the manufacture of the heat exchanger 1 is fixed to the tubes 2, for example by brazing.
  • the first 6A and second 6B portions can be made from the same part.
  • the corrugations 60 of the first 6A and second 6B portions here have a similar pitch and are aligned.
  • the first portion 6A can comprise smooth sidewalls 62 or else corrugated sidewalls 62 as long as at the junction with the second portion 6B the corrugations 60 meet.
  • the first 6A and second 6B portions of the spacers 6 can be produced simultaneously, for example by shaping a metal plate by means of rollers having different patterns in order to form distinct ridges 61 between the first 6A and second 6B portion.

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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)

Abstract

The present invention relates to a heat exchanger (1) comprising a bundle of tubes (2) arranged parallel to one another and inside of which a first heat transfer fluid is intended to circulate, a second fluid being intended to pass through the bundle of tubes (2) between said tubes (2), said bundle of tubes (2) comprising spacers (6) which are disposed between said tubes (2), said spacers (6) having corrugations (60) extending in the longitudinal direction of the tubes (2), said corrugations (60) having ridges (61) in contact with said tubes (2) and sidewalls (62) connecting said ridges (61), the spacers (6) comprising a first portion (6A) and a second portion (6B), the first portion (6A) being arranged upstream of the second portion (6B) in the direction of flow of the second heat transfer fluid, wherein the first portion (6A) protrudes from the front edge of the tubes (2), the ridges (61) of the first portion (6A) having a profile having a flat (64) and the ridges (61) of the second portion (6B) having a rounded profile (65) such that the corrugations (60) have a sinusoidal profile.

Description

Echangeur de chaleur à tubes comportant des intercalaires Tube heat exchanger with spacers
La présente invention concerne un échangeur de chaleur et plus particulièrement un échangeur de chaleur à tubes comportant des intercalaires dans le domaine automobile. Les échangeurs de chaleur à tubes comportent généralement un faisceau de tubes disposés parallèlement les uns aux autres et à l’intérieur desquels circule un premier fluide caloporteur. Un deuxième fluide caloporteur est quant à lui destiné à traverser le faisceau de tubes en passant entre les tubes. Afin d’améliorer les échanges entre les deux fluides caloporteurs, des intercalaires sont disposés entre les tubes dans le passage du deuxième fluide caloporteur. The present invention relates to a heat exchanger and more particularly to a tube heat exchanger comprising spacers in the automotive field. Tube heat exchangers generally have a bundle of tubes arranged parallel to each other and within which circulates a first coolant. A second heat transfer fluid is intended to pass through the tube bundle passing between the tubes. In order to improve the exchanges between the two heat transfer fluids, spacers are placed between the tubes in the passage of the second heat transfer fluid.
Cependant, pour des échangeurs de chaleur tels que des évaporateurs ou évapo/condenseurs, lorsque le premier fluide réfrigérant circulant dans l’échangeur de chaleur est froid et que le deuxième fluide caloporteur est lui aussi froid, il existe un risque de formation de givre sur la surface de l’échangeur de chaleur. La formation de givre diminue la quantité de deuxième fluide caloporteur pouvant traverser l’échangeur de chaleur et ainsi diminue l’efficacité de ce dernier. Un tel phénomène peut notamment se produire au niveau d’un évapo/condenseur placé en face avant du véhicule automobile lorsque ce dernier est utilisé au sein d’une pompe à chaleur. However, for heat exchangers such as evaporators or evapo / condensers, when the first refrigerant circulating in the heat exchanger is cold and the second coolant is also cold, there is a risk of frost forming on the heat exchanger. the surface of the heat exchanger. The formation of frost decreases the amount of second coolant that can pass through the heat exchanger and thus decreases the efficiency of the latter. Such a phenomenon can occur in particular at an evapo / condenser placed on the front face of the motor vehicle when the latter is used in a heat pump.
Une solution connue est de faire circuler périodiquement du premier fluide caloporteur chaud au sein des tubes de l’échangeur de chaleur afin de faire fondre l’éventuel givre. Cependant, cette solution peut ne pas être adaptée car elle oblige d’interrompre temporairement le mode de fonctionnement utilisé. Cela implique alors une diminution du confort des passagers. One known solution is to periodically circulate the first hot coolant fluid within the tubes of the heat exchanger in order to melt any frost. However, this solution may not be suitable because it requires temporarily interrupting the operating mode used. This then implies a reduction in passenger comfort.
Un des buts de la présente invention est donc de remédier au moins partiellement aux inconvénients de l’art antérieur et de proposer un échangeur de chaleur amélioré dont les risques de formation de givre à sa surface sont diminués. One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to provide an improved heat exchanger in which the risks of frost formation on its surface are reduced.
La présente invention concerne donc un échangeur de chaleur comportant un faisceau de tubes disposés parallèlement les uns des autres et à l’intérieur desquels est destiné à circuler un premier fluide caloporteur, un deuxième fluide étant destiné à traverser le faisceau de tubes entre lesdits tubes, ledit faisceau de tubes comportant des intercalaires disposés entre lesdits tubes, lesdits intercalaires comportant des ondulations s’étendant dans le sens de la longueur des tubes, lesdites ondulations comportant des crêtes en contact avec lesdits tubes et des flancs reliant lesdites crêtes, les intercalaires comportant une première portion et une deuxième portion, la première portion étant disposée en amont de la deuxième portion dans le sens de traversée du deuxième fluide caloporteur, la première portion dépassant de la tranche avant des tubes, les crêtes de la première portion ayant un profil présentant un méplat et les crêtes de la deuxième portion ayant un profil arrondi de sorte que les ondulations aient un profil sinusoïdal. The present invention therefore relates to a heat exchanger comprising a bundle of tubes arranged parallel to each other and inside which a first heat transfer fluid is intended to circulate, a second fluid being intended to pass through the bundle of tubes between said tubes, said bundle of tubes comprising spacers disposed between said tubes, said spacers comprising corrugations extending in the direction of the length of the tubes, said corrugations comprising ridges in contact with said tubes and sidewalls connecting said ridges, the spacers comprising a first portion and a second portion, the first portion being disposed upstream of the second portion in the direction of passage of the second heat transfer fluid, the first portion protruding from the portion before the tubes, the ridges of the first portion having a profile having a flat and the ridges of the second portion having a rounded profile so that the corrugations have a sinusoidal profile.
Le fait que la première portion des intercalaires dépasse de la tranche avant des tubes et que ses crêtes comportent un méplat permet une prévention de la formation de givre. En effet, les crêtes avec un méplat conjointement avec le dépassement, permettent une meilleure évacuation des condensais d’eau sur la face avant de l’échangeur de chaleur, c’est-à-dire la face de l’échangeur de chaleur par laquelle le deuxième fluide caloporteur entre. Le givre est donc moins susceptible de ce former. The fact that the first portion of the spacers protrudes from the front edge of the tubes and that its ridges have a flat surface makes it possible to prevent the formation of frost. Indeed, the ridges with a flat part together with the protrusion, allow better evacuation of water condensates on the front face of the heat exchanger, that is to say the face of the heat exchanger through which the second heat transfer fluid enters. Frost is therefore less likely to form.
Selon un aspect de l’invention, la deuxième portion s’étend sur 100 % à 66 % de la largeur des tubes. According to one aspect of the invention, the second portion extends from 100% to 66% of the width of the tubes.
Selon un autre aspect de l’invention, les première et deuxième portions sont réalisées à partir d’une même pièce. According to another aspect of the invention, the first and second portions are made from the same part.
Selon un autre aspect de l’invention, les première et deuxième portions sont réalisées à partir de deux pièces distinctes. According to another aspect of the invention, the first and second portions are made from two separate pieces.
Selon un autre aspect de l’invention, le pas des ondulations de la première portion et le pas des ondulations de la deuxième portion sont différents. According to another aspect of the invention, the pitch of the corrugations of the first portion and the pitch of the corrugations of the second portion are different.
Selon un autre aspect de l’invention, le pas des ondulations de la première portion est supérieure au pas des ondulations de la deuxième portion. According to another aspect of the invention, the pitch of the corrugations of the first portion is greater than the pitch of the corrugations of the second portion.
Selon un autre aspect de l’invention, l’épaisseur de la première portion est supérieure à l’épaisseur de la deuxième portion. According to another aspect of the invention, the thickness of the first portion is greater than the thickness of the second portion.
Selon un autre aspect de l’invention, la première portion comporte, dans le sens de la largeur des tubes, au moins deux séries de créneaux décalées l’une par rapport à l’autre. Selon un autre aspect de l’invention, la première portion s’étend selon un profil rectiligne dans le sens de la largeur des tubes. According to another aspect of the invention, the first portion comprises, in the direction of the width of the tubes, at least two series of slots offset from one another. According to another aspect of the invention, the first portion extends in a rectilinear profile in the direction of the width of the tubes.
Selon un autre aspect de l’invention, la première portion s’étend selon un profil ondulé dans le sens de la largeur des tubes. According to another aspect of the invention, the first portion extends in a corrugated profile in the direction of the width of the tubes.
D'autres caractéristiques et avantages de l'invention apparaîtront plus clairement à la lecture de la description suivante, donnée à titre d'exemple illustratif et non limitatif, et des dessins annexés parmi lesquels : Other characteristics and advantages of the invention will emerge more clearly on reading the following description, given by way of illustrative and non-limiting example, and the appended drawings, among which:
[Fig 1] La figure 1 est une représentation schématique d’un échangeur de chaleur, [Fig 2] la figure 2 est une représentation schématique partielle en perspective d’un faisceau de tubes d’un échangeur de chaleur, [Fig 1] Figure 1 is a schematic representation of a heat exchanger, [Fig 2] FIG. 2 is a partial schematic representation in perspective of a bundle of tubes of a heat exchanger,
[Fig 3] la figure 3 est une représentation schématique partielle en coupe d’une première portion d’intercalaire, [Fig 3] Figure 3 is a partial schematic sectional representation of a first insert portion,
[Fig 4] la figure 4 est une représentation schématique partielle en coupe d’une deuxième portion d’intercalaire, [Fig 4] Figure 4 is a partial schematic sectional representation of a second insert portion,
[Fig 5] la figure 5 est une représentation schématique partielle en perspective d’un intercalaire selon un premier mode de réalisation, [Fig 5] Figure 5 is a partial schematic representation in perspective of a spacer according to a first embodiment,
[Fig 6] la figure 6 est une représentation schématique partielle en perspective d’un intercalaire selon un deuxième mode de réalisation, [Fig 6] Figure 6 is a partial schematic representation in perspective of a spacer according to a second embodiment,
[Fig 7] la figure 7 est une représentation schématique partielle en perspective d’un intercalaire selon un troisième mode de réalisation, [Fig 7] Figure 7 is a partial schematic representation in perspective of a spacer according to a third embodiment,
[Fig 8] la figure 8 est une représentation schématique partielle en perspective d’un intercalaire selon un quatrième mode de réalisation. [Fig 8] Figure 8 is a partial schematic representation in perspective of a spacer according to a fourth embodiment.
Sur les différentes figures, les éléments identiques portent les mêmes numéros de référence. In the various figures, identical elements bear the same reference numbers.
Les réalisations suivantes sont des exemples. Bien que la description se réfère à un ou plusieurs modes de réalisation, ceci ne signifie pas nécessairement que chaque référence concerne le même mode de réalisation, ou que les caractéristiques s'appliquent seulement à un seul mode de réalisation. De simples caractéristiques de différents modes de réalisation peuvent également être combinées et/ou interchangées pour fournir d'autres réalisations. The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to one embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.
Dans la présente description, on peut indexer certains éléments ou paramètres, comme par exemple premier élément ou deuxième élément ainsi que premier paramètre et second paramètre ou encore premier critère et deuxième critère, etc. Dans ce cas, il s’agit d’un simple indexage pour différencier et dénommer des éléments ou paramètres ou critères proches, mais non identiques. Cette indexation n’implique pas une priorité d’un élément, paramètre ou critère par rapport à un autre et on peut aisément interchanger de telles dénominations sans sortir du cadre de la présente description. In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name similar elements or parameters or criteria, but not identical. This indexing does not imply a priority of one element, parameter or criterion over another and such names can easily be interchanged without departing from the scope of the present description.
Dans la présente description, on entend par « placé en amont » qu’un élément est placé avant un autre par rapport au sens de circulation d'un fluide. A contrario, on entend par « placé en aval » qu’un élément est placé après un autre par rapport au sens de circulation du fluide. La figure 1 montre un échangeur de chaleur 1, généralement de forme parallélépipédique, comprenant un faisceau formé d'une multitude de tubes 2 à l'intérieur desquels est destiné à circuler un premier fluide caloporteur, par exemple un fluide réfrigérant circulant dans un circuit de refroidissement inversible. Les tubes 2 sont de section oblongue, définie par un grand axe et un petit axe et sont disposés parallèlement entre eux. Les tubes 2 sont des tubes plats, c’est-à-dire qu’ils présentent deux grands côtés de surface plane et parallèles au grand axe ainsi que deux petits côtés de surface courbe formant la tranche des tubes 2 et reliant les bords des grands côtés. Entre les tubes 2, sont disposés des intercalaires 6 reliant les grands côtés de deux tubes 2 adjacents. Ces intercalaires 6 agissent comme perturbateur et augmentent la surface d'échange thermique avec un deuxième fluide caloporteur destiné à traverser le faisceau de tube 2 en passant entre les tubes 2. Ce deuxième fluide caloporteur peut par exemple être un flux d’air. In the present description, the term “placed upstream” is understood to mean that an element is placed before another with respect to the direction of flow of a fluid. Conversely, the term “placed downstream” is understood to mean that an element is placed after another with respect to the direction of flow of the fluid. Figure 1 shows a heat exchanger 1, generally of parallelepiped shape, comprising a bundle formed by a multitude of tubes 2 inside which is intended to circulate a first coolant, for example a refrigerant circulating in a circuit of reversible cooling. The tubes 2 are of oblong section, defined by a major axis and a minor axis and are arranged parallel to each other. The tubes 2 are flat tubes, that is to say they have two large sides of flat surface and parallel to the large axis as well as two small sides of curved surface forming the edge of the tubes 2 and connecting the edges of the large ones. sides. Between the tubes 2, there are spacers 6 connecting the long sides of two adjacent tubes 2. These spacers 6 act as a disturbance and increase the heat exchange surface with a second heat transfer fluid intended to pass through the tube bundle 2 passing between the tubes 2. This second heat transfer fluid can for example be an air flow.
Les intercalaires 6 sont par exemple des bandes ondulées ou crénelées, placées entre les tubes 2 et fixées auxdits tubes 2. Les tubes 2 et les intercalaires 6 sont généralement réalisés en métal, par exemple en aluminium ou alliage d'aluminium. Les tubes 2 et les intercalaires 6 formant le faisceau sont alors généralement fixés entre eux par brasage. On parle alors de faisceau brasé. The spacers 6 are for example corrugated or crenellated strips, placed between the tubes 2 and fixed to said tubes 2. The tubes 2 and the spacers 6 are generally made of metal, for example aluminum or aluminum alloy. The tubes 2 and the spacers 6 forming the bundle are then generally fixed together by brazing. This is called a brazed bundle.
L'échangeur de chaleur 1 comporte également deux collecteurs 3 ou boites à eau, un collecteur 3 étant disposé à chaque extrémité des tubes 2. Ces collecteurs 3 comportent chacun une plaque collectrice 4 et un couvercle 8 venant recouvrir la plaque collectrice 4 et refermer le collecteur 3. Ces collecteurs 3 permettent la collecte et/ou la distribution du premier fluide caloporteur afin qu'il circule dans les tubes 2. The heat exchanger 1 also comprises two collectors 3 or water boxes, a collector 3 being arranged at each end of the tubes 2. These collectors 3 each comprise a collector plate 4 and a cover 8 covering the collector plate 4 and close the collector 3. These collectors 3 allow the collection and / or distribution of the first heat transfer fluid so that it circulates in the tubes 2.
La plaque collectrice 4 fait la liaison de façon étanche entre le collecteur 3 et le faisceau de tubes 2. De plus, la plaque collectrice 4 peut être de forme générale rectangulaire. La plaque collectrice 4 comporte également une multitude d'orifices ayant une forme correspondant à la forme de la section des tubes 2 et aptes à recevoir les extrémités des tubes 2. Les tubes 2 sont fixés à la plaque collectrice 4 de façon étanche. The collector plate 4 makes the connection in a sealed manner between the collector 3 and the bundle of tubes 2. In addition, the collector plate 4 may be of generally rectangular shape. The collector plate 4 also has a multitude of orifices having a shape corresponding to the shape of the cross section of the tubes 2 and capable of receiving the ends of the tubes 2. The tubes 2 are fixed to the collector plate 4 in a sealed manner.
Les tubes 2, les intercalaires 6 ainsi que les plaques collectrices 4 étant brasés, ces derniers peuvent être réalisés dans un matériau métallique notamment en aluminium ou alliage d'aluminium. On parle alors d’échangeur de chaleur 1 brasé. The tubes 2, the spacers 6 as well as the collector plates 4 being brazed, the latter can be made of a metallic material, in particular aluminum or aluminum alloy. This is called a brazed 1 heat exchanger.
Comme le montre la figure 2, les intercalaires 6 comportent des ondulations 60 s’étendant dans le sens de la longueur des tubes 2. Par longueur des tubes 2, on entend ici l’axe reliant les extrémités des tubes 2 sur lesquelles sont fixés les collecteurs 3. Les ondulations 60 comportent des crêtes 61 (visibles sur les figures 3 et 4) en contact avec les tubes 2, plus précisément avec les surfaces planes des tubes 2, et des flancs 62 (visibles sur les figures 3 et 4) reliant lesdites crêtes 61. Ces crêtes 61 et ces flancs 62 sont disposés perpendiculairement à l’axe de la longueur des tubes 2. As shown in Figure 2, the spacers 6 have corrugations 60 extending in the length direction of the tubes 2. The length of the tubes 2 here means the axis connecting the ends of the tubes 2 on which the tubes are fixed. collectors 3. The corrugations 60 comprise ridges 61 (visible in Figures 3 and 4) in contact with the tubes 2, more precisely with the flat surfaces of the tubes 2, and of the sidewalls 62 (visible in FIGS. 3 and 4) connecting said ridges 61. These ridges 61 and these sidewalls 62 are arranged perpendicular to the axis of the length of the tubes 2.
Les intercalaires 6 comportent notamment, une première portion 6A et une deuxième portion 6B. La première portion 6A est disposée en amont de la deuxième portion 6B dans le sens de traversée du deuxième fluide caloporteur représenté par une flèche 100 sur la figure 2. La première portion 6A dépasse des tubes 2, plus particulièrement de la tranche avant des tubes 2. Par tranche avant des tubes 2, on entend ici la tranche des tubes 2 qui fait face au flux du deuxième fluide caloporteur. The spacers 6 include in particular a first portion 6A and a second portion 6B. The first portion 6A is disposed upstream of the second portion 6B in the direction of passage of the second heat transfer fluid represented by an arrow 100 in FIG. 2. The first portion 6A protrudes from the tubes 2, more particularly from the front section of the tubes 2 The term “front edge of the tubes 2” here means the edge of the tubes 2 which faces the flow of the second heat transfer fluid.
La deuxième portion 6B s’arrête au niveau de la tranche arrière des tubes 2. Par tranche arrière des tubes 2 on entend ici la tranche des tubes 2 opposée à la tranche avant. Comme le montrent les figures 3 et 4, les crêtes 61 de la première portion 6A ont un profil présentant un méplat 64 et les crêtes 61 de la deuxième portion 6B ont un profil arrondi 65 de sorte que les ondulations 60 aient un profil sinusoïdal. The second portion 6B stops at the rear edge of the tubes 2. The rear edge of the tubes 2 here means the edge of the tubes 2 opposite the front edge. As shown in Figures 3 and 4, the ridges 61 of the first portion 6A have a profile having a flat 64 and the ridges 61 of the second portion 6B have a rounded profile 65 so that the corrugations 60 have a sinusoidal profile.
Le fait que la première portion 6A des intercalaires 6 dépasse de la tranche avant des tubes 2 et que ses crêtes 61 comportent un méplat 64 permet une prévention de la formation de givre. En effet, les crêtes 61 avec un méplat 64 conjointement avec le dépassement, permettent une meilleure évacuation des condensais d’eau sur la face avant de l’échangeur de chaleur 1, c’est-à-dire la face de l’échangeur de chaleur par laquelle le deuxième fluide caloporteur entre. Le givre est donc moins susceptible de ce former.The fact that the first portion 6A of the spacers 6 protrudes from the front edge of the tubes 2 and that its ridges 61 include a flat 64 makes it possible to prevent the formation of frost. Indeed, the ridges 61 with a flat 64 together with the protrusion, allow better evacuation of the water condensates on the front face of the heat exchanger 1, that is to say the face of the heat exchanger. heat through which the second coolant enters. Frost is therefore less likely to form.
La deuxième portion 6B peut notamment s’étendre sur 100 % à 66 % de la largeur des tubes 2. Par largeur on entend ici la distance entre la tranche avant et la tranche arrière des tubes 2. Lorsque la deuxième portion 6B s’étend sur 100 % de cette largeur, la première portion 6A est limitée à la partie de l’intercalaire 6 dépassant des tubes 2.The second portion 6B can in particular extend over 100% to 66% of the width of the tubes 2. By width is meant here the distance between the front edge and the rear edge of the tubes 2. When the second portion 6B extends over 100% of this width, the first portion 6A is limited to the part of the insert 6 protruding from the tubes 2.
La première portion 6A comporte de préférence des flancs 62 lisses. Ces flancs 62 lisses permettent également une bonne évacuation des condensais. La deuxième portion 6B peut quant à elle comporter des persiennes 63 sur ses flancs 62. Par persienne 63, on entend ici une paroi déflectrice venant de matière avec le flanc 62, inclinée par rapport audit flanc 62 et faisant saillie de part et d’autre du flanc 62. Ladite paroi déflectrice définie une ouverture de part et d’autre du flanc 62 de sorte que le deuxième fluide caloporteur puisse passer d’un côté à l’autre du flanc 62. The first portion 6A preferably comprises smooth sides 62. These smooth sides 62 also allow good evacuation of condensates. The second portion 6B may for its part include louvers 63 on its sides 62. By louver 63 is meant here a deflecting wall integral with the side 62, inclined relative to said side 62 and projecting on either side. of the sidewall 62. Said deflector wall defines an opening on either side of the sidewall 62 so that the second heat transfer fluid can pass from one side of the sidewall 62 to the other.
Comme le montre la figure 5, mais également la figure 2, les persiennes 63 d’un même flanc 62 peuvent être orientées toutes dans un même sens. Par cela, on entend que leurs ouvertures d’un même côté d’un même flanc 62 font toutes face dans la même direction. Une telle disposition permet un bon brassage du deuxième fluide caloporteur et améliore les échanges calorifiques. As shown in Figure 5, but also in Figure 2, the louvers 63 of the same side 62 can all be oriented in the same direction. By this is meant that their openings on the same side of the same flank 62 all face in the same direction. Such an arrangement allows good mixing of the second heat transfer fluid and improves heat exchange.
Selon une variante illustrée à la figure 6, un même flanc 62 d’ondulations 60 peut comporter des persiennes 63 orientées dans des sens différents. Dans l’exemple illustré à la figure 6, un même flanc 62 comporte sur un même côté une première série de persiennes 63 orientées vers la tranche avant des tubes 2 et une deuxième série de persiennes 63 orientées vers la tranche arrière des tubes 2. According to a variant illustrated in Figure 6, the same side 62 of corrugations 60 may include louvers 63 oriented in different directions. In the example illustrated in Figure 6, the same sidewall 62 has on the same side a first series of louvers 63 oriented towards the front edge of the tubes 2 and a second series of louvers 63 oriented towards the rear edge of the tubes 2.
Au sein d’une même ondulation 60, les persiennes 63 des deux flancs 62 peuvent être orientées à l’identique. Il est également possible d’imaginer que l’orientation des persiennes 63 soit inversée d’un flanc 62 à l’autre. Within the same corrugation 60, the louvers 63 of the two sides 62 can be oriented identically. It is also possible to imagine that the orientation of the louvers 63 is reversed from one side 62 to the other.
Selon un premier mode de réalisation, illustré notamment aux figures 2, 5 et 6, les première 6 A et deuxième 6B portions sont réalisées à partir de deux pièces distinctes. Les première 6A et deuxième 6B portions correspondent alors à deux bandes ondulées disposées côte-à-côte dans le sens de la longueur des tubes 2. According to a first embodiment, illustrated in particular in Figures 2, 5 and 6, the first 6A and second 6B portions are made from two separate parts. The first 6A and second 6B portions then correspond to two corrugated strips arranged side by side in the direction of the length of the tubes 2.
Les ondulations 60 comportant des crêtes 61 avec méplats 64 sont plus difficiles à produire que les ondulations 60 comportant des crêtes 61 avec un profil arrondi 65 et il est plus difficile de contrôler le pas des ondulations 60. Ainsi, il est possible de limiter ces ondulations 60 comportant des crêtes 61 avec méplats 64 à la première portion 6A pour limiter les coûts de productions de l’échangeur de chaleur 1. The corrugations 60 having ridges 61 with flats 64 are more difficult to produce than the corrugations 60 comprising ridges 61 with a rounded profile 65 and it is more difficult to control the pitch of the corrugations 60. Thus, it is possible to limit these corrugations. 60 comprising ridges 61 with flats 64 at the first portion 6A to limit the production costs of the heat exchanger 1.
De préférence les première 6A et deuxième 6B portions sont disposées bord à bord et ne s’emboîtent pas l’une dans l’autre. Pour cela, les ondulations 60 des première 6A et deuxième 6B sont de préférences décalées les unes par rapport aux autres. Comme visible sur la figure 5, le pas des ondulations 60 de la première portion 6 A et le pas des ondulations 60 de la deuxième portion 6B peuvent être différents. Plus particulièrement, le pas des ondulations 60 de la première portion 6A peut être supérieure au pas des ondulations 60 de la deuxième portion 6B. Preferably the first 6A and second 6B portions are arranged edge to edge and do not fit into each other. For this, the corrugations 60 of the first 6A and second 6B are preferably offset with respect to each other. As can be seen in FIG. 5, the pitch of the corrugations 60 of the first portion 6A and the pitch of the corrugations 60 of the second portion 6B can be different. More particularly, the pitch of the corrugations 60 of the first portion 6A can be greater than the pitch of the corrugations 60 of the second portion 6B.
L’épaisseur e de la première portion 6A (visible figure 3) peut également être supérieure à l’épaisseur e’ de la deuxième portion 6B (visible figure 4). Cela permet également que les deux portions ne s’emboîtent pas l’une dans l’autre mais cela permet également une protection accrue de l’échangeur de chaleur 1 contre les chocs. En effet, du fait que la première portion 6 A dépasse de la tranche avant des tubes 2, cette dernière est plus susceptible de recevoir des chocs d’éléments tels que des gravillons notamment s’il s’agit d’un évapo/condenseur disposé en face avant du véhicule automobile. Une épaisseur e plus important permet ainsi d’absorber plus efficacement ces chocs et permet de protéger l’échangeur de chaleur 1, notamment ses tubes 2. The thickness e of the first portion 6A (visible in FIG. 3) can also be greater than the thickness e 'of the second portion 6B (visible in FIG. 4). This also allows the two portions not to fit into each other but it also allows increased protection of the heat exchanger 1 against impacts. Indeed, the fact that the first portion 6 A protrudes from the front section of the tubes 2, the latter is more likely to receive impacts from elements such as chippings, especially if it is an evapo / condenser arranged on the front of the motor vehicle. A thickness e more important thus makes it possible to absorb these shocks more effectively and makes it possible to protect the heat exchanger 1, in particular its tubes 2.
Le fait que les première 6A et deuxième 6B portions soient des pièces distinctes permet également de varier leur forme l’une de l’autre afin de limiter les risques de formation de givre. Ainsi, comme illustré sur les figures 1, 5 et 6, la première portion 6Apeut s’étendre selon un profil rectiligne dans le sens de la largeur des tubes 2. Selon un autre exemple illustré à la figure 7, la première portion 6A peut s’étendre selon un profil ondulé dans le sens de la largeur des tubes 2. The fact that the first 6A and second 6B portions are separate pieces also makes it possible to vary their shape from each other in order to limit the risk of frost forming. Thus, as illustrated in Figures 1, 5 and 6, the first portion 6A can extend in a rectilinear profile in the direction of the width of the tubes 2. According to another example illustrated in Figure 7, the first portion 6A can s '' extend according to a corrugated profile in the direction of the width of the tubes 2.
Il est également possible d’imaginer des premières portions 6A encore plus complexes, comme par exemple tel qu’illustré à la figure 8. La première portion 6A peut ainsi comporter, dans le sens de la largeur des tubes 2, au moins deux séries de créneaux 601, 602, 603, 604 décalées l’une par rapport à l’autre. Dans l’exemple illustré à la figure 8, la première portion 6A comporte quatre séries séries de créneaux 601, 602, 603, 604. It is also possible to imagine even more complex first portions 6A, as for example as illustrated in FIG. 8. The first portion 6A can thus comprise, in the direction of the width of the tubes 2, at least two series of slots 601, 602, 603, 604 offset from one another. In the example illustrated in Figure 8, the first portion 6A comprises four series of slots 601, 602, 603, 604.
Les première 6A et deuxième 6B portions des intercalaires 6 peuvent ainsi être réalisées séparément par exemple par mise en forme de deux plaques métalliques distinctes au moyen de rouleaux présentant des motifs différents afin de former des crêtes 61 distinctes entre la première 6A et deuxième 6B portion. Les deux portions 6A, 6B sont alors disposées côte-à-côte lors de la fabrication de l’échangeur de chaleur 1 est fixées aux tubes 2, par exemple par brasage. The first 6A and second 6B portions of the spacers 6 can thus be produced separately, for example by shaping two separate metal plates by means of rollers having different patterns in order to form distinct ridges 61 between the first 6A and second 6B portion. The two portions 6A, 6B are then placed side by side during the manufacture of the heat exchanger 1 is fixed to the tubes 2, for example by brazing.
Selon un deuxième mode de réalisation non représenté, les première 6A et deuxième 6B portions peuvent être réalisées à partir d’une même pièce. Les ondulations 60 des première 6A et deuxième 6B portions ont ici un pas similaire et sont alignées. La première portion 6Apeut comporter des flancs 62 lisses ou bien des flancs 62 ondulés du moment qu’au niveau de la jonction avec la deuxième portion 6B les ondulations 60 se rejoignent. Toujours selon ce deuxième mode de réalisation, les première 6A et deuxième 6B portions des intercalaires 6 peuvent être réalisées simultanément par exemple par mise en forme d’une plaque métallique au moyen de rouleaux présentant des motifs différents afin de former des crêtes 61 distinctes entre la première 6A et deuxième 6B portion. According to a second embodiment not shown, the first 6A and second 6B portions can be made from the same part. The corrugations 60 of the first 6A and second 6B portions here have a similar pitch and are aligned. The first portion 6A can comprise smooth sidewalls 62 or else corrugated sidewalls 62 as long as at the junction with the second portion 6B the corrugations 60 meet. Still according to this second embodiment, the first 6A and second 6B portions of the spacers 6 can be produced simultaneously, for example by shaping a metal plate by means of rollers having different patterns in order to form distinct ridges 61 between the first 6A and second 6B portion.
Ainsi, on voit bien que l’échangeur de chaleur 1 du fait de la présence de deux portions 6 A, 6B d’intercalaire 6 distinctes, permet de diminuer les risques de formation de givre lors de G utilisation dudit échangeur de chaleur 1. Thus, it is clear that the heat exchanger 1, due to the presence of two separate portions 6 A, 6B of spacer 6, makes it possible to reduce the risks of frost forming when using said heat exchanger 1.

Claims

Revendications Claims
[Revendication 1] Échangeur de chaleur (1) comportant un faisceau de tubes (2) disposés parallèlement les uns des autres et à l’intérieur desquels est destiné à circuler un premier fluide caloporteur, un deuxième fluide étant destiné à traverser le faisceau de tubes (2) entre lesdits tubes (2), ledit faisceau de tubes (2) comportant des intercalaires (6) disposés entre lesdits tubes (2), lesdits intercalaires (6) comportant des ondulations (60) s’étendant dans le sens de la longueur des tubes (2), lesdites ondulations (60) comportant des crêtes (61) en contact avec lesdits tubes (2) et des flancs (62) reliant lesdites crêtes (61), caractérisé en ce que les intercalaires (6) comportent une première portion (6A) et une deuxième portion (6B), la première portion (6A) étant disposée en amont de la deuxième portion (6B) dans le sens de traversée du deuxième fluide caloporteur, la première portion (6A) dépassant de la tranche avant des tubes (2), les crêtes (61) de la première portion (6 A) ayant un profil présentant un méplat (64) et les crêtes (61) de la deuxième portion (6B) ayant un profil arrondi (65) de sorte que les ondulations (60) aient un profil sinusoïdal. [Claim 1] Heat exchanger (1) comprising a bundle of tubes (2) arranged parallel to each other and inside which a first heat transfer fluid is intended to circulate, a second fluid being intended to pass through the bundle of tubes (2) between said tubes (2), said bundle of tubes (2) comprising spacers (6) arranged between said tubes (2), said spacers (6) comprising corrugations (60) extending in the direction of the length of the tubes (2), said corrugations (60) comprising ridges (61) in contact with said tubes (2) and flanks (62) connecting said ridges (61), characterized in that the spacers (6) comprise a first portion (6A) and a second portion (6B), the first portion (6A) being arranged upstream of the second portion (6B) in the direction of passage of the second heat transfer fluid, the first portion (6A) projecting from the section before the tubes (2), the ridges (61) of the first portion (6 A) having a profile having a flat (64) and the ridges (61) of the second portion (6B) having a rounded profile (65) so that the corrugations (60) have a sinusoidal profile.
[Revendication 2] Échangeur de chaleur (1) selon la revendication 1, caractérisé en ce que la deuxième portion (6B) s’étend sur 100 % à 66 % de la largeur des tubes (2). [Claim 2] A heat exchanger (1) according to claim 1, characterized in that the second portion (6B) extends over 100% to 66% of the width of the tubes (2).
[Revendication 3] Échangeur de chaleur (1) selon l’une quelconque des revendications 1 ou 2, caractérisé en ce que les première (6 A) et deuxième (6B) portions sont réalisées à partir d’une même pièce. [Claim 3] Heat exchanger (1) according to any one of claims 1 or 2, characterized in that the first (6 A) and second (6B) portions are made from the same part.
[Revendication 4] Échangeur de chaleur (1) selon l’une quelconque des revendications 1 ou 2, caractérisé en ce que les première (6 A) et deuxième (6B) portions sont réalisées à partir de deux pièces distinctes. [Claim 4] Heat exchanger (1) according to any one of claims 1 or 2, characterized in that the first (6 A) and second (6B) portions are made from two separate parts.
[Revendication 5] Échangeur de chaleur (1) selon la revendication 4, caractérisé en ce que le pas des ondulations (60) de la première portion (6A) et le pas des ondulations (60) de la deuxième portion (6B) sont différents. [Claim 5] Heat exchanger (1) according to claim 4, characterized in that the pitch of the corrugations (60) of the first portion (6A) and the pitch of the corrugations (60) of the second portion (6B) are different .
[Revendication 6] Échangeur de chaleur (1) selon la revendication précédente, caractérisé en ce que le pas des ondulations (60) de la première portion (6A) est supérieure au pas des ondulations (60) de la deuxième portion (6B). [Claim 6] Heat exchanger (1) according to the preceding claim, characterized in that the pitch of the corrugations (60) of the first portion (6A) is greater than the pitch of the corrugations (60) of the second portion (6B).
[Revendication 7] Échangeur de chaleur (1) selon l’une quelconque des revendications 4 à 6, caractérisé en ce que l’épaisseur (e) de la première portion (6A) est supérieure à l’épaisseur (e’) de la deuxième portion (6B). [Claim 7] Heat exchanger (1) according to any one of claims 4 to 6, characterized in that the thickness (e) of the first portion (6A) is greater than the thickness (e ') of the second portion (6B).
[Revendication 8] Échangeur de chaleur (1) selon l’une quelconque des revendications 4 à 7, caractérisé en ce que la première portion (6A) comporte, dans le sens de la largeur des tubes (2), au moins deux séries de créneaux (601, 602, 603, 604) décalées l’une par rapport à l’autre. [Claim 8] Heat exchanger (1) according to any one of claims 4 to 7, characterized in that the first portion (6A) comprises, in the width direction of the tubes (2), at least two series of slots (601, 602, 603, 604) offset from one another.
[Revendication 9] Échangeur de chaleur (1) selon l’une quelconque des revendications 1 à 7, caractérisé en ce que la première portion (6A) s’étend selon un profil rectiligne dans le sens de la largeur des tubes (2). [Claim 9] Heat exchanger (1) according to any one of claims 1 to 7, characterized in that the first portion (6A) extends in a rectilinear profile in the direction of the width of the tubes (2).
[Revendication 10] Échangeur de chaleur (1) selon l’une quelconque des revendications 1 à 7, caractérisé en ce que la première portion (6A) s’étend selon un profil ondulé dans le sens de la largeur des tubes (2). [Claim 10] Heat exchanger (1) according to any one of claims 1 to 7, characterized in that the first portion (6A) extends in a corrugated profile in the width direction of the tubes (2).
PCT/FR2020/052481 2020-01-03 2020-12-16 Tube heat exchanger having spacers WO2021136896A1 (en)

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