WO2017072425A1

WO2017072425A1 - Heat exchange bundle for heat exchanger, tube designed for the said exchange bundle and heat exchanger comprising the said heat exchange bundle and/or the said tube

Info

Publication number: WO2017072425A1
Application number: PCT/FR2016/052513
Authority: WO
Inventors: Carlos Martins; Anne-Sylvie Magnier-Cathenod; Samer Saab
Original assignee: Valeo Systemes Thermiques
Priority date: 2015-10-28
Filing date: 2016-09-30
Publication date: 2017-05-04
Also published as: FR3043186B1; FR3043186A1

Abstract

The present invention relates to a heat exchange bundle (3) for a heat exchanger (1) allowing the exchange of heat between a first fluid and a second fluid, comprising a stack of tubes (31), the said stack of tubes comprising a determined quantity of tube levels, in which bundle each tube (31) comprises a plurality of conduits extending in the longitudinal direction of the heat exchange bundle (3) for guiding the said first fluid inside the tube (31) from a first end to a second end of the said tube (31), the stack being designed to guide the second fluid between the adjacent levels of tube (31), each tube (31) comprising a plurality of corrugations between its first end and its second end, the corrugations being essentially mutually parallel or being mutually parallel and in which the tubes (31) are stacked in such a way that the corrugations of each level of tubes form a zig zag comprising at least two legs, extending in the transverse direction of the heat exchange bundle (3).

Description

THERMAL EXCHANGE BEAM FOR A HEAT EXCHANGER,

SUITABLE TUBE FOR THIS EXCHANGE BEAM AND HEAT EXCHANGER COMPRISING SAID THERMAL EXCHANGE BEAM AND / OR

LEDIT TUBE

Field of the invention

The present invention relates to a heat exchange bundle for a heat exchanger for exchanging heat between a first fluid and a second fluid, comprising a stack of tubes, said stack of tubes comprising a determined amount of tube levels.

State of the art

In an air-conditioning system intended for example for a motor vehicle, a refrigerant or refrigerant is used to cool the passenger compartment of said motor vehicle during a cooling cycle. In order to allow condensation of the refrigerant, a given amount of heat is subtracted from said refrigerant when it is in a gaseous state.

In the prior art, it is known to use a heat exchanger to obtain cooling of the refrigerant, said heat exchanger being adapted to allow a heat exchange between the refrigerant and a fluid, such as water, so that to cool said refrigerant.

In order to allow the above-mentioned heat exchange, the heat exchangers of the prior art generally comprise two separate circuits, one for the refrigerant and the other for the suitable fluid for cooling the refrigerant.

Thus, the prior art discloses the use of a heat exchanger comprising a heat exchange bundle, said heat exchange bundle comprising a stack of tubes, each of these tubes being provided with channels. The refrigerant can circulate inside the channels, from a first end to a second end of the channels. The fluid used to cool the refrigerant circulates counter refrigerant flow outside the tubes, from the second end to the first end of the channels, between two adjacent tubes.

According to the prior art, the channels comprise a wall of a thickness determined to withstand the high pressure to which the refrigerant circulating inside said channels (typically greater than 40 bars) is subjected. The heat exchange between the refrigerant and the fluid is carried out through this wall.

A heat exchanger, as known in the prior art and described above, is disclosed in the French patent application FR-A-2923589. More specifically, the heat exchanger described in this document comprises a heat exchange bundle comprising a stack of corrugated tubes.

Today, the operation of heat exchangers is subject to many constraints. Thus, the space available for the insertion of a heat exchanger within a motor vehicle is increasingly restricted. This restricted space can in particular impede the proper functioning of the heat exchanger and represents a significant technical constraint. Therefore, there is a need to develop technical solutions for improving the heat exchange between a first fluid flowing inside a heat exchanger and a second fluid flowing out of said fluid element. the heat exchanger, in order to increase the efficiency of the heat exchange, particularly when this heat exchanger is intended to be installed in a small space, within a motor vehicle.

Object of the invention

The present invention proposes to meet the need mentioned above. For this purpose, the subject of the invention is a heat exchange bundle for a heat exchanger for exchanging heat between a first fluid and a second fluid, comprising a stack of tubes, said stack of tubes comprising a predetermined quantity. of tube levels, wherein each tube comprises a plurality of channels extending in the longitudinal direction of the heat exchange bundle for guiding said first fluid inside the tube of a first end towards a second end of said tube, the stack being adapted to guide the second fluid between the adjacent tube levels, each tube comprising a plurality of corrugations between its first end and its second end, the corrugations being substantially parallel to each other; or parallel to each other, and wherein the tubes are stacked so that the corrugations of each level of tubes form a zigzag comprising at least two strands, extending in the transverse direction of the heat exchange bundle.

According to one embodiment of the invention, a level of tubes, as mentioned above, comprises at least a first tube and at least a second tube, advantageously consisting of a first tube and a second tube, said second tube being adjacent and substantially coplanar, preferably coplanar, to said first tube such that the corrugations of each of said first and second tubes together form said zigzag comprising at least two strands extending in the transverse direction of the heat exchange bundle .

According to one embodiment of the invention, the corrugations form a determined angle with respect to the longitudinal direction of the tube between 40 ^° and 60 ^° , preferably equal to 45 ^° .

According to one embodiment of the invention, the aforesaid zigzag is a two-stranded, V-shaped zigzag. Advantageously, in this embodiment, a level of tubes comprises at least a first tube and at least a second tube, advantageously consists of a first tube and a second tube, said second tube being adjacent and substantially coplanar, preferably coplanar, to said first tube so that the corrugations of each of said first and second tubes together form said two-stranded zigzag, in V-shape, preferably the corrugations of each of said first and second tubes are single strands substantially parallel to each other, or parallel to each other.

According to one embodiment of the invention, the aforesaid zigzag is a three-stranded, N-shaped zigzag. Advantageously, in this embodiment, a level of tubes comprises at least one first tube and at least one second tube. , advantageously consists of a first tube and a second tube, said second tube being adjacent and essentially coplanar, preferably coplanar, to said first tube so that the corrugations of each of said first and second tubes together form said three-strand, N-shaped zigzag, advantageously the corrugations of the first tube being substantially parallel to each other, or parallel to each other, and second tube corrugations being double-stranded, V-shaped zigzags.

According to one embodiment of the invention, the aforesaid zigzag is a four-strand, W-shaped zigzag. Advantageously, in this embodiment, a level of tubes comprises at least one first tube and at least one second tube. advantageously consists of a first tube and a second tube, said second tube being adjacent and substantially coplanar, preferably coplanar, to said first tube so that the corrugations of each of said first and second tubes together form said four-stranded zigzag, W-shaped, preferably the corrugations of each of said first and second tubes being zigzags with two strands, V-shaped.

According to one embodiment of the invention, the width of a tube corresponds to half the width of the heat exchange bundle. According to one embodiment of the invention, the width of a tube corresponds to the width of the heat exchange bundle.

According to one embodiment of the invention, the width of a tube corresponds to the dimension of the projection of a strand of said zigzag on a line parallel to the transverse direction of the heat exchange bundle, that is to say say on a line perpendicular to the longitudinal direction of the heat exchange bundle.

According to one embodiment of the invention, the width of a tube corresponds to the dimension of the projection of two strands of said zigzag on a straight line parallel to the transverse direction of the heat exchange bundle, that is to say on a straight line perpendicular to the longitudinal direction of the heat exchange bundle.

According to one embodiment of the invention, the corrugations of a level of tubes n are oriented in the direction opposite to the direction of the corrugations of the level of tubes immediately higher n + 1 and / or immediately lower n-1 within the stack of tubes.

Another object of the invention relates to a tube adapted for the heat exchange bundle according to the invention, wherein the tube comprises corrugations, extending between a first flat zone, located at one of the two ends of the tube, and a second flat area, located at the opposite end of the tube, the flat areas of the tubes comprising elevations, said elevations being adapted to define a space between a first elevation of a first tube, positioned in a n tube level, and a second elevation of a second tube, positioned in an immediately higher n + 1 or immediately lower n-1 tube level within the stack of tubes.

The invention also relates to a heat exchanger, adapted to be installed in a vehicle such. a motor vehicle, said heat exchanger comprising the heat exchange bundle according to the invention (see above) and / or the tube according to the invention (see also supra). Advantageously, the heat exchange bundle is received in a housing; the wall of said housing located in the immediate vicinity of the upper end of said heat exchange bundle and / or the wall of said housing located in the immediate vicinity of the lower end of said heat exchange bundle being provided with a plurality of undulations. According to a preferred embodiment, the latter have a shape similar to (or identical to) or complementary to the shape of the corrugations of the upper end of said heat exchange bundle and / or of the lower end of said exchange bundle. thermal. This makes it possible to create a sufficiently disturbed flow of the second fluid (coolant) between:

the wall of said housing located in the immediate vicinity of the upper end of said heat exchange bundle and the latter, and / or

the wall of said housing located in the immediate vicinity of the lower end of said heat exchange bundle and the latter, preferably both. Brief description of the drawings

The objects, objects and features of the present invention, as well as its technical advantages, will appear more clearly on reading the present description, with reference to the drawings in which: FIG. 1 represents an assembled and perspective view of a part a heat exchanger according to a first embodiment of the present invention,

FIG. 2 is an exploded view of the heat exchanger shown in FIG. 1, said view making it possible to distinguish the various components of said heat exchanger,

FIG. 3 represents a detailed sectional view of the heat exchanger illustrated in FIGS. 1 and 2;

FIG. 4 represents a perspective view, in detail, of the end of a tube used to form a heat exchange bundle for the heat exchanger which is the subject of FIGS. 1, 2 and 3,

FIG. 5 represents a level of tubes for a heat exchange bundle according to a variant of the first embodiment of the present invention,

FIG. 6 represents a level of tubes for an additional variant of the first embodiment of the heat exchange bundle according to the present invention,

FIG. 7 is an exploded view of a heat exchanger according to a second embodiment of the present invention, and

FIG. 8 represents a sectional view of one end of the heat exchanger illustrated in FIG. 7.

Detailed Description of the Embodiments

The purpose of the detailed description presented below is to set forth the invention in a sufficiently clear and complete manner but should not be construed as limiting the scope of protection to the particular embodiments described hereinafter. Figure 1 shows a perspective view of a portion of a heat exchanger 1 according to a first embodiment of the present invention. The heat exchanger 1 is particularly suitable for use during a condensation step, during a cooling cycle of an air conditioning system, for example in a motor vehicle. For this purpose, the heat exchanger 1 comprises a condenser adapted to cool a refrigerant, during the cooling cycle during which the refrigerant passes from a gaseous state to a liquid state.

As shown in FIG. 1, the heat exchanger 1 comprises a housing or housing having an upper wall 2, a lower wall (not shown) and two side walls 4, 5. The heat exchanger 1 is adapted to receive the refrigerant in the direction of the arrow 20, at a relatively high temperature and pressure. The heat exchanger 1 comprises a heat exchange bundle comprising a stack of tubes, said tubes comprising a set of channels adapted to guide the refrigerant from a first end to a second end of the tubes. The channels are spaced apart and adapted to withstand the relatively high temperature and pressure of the refrigerant.

One end of the heat exchanger 1 is shown in this figure 1. The fluids present inside said heat exchanger 1 circulate essentially in a longitudinal direction L _1; as shown in Figure 1. The transverse direction of said heat exchanger 1 is indicated using the reference L ₂ .

The heat exchange bundle is shown in detail in FIG. 2. The refrigerant is guided inside the heat exchanger 1 from its inlet to its outlet, in the direction of the arrow 20. In order to cool the refrigerant a cooling liquid, such as water, is introduced into the heat exchanger 1. The coolant circulates outside the tubes 31 and against the current of the coolant, thus allowing a heat exchange between the coolant and the coolant within the heat exchanger 1. Then, the coolant is guided to an outlet 51. The heat exchanger 1 is thus adapted to facilitate the movement of the coolant within the space between the different channels (not visible) used for the circulation of the refrigerant in the tubes 31.

More precisely, FIG. 2, showing an exploded view of the heat exchanger 1 according to FIG. 1, shows the side walls 4, 5, as well as the upper wall 2 of the heat exchanger 1. As shown in this FIG. 2, a heat exchange bundle 3 comprises a stack of tubes 31, each of said tubes 31 being provided with a set of channels or microchannels (not visible). As illustrated in FIG. 2, these tubes 31 are preferably flat tubes that are typically extruded. However, these tubes 31 may be of different shape, depending on the needs and / or technical constraints. The heat exchange bundle 3 is located inside a housing or housing formed by the upper wall 2, the side walls 4, 5 and the bottom wall (not shown). A heat exchange bundle 3 is shown in detail in FIG. 2. This heat exchange bundle 3 comprises a stack of tubes 31. This stack of tubes 31 is obtained by superimposing different levels of tubes 31; each of said tube levels 31 resulting from the adjacent (or even contiguous) and substantially coplanar, or coplanar, positioning of two tubes 31, as shown in this figure 2.

As shown in Figure 2, the ends of the tubes 31 are received in a connecting element 6, which ensures the maintenance of said ends of the tubes 31 and allows to easily position the different tubes 31 with respect to each other, when the assembly of the heat exchanger. The connecting element 6 is connected to an element 7 provided with an opening 71 adapted to receive the refrigerant in the direction indicated by the arrow 20. The refrigerant penetrates inside a given number of channels located in the different tubes 31. Thus, the refrigerant circulates inside said channels. The coolant flows countercurrently between two adjacent tubes 31 or between two levels of tubes (as previously defined and shown in FIG. 2), thus ensuring the exchange of heat between the coolant and the coolant through the wall of said tubes 31. According to the embodiment shown in FIG. 2, each tube 31 is provided with a determined quantity of corrugations. For a better understanding, the reader is invited to refer to FIG. 4, which shows in detail one of the ends of a tube 31.

Referring back to FIG. 2, it can be observed that the corrugations of the tubes 31 are essentially parallel and form a determined angle with the longitudinal direction I_i of the heat exchanger 1 (represented by "dash-dots" on Figure 1). According to one embodiment of the invention, the corrugations form an angle ranging from about 40 ° to about 60 °, preferably from 40 ° to 60 °, with respect to the longitudinal direction 11 of the heat exchanger 1 . According to a particular embodiment of the invention, the angle between the corrugations and the longitudinal direction I_i is approximately 45 °, preferably 45 °. The corrugations of the tubes 31 make it possible to lengthen the path of the refrigerant inside the various channels of each tube 31, from a first end to a second end. Indeed, the outer surface of the tubes 31, available to achieve the exchange of heat exchanged between the coolant and the coolant, is increased by the presence of the corrugations. This results in an increase in the amount of heat exchanged within the heat exchanger 1.

According to the embodiment shown in FIG. 2, the heat exchange bundle 3, comprising a set of tubes 31, is obtained by assembling a determined number of tubes, arranged in tube levels. Each tube level of said heat exchange bundle 3 comprises two tubes 31 adjacent (or contiguous) and substantially coplanar, preferably coplanar.

In the embodiment shown in FIG. 2, the two adjacent tubes 31 (even contiguous) and essentially coplanar, preferably coplanar, forming the same level of tubes are of the same size. In this embodiment, the width of each tube 31 corresponds to half the width of the corresponding level of tubes 31 and, consequently, to half the width of the heat exchange bundle 3 (whose width is determined by the width of the different levels of tubes superimposed on each other). The tubes 31 are positioned in such a way that the corrugations of two adjacent tubes 31 (ie positioned on a same level of tube) form, in combination, a "V" or a "chevron". Within the heat exchange bundle 3 shown in FIG. 2, there is an alternation between the different levels of tubes superimposed on one another: the levels of tubes 31 of rank n (with n being, for example, a odd integer) have a "V" directed in a first direction, whereas the levels of tubes 31 of rank n + 1 (with n being, for example an odd integer) have a "V" directed in a second direction, opposite to the first sense, or vice versa. In other words, if a level of tubes 31 (composed of two adjacent tubes 31 - even contiguous - and coplanar) has "V" corrugations directed in a first direction, the level of tubes 31 situated immediately above ( if it is present) and the level of tubes 31 located immediately below (if it is present) have "V" corrugations directed in a second direction, opposite the first direction. The presence of the various undulations forming, on each level of tubes 31, rafters ("V" shape), ensures a turbulent flow of the coolant. This turbulent flow of the coolant optimizes the contact between the coolant and the outer surface of the various tubes 31, thus improving the heat exchange between the coolant and the coolant.

The combination of the characteristics, described above, concerning the positioning of the various tubes 31 present within the heat exchange bundle 3, ensures an optimal heat exchange between the refrigerant present inside the channels within the tubes 31 and coolant circulating in a direction opposite to the outside of the different tubes 31.

As indicated above, FIG. 3 is a view from above and in section of the heat exchanger 1 according to FIGS. 1 and 2. FIG. 3 shows a level of tubes of the heat exchange bundle 3 comprising a first tube 31 and a second tube 31, adjacent to the first tube 31. The tubes 31 are positioned on the same level of tubes so that their respective undulations form, in combination, a "V" (or a chevron), as described with reference to FIG. 2. The refrigerant, received at the end of the heat exchanger 1, penetrates within said heat exchanger 1 in the direction of the arrow 20. The liquid of cooling is expelled from the heat exchanger 1 through the outlet 51, in the direction of the arrow 21. As shown in FIGS. 2 and 3, in combination with FIG. 1, the upper wall 2 of the heat exchanger 1 comprises a determined quantity of corrugations, each corrugation having a "V" shape or a chevron shape. Thus, the determined amount of coolant, flowing between the upper part of the heat exchanger 3 and the inside of the upper wall 2, also undergoes a turbulent flow, close to or even similar or identical to the flow. turbulent coolant occurring between two levels of tubes 31. This turbulent flow of the coolant allows an optimal heat exchange within the heat exchanger 1 according to the present invention. In other words, the presence of "V" (or "chevron") corrugations on the top wall 2 - and, optimally, on the bottom wall (not visible) - ensures optimal circulation. coolant (through a turbulent flow) at the upper and lower ends of the heat exchange bundle 3. Thus, the circulation of the coolant takes place in a complete channel instead of a half channel as proposed in heat exchangers known from the state of the art.

As indicated above, FIG. 4 shows the end of a tube 31. Said tube 31 comprises undulations 40, positioned substantially parallel and forming a determined angle with the longitudinal direction of the tube 31 (see FIG.

As illustrated in this FIG. 4, the end of said tube 31 is provided with an essentially flat or even flat portion 42. An elevation 44 is present between the essentially flat portion 42 and the edge forming the end of the tube 43. Said Elevation 44 is directed essentially in the transverse direction L ₂ of the tube 31. The tubes 31, as shown in FIG. 4, are particularly suitable for use in pairs, that is to say that a first tube 31, used within a stack of tubes, is oriented in accordance with FIG. FIG. 4 and is positioned on a second tube 31, after this second tube 31 has been rotated by 180 ^° about the longitudinal direction Li (see FIG. 1) from the orientation shown in FIG. in other words, the respective elevations 44 of said first and second tubes 31 are opposite and together define a space adapted to receive the coolant. The set of different spaces created by the superposition tubes, two by two, avoids having to use a collector (also called "collector box") within a heat exchanger comprising said tubes 31. The presence of these different spaces is described below in detail with reference to a second embodiment of the heat exchanger 11 according to the invention.

According to the first embodiment of the heat exchanger according to the invention, represented by FIGS. 1 -3, each level of tubes of the heat exchange bundle 3 is constituted by the assembly of a first and a second tubes 31, the two tubes 31 being adjacent or even contiguous and substantially coplanar, preferably coplanar, as explained above. The possibility of forming a level of tubes, by assembling adjacent or even contiguous and essentially coplanar tubes, preferably coplanar, offers great freedom as to the assembly of the heat exchange bundle 3 in its finished form. Figures 5 and 6 illustrate various options for obtaining a level of tubes within a stack of tubes constituting a heat exchange bundle.

The level of tubes shown in Figure 5 comprises a tube 91 having chevron-shaped corrugations 95 (more particularly inverted "V"). The level of tubes is completed by a tube 31, adjacent to the tube 91 and positioned in such a way that the corrugations 40 of this tube 31 form, with the chevron-shaped corrugations 95 of said tube 91, "zigzags" with three strands, in the form of "N" (abbreviated as "zigzags in" N ""), in which the first strand (in a first direction) and second strand (in a second direction, different from the first direction) are formed by the corrugations in chevron 95 and the third strand is formed, meanwhile, by the corrugations 40 of the tube 31. According to FIG. 6, the third strand of the "N" zigzag (constituted by the undulations 40) is essentially parallel - or even parallel - to the first strand of said "N" zigzag. These "N" zigzags extend in the transverse direction L ₂ (see FIG.

In a similar manner to the previous embodiment, the upper wall 2 of the heat exchanger 1 may comprise a determined amount of undulations, each undulation having an "N" shape. A different configuration of a level of tubes is illustrated in FIG. 6. As for the level of tubes shown in FIG. 5, the level of tube visible in this FIG. 6 comprises a tube 91 having corrugations 95 in the form of a chevron (more especially in inverted "V"). However, the level of tubes is completed not by a tube 31 (as in Figure 5) but by another identical tube 91, the latter being positioned in such a way that the corrugations 95 of the two adjacent tubes 91 together form "zigzags" three-strand, "W" shaped (abbreviated as "W" zigzags). Like the zigzags in "N" of Figure 5, these zigzags in "W" (or in "M", if we observe them "upside down") extend in the transverse direction L ₂ (see figure 1).

In a similar manner to the previous embodiment, the upper wall 2 of the heat exchanger 1 may comprise a determined amount of undulations, each undulation having a shape "W".

FIG. 7 represents a second embodiment of a heat exchanger according to the invention. Thus, the heat exchanger 11 comprises a heat exchange bundle 13 obtained by means of a stack of tubes 31. Each tube 31 is provided with a determined quantity of channels and undulations depending on the length of said tube 31. The heat exchanger 1 1 comprises a housing or housing comprising an upper wall 12, two side walls 14, 15 and a bottom wall 18. The housing contains the heat exchange bundle 13. As shown in FIG. 7, each level of tubes of the stack of tubes 31 forming the heat exchange bundle 13 comprises a single tube 31. The various tubes 31 are stacked upside down on each other, that is to say that one rotates a tube 31 out of two, within the stack, in order to "cross" the ripple lines. of each of the tubes 31. Thus, the corrugations of a first tube 31, in a first direction, are associated with the corrugations of a second tube 31, in a second direction, in order to alternate the direction of the corrugations along the length of said tubes 31. The upper 12 and lower 18 walls are provided with a determined number of corrugations. The flow of the fluid flowing in the space between said upper and lower walls 18 and the heat exchange bundle 13 is disturbed by said undulations by stacking the tubes 31 and the inner surface of the upper walls 12 and lower 18. The fluid, moving between the upper end and the lower end of the exchange beam 13 and the inside of said walls 12 and 18, circulates inside a channel whose walls are provided with corrugations. Thus, the coolant (second fluid) flows turbulently within the heat exchanger January 1, allowing optimal heat exchange.

Advantageously, it is possible to alternate the direction of the corrugations of the upper wall 2 relative to the level of the upper tubes of the stack of tubes 31.

FIG. 8 represents a sectional view of one end of the heat exchanger January 1 according to FIG. 7. More specifically, FIG. 8 shows an assembled view of the heat exchanger January 1. A connecting element 61 receives and maintains a first end of the tubes 31 inside said connecting element 61. The connecting element 61 is connected to a part provided with an opening 71 for receiving the refrigerant in the direction indicated by the arrow 20 and ensuring the penetration of the refrigerant inside the channels (or microchannels) located within tubes 31. With reference to FIGS. 7 and 8, the refrigerant collector boxes are dimensioned to the width of the tubes 31 in order to obtain optimum compactness of the heat exchanger 13. Three combs are then inserted vertically into the arches of the refrigerant collecting boxes. and are intended to strengthen said collector boxes of said refrigerant.

As shown in FIG. 8, the tubes 31, stacked "back-to-back" on each other (see above), comprise, at their end, elevations 44. As explained previously, with reference to FIG. spaces 80 are formed / defined by two opposite elevations 44 of two tubes 31 superimposed one on the other. The plurality of spaces 80 makes it possible to avoid the use of a collector (or manifold) within the heat exchanger 11.

In addition, the presence of the elevations 44 has another advantage, namely that these elevations 44 may, for example, serve as a stop for a folded sheet collector or a fine collector.

As shown in FIG. 7, the corrugations of the various tubes 31 in opposite directions induce points of contact between the different tubes, which can advantageously be used for soldering points between two tubes 31. positioned one on the other in the stack of tubes 31. Said points of contact / brazing between the various tubes 31 have in particular two following technical effects:

- improved heat exchange, and

- Increasing the strength / resistance of the heat exchange bundle.

With reference to FIG. 7, it should be noted that the corrugations in the walls 12, 13 of a heat exchanger 11 may be used, in combination with a heat exchange bundle according to the prior art such as identified in the present description, in particular to improve the operation / efficiency of said heat exchanger. Said corrugations of the upper 12 and lower 18 walls have a positive impact on the circulation at the ends of the heat exchange bundle, thus allowing optimized heat exchange. In addition, with reference to FIG. 8, it should be noted that the elevations 44, forming the spaces 80 between two adjacent tubes (see above), can be used to improve the operation of the heat exchanger according to the art. previous as identified in the present description. The operation of said heat exchanger can indeed be optimized by the presence of said elevations 44. Indeed, the presence of elevations 44, and therefore spaces 80, avoids the use of a collector, which allows, among others, to limit the number of components of the heat exchanger according to the invention and, therefore, to limit the size and cost thereof while maximizing the efficiency of the heat exchange.

In any event, even when the heat exchanger according to the invention is provided with a collector, the spaces 80 formed / defined by the opposing elevations 44 of two neighboring tubes 31 may be advantageous from a point of contact. technical view. Indeed, the elevations 44, forming the spaces 80, can serve as a stop within a folded sheet collector or a fine collector.

Figures 1, 2, 3, 7 and 8 show only one end of the heat exchanger 1, 1 1 according to the present invention. Similarly, the opposite end (not shown) for the heat exchanger 1, 1 1 is essentially in the same form and has the function of creating an outlet for the refrigerant and a inlet for coolant. Particularly advantageously, the various elements shown in FIGS. 1 to 8 are, after assembly, introduced into an oven for undergoing a brazing process, said brazing process allowing said elements to be fastened to each other to produce a heat exchanger 1, 1 1 according to the invention.

The use of two adjacent tubes to create a chevron zigzag with respect to a single tube having the same chevron-shaped zigzag has a technical advantage. It is difficult to get a sharp chevron angle with a single tube. Indeed, the angle of the chevron of a tube will have a rounded appearance. This difficulty disappears with the use of two tubes. The zigzag with a sharp angle between two browns allows a better disruption of the fluid.

Claims

Heat exchange bundle (3) for a heat exchanger (1) for exchanging heat between a first fluid and a second fluid, comprising a stack of tubes (31, 91), said stack of tubes comprising a predetermined quantity of tube levels, wherein each tube (31, 91) comprises a plurality of channels extending in the longitudinal direction i_i of the heat exchange bundle (3) for guiding said first fluid inside the tube (31, 91) from a first end to a second end of said tube (31, 91), the stack being adapted to guide the second fluid between the adjacent tube levels (31, 91), each tube (31, 91) comprising a plurality of corrugations (40, 95) between its first end and its second end, the corrugations (40, 95) being substantially parallel to each other or parallel to each other and wherein the tubes (31, 91) are stacked so that the waves (40, 95) of each level of tubes form a zigzag comprising at least two strands, extending in the transverse direction L ₂ of the heat exchange bundle (3).

A heat exchange bundle (3) according to claim 1, wherein a tube level comprises at least a first tube (31, 91) and at least a second tube (31, 91), preferably consisting of a first tube (31 , 91) and a second tube (31, 91), said second tube (31, 91) being adjacent and substantially coplanar, preferably coplanar, to said first tube (31, 91) so that the corrugations (40, 95) of each of said first and second tubes (31, 91) together form said zigzag comprising at least two strands, extending in the transverse direction L ₂ of the heat exchange bundle (3).

The heat exchange bundle (3) according to claim 1 or 2, wherein said zigzag is a two-strand, V-shaped zigzag.

4. heat exchange bundle (3) according to claim 3, wherein a level of tubes comprises at least a first tube (31) and at least a second tube (31), advantageously consisting of a first tube (31) and a second tube (31), said second tube (31) being adjacent and substantially coplanar, preferably coplanar, to said first tube (31) so that the corrugations (40) of each of said first and second tubes (31) together form said V-shaped, two-strand zigzag, preferably the corrugations (40) of each of said first and second tubes (31) are essentially parallel single strands between them, or parallel to each other.

A heat exchange bundle (3) according to claim 1 or 2, wherein said zigzag is a three-strand, N-shaped zigzag.

A heat exchange bundle (3) according to claim 5, wherein a tube level comprises at least a first tube (31) and at least a second tube (91), preferably consisting of a first tube (31) and a second tube (91), said second tube (91) being adjacent and substantially coplanar, preferably coplanar, to said first tube (31) so that the corrugations (40, 95) of each of said first and second tubes (31, 91) together they form said three-strand, N-shaped zigzag, advantageously the corrugations (40) of the first tube (31) being essentially parallel to each other or parallel to each other, and the corrugations (95) of the second tube ( 91) being double-stranded, V-shaped zigzags.

A heat exchange bundle (3) according to claim 1 or 2, wherein said zigzag is a four-strand, W-shaped zigzag.

A heat exchange bundle (3) according to claim 7, wherein a tube level comprises at least a first tube (91) and at least a second tube (91), preferably consisting of a first tube (91) and a second tube (91), said second tube (91) being adjacent and substantially coplanar, preferably coplanar, to said first tube (91) so that the corrugations (95, 95) of each of said first and second tubes (91, 91) together form said W-shaped four-strand zigzag, preferably the corrugations (95) of each of said first and second tubes (91) being double-stranded, V-shaped zigzags.

Heat exchange bundle (3) according to one of the preceding claims, wherein the width of a tube (31, 91) corresponds to half the width of the heat exchange bundle (3).

10. heat exchange bundle (3) according to one of the preceding claims, wherein the corrugations (40, 95) of a level of tubes n are oriented in the opposite direction of the direction of the corrugations (40, 95) of tube level immediately higher n + 1 and / or immediately lower n-1 within the stack of tubes (31, 91).

1 1. Tube (31, 91) adapted for the heat exchange bundle (3) according to one of the preceding claims, wherein the tube (31, 91) comprises corrugations (40, 95) extending between a first flat zone at one of the two ends of the tube (31, 91), and a second flat area at the opposite end of the tube (31, 91), the flat areas of the tubes (31, 91) including elevations (44). ), said elevations (44) being adapted to define a space (80) between a first elevation (44) of a first tube (31, 91), positioned in a level of tubes n, and a second elevation (44) of a second tube (31, 91) positioned in an immediately higher n + 1 or immediately lower n-1 tube level within the stack of tubes (31, 91).

12. Heat exchanger (1, 1 1) adapted to be installed in a vehicle such as a motor vehicle, said heat exchanger (1, 1 1) comprising the heat exchange bundle (3) according to one of claims 1 to 10 and / or the tube according to claim 1 1.

13. Heat exchanger (1, 1 1) according to claim 12, wherein the heat exchange bundle (3) is received in a housing; the wall of said housing located in the immediate vicinity of the upper end of said heat exchange bundle (3) and / or the wall of said housing located at the immediate vicinity of the lower end of said heat exchange bundle (3) being provided (s) with a plurality of corrugations.