EP2726808B1 - Heat exchanger, housing, and air-conditioning circuit including such an exchanger - Google Patents

Description

The present invention relates to a heat exchanger according to the preamble of claim 1, for example used as a condenser in a ventilation system, heating and / or air conditioning of a passenger compartment of a motor vehicle. Such an exchanger is known from FR-A1-2 803 378 . The invention also relates to a ventilation, heating and / or air conditioning installation box and an air conditioning circuit comprising such a heat exchanger.

• soit à l'aide de deux boîtes collectrices supplémentaires qui reçoivent respectivement les extrémités de la première et de la seconde rangées de tubes, ces boîtes collectrices étant reliées l'une à l'autre, à leurs extrémités longitudinales, par deux conduits de liaison. Cependant, outre sa fragilité manifeste, la liaison des boîtes collectrices supplémentaires est complexe à réaliser et provoque des pertes de charges non négligeables qui perturbent et dégradent l'efficacité de l'échangeur intérieur ;
• soit en cintrant des éléments tubulaires de manière à obtenir, à partir de chaque élément tubulaire, deux tubes dont un appartient à la première rangée et l'autre à la seconde. Cependant, lorsque l'encombrement imposé est réduit, le cintrage des tubes diminue sensiblement la hauteur "utile" du faisceau de tubes, c'est-à-dire la hauteur des tubes dédiée à l'échange de chaleur. Une partie de la hauteur des tubes se trouve en effet sacrifiée au profit du cintrage, ce qui nuit à l'efficacité thermique de l'échangeur intérieur.

By the document EP-1460364 there is known an inner heat exchanger (also called "inner condenser" in English) which comprises a beam with two rows of tubes. For each row of tubes, one end of the tubes is received in a manifold, while the opposite end is connected in fluid communication with one or more tubes of the other row. This fluidic connection can be realized:

• or by means of two additional manifold boxes which respectively receive the ends of the first and second rows of tubes, these manifolds being connected to one another at their longitudinal ends by two connecting ducts. However, in addition to its obvious fragility, the connection of the additional manifolds is complex to achieve and causes significant losses of loads that disturb and degrade the efficiency of the indoor heat exchanger;
• or by bending tubular elements so as to obtain, from each tubular element, two tubes, one of which belongs to the first row and the other to the second row. However, when the imposed space requirement is reduced, the bending of the tubes substantially decreases the "useful" height of the tube bundle, that is to say the height of the tubes dedicated to the heat exchange. Part of the height of the tubes is indeed sacrificed in favor of bending, which affects the thermal efficiency of the inner heat exchanger.

• un compartiment d'entrée de fluide réfrigérant dans lequel débouchent les tubes de la première rangée, ce qui assure une mise en communication fluidique des canaux des tubes de la première rangée ; et
• un compartiment de sortie de fluide réfrigérant, adjacent au compartiment d'entrée, dans lequel débouchent les tubes de la seconde rangée, permettant une mise en communication fluidique des canaux des tubes de la seconde rangée.

In addition, from EP-1298401 there is known a front-end heat exchanger comprising a plurality of tubes - in each of which are formed one or more channels adapted to the circulation of a refrigerant - which are arranged in a bundle in a first and a second row of tubes opposite, and a first and a second manifolds inside which open out the tubes of each of said rows. A first longitudinal separation partition, arranged in the first manifold, divides the latter longitudinally into:

• a refrigerant inlet compartment into which the tubes of the first row open, which ensures a fluidic communication of the channels of the tubes of the first row; and
• a coolant outlet compartment, adjacent to the inlet compartment, into which the tubes of the second row open, allowing a fluidic communication of the channels of the tubes of the second row.

A second longitudinal partition wall, arranged in the second manifold, longitudinally separates the latter into two fluid reversal compartments. The second partition is multi-perforated, so as to put in fluid communication the two turning compartments.

Nevertheless, the reduced section of the perforations of the second partition is at the origin of significant pressure losses, which degrade the efficiency of the heat exchanger. In addition, the plurality of perforations weakens the structure of the second header, thereby affecting the overall strength of the heat exchanger. Consequently, any increase in the number or dimensions of the perforations would further weaken the structure of the exchanger.

The object of the present invention is to remedy these drawbacks and, in particular, to provide a front or inner face heat exchanger with minimal pressure drop and satisfactory thermal performance, and in particular a uniformity of the flow temperature of air at the outlet of the exchanger in the case of an indoor exchanger.

For this purpose, according to the invention, the heat exchanger comprises the features defined in claim 1.

The partitions are transverse in that they extend in a direction perpendicular to a front face of the exchanger, said face receiving the air flow with which the coolant exchange.

Thus, thanks to the invention, the refrigerant fluid for circulation in the heat exchanger is uniformly distributed in the tubes of the first row through the fluid inlet compartment. After passing through the tubes of the first row, the coolant is guided in the tubes of the second row, facing, using the corresponding reversing compartments. Once in the outlet compartment, the refrigerant is discharged outside the heat exchanger. The use of a plurality of reversing compartments makes it possible to improve the distribution of the fluid in the tubes - and thus to improve the efficiency of the exchanger by making the temperature of the air at the outlet of the exchanger uniform, in particular while reducing the pressure losses that could adversely affect the performance of the exchanger, the turning compartments being advantageously dimensioned to reduce as much as possible load losses. In addition, the size of such an exchanger is substantially reduced and the rigidity thereof improved by the presence of a plurality of transverse partitions.

In other words, the invention makes it possible to optimize the thermal performance of the heat exchanger relative to an imposed space requirement, in particular when the heat exchanger must be integrated in a heating, ventilation and / or heating casing. in the latter case, the heat exchanger being an indoor heat exchanger.

Preferably, the inverting compartments have identical dimensions with respect to each other, so that they all accommodate the same number of tubes of the first and second rows. Note that each turning compartment can accommodate one or a plurality of tubes of each of the two rows.

• la première et la seconde boîtes collectrices comportent chacune une plaque de fond, comprenant une pluralité d'orifices recevant les tubes correspondants, et un couvercle rapporté sur ladite plaque de fond ; et
• le couvercle de la première boîte collectrice se présente sous la forme d'une plaque de métal emboutie définissant le compartiment d'entrée et le compartiment de sortie.

In the invention,

• the first and second manifolds each comprise a bottom plate, comprising a plurality of orifices receiving the corresponding tubes, and a lid attached to said bottom plate; and
• the cover of the first manifold is in the form of a stamped metal plate defining the inlet compartment and the outlet compartment.

According to this embodiment, a portion of said metal plate is in sealing contact with the corresponding bottom plate, to form the longitudinal partition wall. Of course, in a variant, the longitudinal separation partition may be separate and independent of the cover and be interposed between the latter and the bottom plate.

Preferably, the contour of each of the orifices of the bottom plate is surmounted by an external collar, that is to say which extends outwardly of an internal volume defined by the manifold, for fixing corresponding tube.

• réduit les perturbations de l'écoulement du fluide réfrigérant en limitant les turbulences ;
• évite l'apparition de pertes de charges et de problèmes d'alimentation des tubes ; et
• permet une réduction des dimensions des boîtes collectrices.

Thus, thanks to the collars, the longitudinal ends of the tubes do not penetrate, or almost no, into the inlet, outlet or overturning compartments, as the case may be, which:

• reduces disturbances of the refrigerant flow by limiting turbulence;
• avoids the appearance of pressure drops and tube feeding problems; and
• allows a reduction of the dimensions of the collector boxes.

• la plaque de fond de la première boîte collectrice comporte deux déformations semi-circulaires disposées respectivement en regard des extrémités longitudinales des compartiments d'entrée et de sortie ; et
• le fond des déformations semi-circulaires est relié à la face de la plaque de fond, tournée vers le couvercle, par une zone intermédiaire de liaison qui présente, en coupe axiale, une courbure prédéterminée comportant un point d'inflexion.

According to the invention:

• the bottom plate of the first collector box comprises two semicircular deformations disposed respectively facing the longitudinal ends of the inlet and outlet compartments; and
• the bottom of the semicircular deformations is connected to the face of the bottom plate, turned towards the cover, by an intermediate connecting zone which has, in axial section, a predetermined curvature comprising a point of inflection.

Thus, such semicircular deformations promote the flow of refrigerant at the inlet / outlet of the first header, preventing the formation of turbulence by detachment of the current lines. In addition, the pressure losses resulting from the geometry of this zone are reduced.

Still according to this embodiment, the lid of the second manifold is in the form of a stamped metal plate defining the flipping compartments.

Advantageously, portions of said metal plate are in sealing contact with the corresponding bottom plate, to form the transverse partition walls. Again, alternatively, the transverse partition walls can be separate and independent of the cover and be interposed between the latter and the bottom plate.

Furthermore, the heat exchanger preferably comprises a refrigerant inlet tubing and a refrigerant outlet tubing in fluid communication with the inlet compartment and the outlet compartment, respectively.

In particular, the inlet and outlet pipes may each comprise a lateral skirt attached to an outer face of the first manifold, which facilitates the pre-assembly before brazing of the heat exchanger, in particular by holding together the bottom plate and the cover of the first collector box.

In addition, the heat exchanger advantageously comprises corrugated spacers arranged such that each spacer is disposed between two adjacent tubes of the first row and extends between the two facing adjacent tubes belonging to the second row.

Preferably, the first and second rows of tubes extend in the vertical direction, so as to minimize the temperature differences of the air output of the heat exchanger. In the case of an indoor exchanger, such an orientation facilitates the evacuation of the water which condenses on an outer face of the tubes. Indeed, the gravity and the vertical character of the tubes when the indoor heat exchanger is installed in the ventilation system facilitates the flow of this water.

Furthermore, the invention also relates to a housing of a ventilation system, heating and / or air conditioning, including a passenger compartment of a motor vehicle, comprising a heat exchanger of the type described above.

The present invention also relates to an air conditioning circuit inside which circulates a refrigerant fluid, comprising at least one compressor, an external heat exchanger, an evaporator and an indoor heat exchanger as detailed above.

• La figure 1 représente, dans une vue schématique en perspective, un exemple de réalisation d'un échangeur de chaleur conforme à la présente invention, une fois assemblé.
• La figure 2 illustre schématiquement, dans une vue en perspective éclatée, l'échangeur de chaleur de la figure 1.
• La figure 3 est une coupe axiale partielle d'une extrémité longitudinale du compartiment d'entrée de l'échangeur de chaleur de la figure 1.

The figures of the appended drawing will make it clear how the invention can be realized. In these figures, identical references designate similar elements.

• The figure 1 represents, in a schematic perspective view, an embodiment of a heat exchanger according to the present invention, once assembled.
• The figure 2 schematically illustrates, in an exploded perspective view, the heat exchanger of the figure 1 .
• The figure 3 is a partial axial section of a longitudinal end of the inlet compartment of the heat exchanger of the figure 1 .

On the figures 1 and 2 an exemplary embodiment of a heat exchanger 1 according to the present invention is shown. In a particular application of the present invention, the heat exchanger 1 is an internal condenser integrated in a motor vehicle air conditioning circuit (not shown in the figures) operating at least in a heat pump mode, the internal condenser being arranged in a housing of the ventilation system, heating and / or air conditioning of the vehicle (not shown).

It will be noted that, alternatively, such a heat exchanger could also be used as a front-end heat exchanger for a vehicle, subject to modifications relating, in particular, to the dimensions of the structure of the exchanger.

As shown in these figures, the heat exchanger 1, which extends over a width l in a longitudinal direction x, a depth p in a transverse direction y perpendicular to the longitudinal direction x, and a height h according to a vertical direction z perpendicular to the longitudinal direction x and to the transverse direction y, comprises a bundle of tubes formed of a plurality of longitudinal tubes 2 - extending in the vertical direction z - within which a cooling fluid can pass which comes from the air conditioning circuit.

It should be noted that the tubes 2 could still be arranged horizontally or at any inclination, the vertical direction being the preferred direction for the indoor exchanger mounted in the housing of the ventilation system of the vehicle. Vertical or horizontal direction of an element, in particular the tubes, is determined with regard to the position that the exchanger can take once installed on the vehicle, such a position that can be evaluated without necessarily arranged the exchanger in the vehicle.

The tubes 2 are distributed in a first row 3A and a second row 3B parallel to each other and arranged one behind the other in the transverse direction y. Thus, each row of tubes 3A, 3B comprises a plurality of tubes 2 regularly distributed in the longitudinal direction x.

The heat exchanger 1 also comprises a first and a second collector boxes 4 and 5 - of elongate shape in the longitudinal direction x - within which open the tubes 2 of each of said rows 3A and 3B. The two longitudinal ends of the tubes 2 are thus received respectively in the first manifold 4 and in the second manifold 5.

The first and second manifolds 4 and 5 each have a bottom plate 6, 7 and a cover 8, 9 attached thereto.

The bottom plate 6, 7 and the cover 8, 9 of each of the manifolds 4, 5 have a rectangular shape and extend, in length, in the longitudinal direction x and, in width, in the transverse direction y.

Each bottom plate 6, 7, formed of metallic material, comprises a plane contact face 6A, 7A - against which is mounted the cover 8, 9 corresponding - which is pierced with a plurality of through holes 10 distributed in a first and a second parallel array extending in the longitudinal direction x.

The section of the orifices 10 corresponds to the external cross section of the tubes 2, so that the longitudinal end of each of the tubes 2 can pass, at least in part, the corresponding orifice 10 of the bottom plate 6, 7.

In addition, the contour of each of the orifices 10 of the bottom plates 6 and 7 is surmounted by an outer collar 11 - whose internal section is substantially identical to that of the orifice 10 that it extends - to ensure a quality fixation of the corresponding tube 2. Each collar 11 extends, in the vertical direction z, outside the corresponding header 4, 5.

In addition, each bottom plate 6, 7 comprises a plurality of attachment tabs 12 - evenly distributed along its side edges - which are folded over the side edges of the lid 8, 9 corresponding.

On the other hand, the cover 8 of the first manifold 4 has first and second longitudinal recesses 13 and 14, otherwise known as longitudinal deformations - parallel to each other - which extend in the longitudinal direction x. The two adjacent recesses 13 and 14 have a cross section of semicircular shape.

The longitudinal recesses 13 and 14 can be made by stamping a metal plate 15 which, when pressed, forms the cover 8 of the first manifold 4.

The first longitudinal recess 13 is separated from the second longitudinal recess 14 by a longitudinal partition 16, extending in the x direction. In particular, this longitudinal partition 16 is formed by a portion of the metal plate 15 kept in sealing contact with the corresponding bottom plate, for example by brazing. In other words, the longitudinal partition wall 16 corresponds to a longitudinal unsworn portion of the metal plate 15, forming the cover 8.

Thus, when the cover 8 of the first manifold 4 is secured to the corresponding bottom plate 6, the first and second longitudinal recesses 13 and 14 define respectively a coolant inlet compartment 17, into which the tubes 2 of the first row 3A, and a coolant outlet compartment 18, adjacent to the inlet compartment 17, into which the tubes 2 of the second row 3B open. In other words, the orifices 10 of the first row of the bottom plate 6 open into the inlet compartment 17, while those of the second row open into the outlet compartment 18.

One of the longitudinal ends of the first and second recesses 13 and 14 is open and opens into one of the longitudinal ends of the cover 8, the opposite longitudinal end being closed by a transverse partition 19 formed by a non-stamped portion of the metal plate 15. sealed contact with the bottom plate 6.

Furthermore, the bottom plate 6 of the first manifold 4 comprises two gutters, otherwise called semicircular deformation 20, respectively arranged facing the longitudinal ends of the inlet and outlet compartments 17 and 18. Each of the semi-circular deformations 20, for example made by stamping the bottom plate 6, extends longitudinally over a reduced portion of the latter and has a cross section of semi-circular shape whose internal diameter is identical to that of the longitudinal recesses 13 and 14.

Thus, when the bottom plate 6 and the cover 8 of the first manifold 4 are joined to each other, the longitudinal recesses 13 and 14 are respectively facing semi-circular deformations 20, so as to delimit an inlet channel 21 or outlet 22 of refrigerant with circular internal and external transverse sections.

In addition, the heat exchanger 1 comprises a coolant inlet pipe 23 and a coolant outlet pipe 24 in fluid communication respectively with the inlet compartment 17 and the outlet compartment 18, in order to allow a free flow of water. connecting the heat exchanger 1 to the refrigerant circuit. The inlet pipes 23 and outlet 24 each comprise a side skirt 23A, 24A attached to an outer face of the inlet channels 21 and outlet 22 of the first manifold 4, at one of its longitudinal ends. It is thus understood that the lateral skirt 23A, 23B has an internal diameter equal to the external diameter of the assembly formed by the longitudinal recess 13, 14 joined or close to the semicircular deformation 20 concerned.

As schematically shows figure 3 the bottom 20A of the semicircular deformations 20 is connected to the face of the bottom plate 6, turned towards the cover 8, by an intermediate connecting zone 20B which has, in axial section, a predetermined curvature comprising a point of inflection O.

On the other hand, the cover 9 of the second manifold 5 has a plurality of identical transversal recesses - parallel to each other - which extend in the transverse direction y. The transverse recesses 25 have a cross section of substantially semicircular shape. They can be made by stamping a metal plate 26 which, when pressed, forms the lid 9 of the second header 5.

In addition, the transverse recesses 25 are separated from each other by transverse partition walls 27, extending in the y direction. In particular, each transverse partition 27 is formed by a portion of the metal plate 26 held in sealing contact with the corresponding bottom plate 7. In other words, the transverse partition walls 27 each correspond to a longitudinal unsworn portion of the metal plate 26 which forms the cover 9.

Once the cover 9 of the second manifold 5 is fixed on the associated bottom plate 7, the transverse recesses 25 define refrigerant flipping compartments 28 into which two tubes 2 of the first row 3A and two tubes 2 open. of the second row 3B. It goes without saying that the number of tubes 2 of the first row 3A and the second row 3B opening in each turnaround compartment 28 may be less than or greater than two.

Each turnaround compartment 28 is devoid of fluid communication with the adjacent turnaround compartment (s) 28.

Thus, each turning compartment 28 puts in fluid communication two tubes 2 of the first row 3A with the two tubes 2 opposite the second row 3B. The section of the turning compartments 28 is advantageously determined so that the pressure drops of the fluid flowing through the heat exchanger 1 are minimized.

Furthermore, the heat exchanger 1 also comprises corrugated spacers 29 formed of a plurality of heat exchange fins. Each corrugated spacer 29 is disposed between two adjacent tubes 2 of the first row 3A and extends between the two adjacent tubes 2 opposite belonging to the second row 3B. A solder contact is maintained between the corrugated insert 29 and the corresponding tubes 2 which frame it to facilitate heat exchange.

By way of exception, the spacers 29 disposed at the ends of the bundle of tubes 2 are in contact with a single tube 2 of the first row 3A and the second row 3B and with an end plate 30 providing a stiffening of the structure of the heat exchanger 1.

Thanks to the invention, the refrigerant circulating in the heat exchanger 1 is uniformly distributed in the tubes 2 of the first row 3A through the inlet compartment 17, after being introduced into it by the inlet manifold 23, as represented symbolically arrow F1.

Once the crossing of the tubes 2 of the first row 3A completed, the coolant is guided in the tubes 2 of the second row 3B through the corresponding turning compartments 28.

The refrigerant then passes through the tubes 2 of the second row 3B to end in the outlet compartment 18 through which it is finally discharged outside the heat exchanger 1, after passing through the outlet pipe 24, as the illustrates the arrow F2.

In other words, according to the invention, the circulation of the refrigerant fluid in the heat exchanger 1 is a two-pass circulation, the first pass corresponding to the crossing of the first row of tube 3A, the second pass corresponding to the passing through the second row 3B, the air symbolically represented by the arrow G traversing in order the second row of tubes 3B and the first row of tubes 3A. Thus, it limits the internal pressure losses, particularly in comparison with a four-pass heat exchanger, while maintaining a uniformity of temperature on the front side of the exchanger which makes it compatible and usable for mounting in a housing of a vehicle ventilation system.

Advantageously, the heat exchanger 1 comprises fastening means (not shown in the figures) which, once the heat exchanger installed in a housing of a ventilation system, heating and / or air conditioning, a vertical holding of his tubes.

Claims (11)

1. Heat exchanger comprising:

   - a plurality of tubes (2), arranged in a first and a second row (3A, 3B), and through which a refrigerant is intended to circulate;

   - a first and a second header tank (4, 5) inside which tanks the tubes (2) of each of the said rows emerge;

   - a longitudinal dividing partition (16) arranged in the first header tank (4) to divide it longitudinally into:

   ▪ a refrigerant inlet compartment (17) into which the tubes of the first row (3A) emerge; and

   ▪ a refrigerant outlet compartment (18) into which the tubes of the second row (3B) emerge,

   - a plurality of transverse dividing partitions (27) arranged in the second header tank (5) to divide it transversely into a plurality of return compartments (28) into which at least one tube of the first row (3A) and one tube of the second row (3B) emerge,

   - the first and second header tanks (4, 5) each comprising a bottom plate (6, 7) comprising a plurality of orifices (10) that accept the corresponding tubes (2), and a cover (8, 9) attached to the said bottom plate, the cover (8) of the first header tank (4) taking the form of a pressed metal plate (15) defining the inlet compartment (17) and the outlet compartment (18),
   characterized in that:

   - the bottom plate (6) of the first header tank (4) comprises two semicircular deformations (20) arranged respectively facing the longitudinal ends of the inlet and outlet compartments (17, 18); and

   - the bottom (20A) of the semicircular deformations is connected to the face (6A) of the bottom plate (6) that faces towards the cover (8) by an intermediate connecting zone (20B) which, in axial section, has a predetermined curvature comprising a point of inflection (0).
2. Heat exchanger according to the preceding claim, in which the return compartments (28) have identical dimensions to one another.
3. Heat exchanger according to either one of Claims 1 and 2, in which a portion of the said metal plate (15) is in sealed contact with the corresponding bottom plate (6) to form the longitudinal dividing partition (16).
4. Heat exchanger according to any one of Claims 1 to 3, in which the contour of each of the orifices (10) in the bottom plate (6, 7) is surmounted by an external collar (11) for securing the corresponding tube (2).
5. Heat exchanger according to Claims 1 to 4, in which the cover (9) of the second header tank (5) takes the form of a pressed metal plate (26) defining the return compartments (28).
6. Heat exchanger according to the preceding claim, in which portions of the said metal plate (26) are in sealed contact with the corresponding bottom plate (7) to form the transverse dividing partitions (27).
7. Heat exchanger according to one of the preceding claims, comprising a refrigerant inlet nozzle (23) and a refrigerant outlet nozzle (24) which are respectively in fluidic communication with the inlet compartment (17) and the outlet compartment (18), the inlet (17) and outlet (18) nozzles each comprising a lateral skirt (23A, 24A) attached to an exterior face of the first header tank (4).
8. Heat exchanger according to one of the preceding claims, comprising corrugated separators (29) arranged in such a way that each separator is intercalated between two adjacent tubes (2) of the first row (3A) and extends between the two adjacent tubes (2) belonging to the second row (3B).
9. Heat exchanger according to one of the preceding claims, in which the tubes of the first and second rows extend in the vertical direction.
10. Housing of a heating, ventilation and/or air conditioning installation for a motor vehicle interior, comprising a heat exchanger (1) as specified in one of Claims 1 to 9.
11. Air conditioning circuit through which there circulates a refrigerant, comprising at least a compressor, an external heat exchanger, an evaporator and an internal heat exchanger (1) as specified in one of Claims 1 to 9.

Images