Heat exchanger tube

Abstract

The invention deals with a heat exchanger tube (1) for use in a heat exchanger tube (1) of a motor vehicle, the heat exchanger tube (1) comprising a pair (2) of plates (3) elongating along a longitudinal plan (A), the pair (2) of plates (3) comprising a first plate (3) and a second plate (4) joined to each other to form an inner area (5) dedicated to refrigerant fluid (RF) circulation and divided in at least six channels (6), at least one channel (6) is defined by a cross section area (S) that has a length (L), at least one of the plate is defined by a thickness (T) measured between an internal wall (7) of the plate and an external wall (8) of the plate opposed to the internal wall (7), wherein said thickness (T) is between 0.190 mm and 0.300 mm and said length (L) is between 2 mm and 5 mm.

Claims

1. A heat exchanger tube for use in a heat exchanger of a motor vehicle, the heat exchanger tube comprising: a pair of plates elongating along a longitudinal plan, the pair of plates comprising a first plate and a second plate joined to each other to form an inner area dedicated to refrigerant fluid circulation and divided in at least six channels, at least one channel is defined by a cross section area delimited by the first plate and the second plate, the cross section area has a length, and at least one of the plates is defined by a thickness, wherein the thickness of each plate is between 0.190 mm and 0.300 mm and the length of the cross section area is between 2 mm and 5 mm, wherein all of the at least six channels have the same cross section area, wherein each plate comprises at least two openings located at a first distal extremity and at least two openings located at a second distal extremity, wherein for each plate, a plurality of straight channels connect the at least two openings at the first distal extremity with the at least two openings at the second distal extremity, and wherein for each plate, the refrigerant fluid is divided into at least three individualized flows in at least three different straight channels.

2. The heat exchanger tube according to claim 1, wherein a length/thickness ratio is in a range of 7.81 to 22.79.

3. The heat exchanger tube according to claim 1, wherein the cross section area of each channel is between 2.76 mm.sup.2 to 6 mm.sup.2.

4. The heat exchanger tube according to claim 2, wherein the cross section area is delimited by a flat portion of the first plate, a flat portion of the second plate, a first pair of ridges and a second pair of ridges, each pair of ridges comprising a ridge of the first plate and a ridge of the second plate, two ridges of a pair being in contact with each other to define a contact zone.

5. The heat exchanger tube according to claim 4, wherein each ridge of the first plate is linked to the flat portion of the first plate by way of a first ridge binding part, and each ridge of the second plate is linked to the flat portion of the second plate by way of a second ridge binding part.

6. The heat exchanger tube according to claim 4, wherein at least one of the contact zones extends throughout a mid-longitudinal plan of the heat exchanger tube.

7. The heat exchanger tube according to claim 4, wherein the thickness is below or equal to a width of the contact zone.

8. The heat exchanger tube according to claim 4, wherein the ridges of a pair of ridges are continuous lines between ridges ends to form each channel.

9. The heat exchanger tube according to claim 7, wherein the inner area is divided in at least six channels, the thickness of the plate is between 0.243 mm and 0.297 mm, the length of the cross section area is between 3.51 mm and 4.29 mm, the width of the contact zone is between 0.54 mm and 1.144 mm, a height of the cross section area is between 1.206 mm and 1.474 mm, and a width of the plate is between 34.2 mm and 41.8 mm.

10. The heat exchanger tube according to claim 9, wherein the inner area is divided in six channels and the ratio is in range of 11.67 to 22.79.

11. The heat exchanger tube according to claim 7, wherein the inner area is divided in at least height channels, the thickness of the plate is between 0.243 mm and 0.297 mm, the length of the cross section area is between 2 mm and 2.849 mm, the width of the contact zone is between 0.45 mm and 0.55 mm, the height of the cross section area is between 1.206 mm and 1.474 mm, and the width of the plate is between 34.2 mm and 41.8 mm.

12. A heat exchanger comprising: a plurality of heat exchanger tubes, each of which comprises: a pair of plates elongating along a longitudinal plan, the pair of plates comprising a first plate and a second plate joined to each other to form an inner area dedicated to refrigerant fluid circulation and divided in at least six channels, at least one channel is defined by a cross section area delimited by the first plate and the second plate, the cross section area has a length, and at least one of the plates is defined by a thickness, wherein the thickness of each plate is between 0.190 mm and 0.300 mm and the length of the cross section area is between 2 mm and 5 mm; wherein all of the at least six channels have the same cross section area, wherein each plate comprises at least two openings located at a first distal extremity and at least two openings located at a second distal extremity, wherein for each plate, a plurality of straight channels connect the at least two openings at the first distal extremity with the at least two openings at the second distal extremity, and wherein for each plate, the refrigerant fluid is divided into at least three individualized flows in at least three different straight channels; and at least one dissipation device being located between two exchanger tubes, the dissipation device being corrugated with a pitch below or equal to 1.4 mm.

Description

(1) Other specificities, details and characteristics of the present invention will be highlighted thanks to the following description, given for general guidance, in relation with the following figures:

(2) FIG. 1 is a general view of a heat exchanger including heat exchanger tubes according to the present invention,

(3) FIG. 2 is an exploded view of a heat exchanger tube according to the present invention, in a first embodiment,

(4) FIG. 3 is a front view of a heat exchanger tube according to the present invention shown in FIG. 2,

(5) FIG. 4 is a transversal section of the heat exchanger tube according to the present invention shown in FIGS. 2 and 3,

(6) FIG. 5 is a front view of a heat exchanger tube according to the present invention, in a second embodiment,

(7) FIG. 6 is a transversal section of the heat exchanger tube according to the present invention shown in FIG. 5.

(8) Concerning dimensions, a length is a dimension measured in a direction where a considered element extends in its biggest way. A width or a height of the considered element are dimensions perpendicular to said length.

(9) Note that features and different embodiments of the invention may be combined with one another in various combinations, as well as they are not incompatible or exclusive to one another. More particularly, it will be possible to imagine variants of the invention comprising only a selection of the features described hereinafter, without the other characteristics described, if said selection of features provides a technical advantage or if it allows to distinguish the invention over the prior art.

(10) In particular, the embodiments described hereafter are combinable if said combination is functional from a technical point of view.

(11) In the following figures, features common to several figures have the same reference.

(12) Starting from FIG. 1, a plurality of heat exchanger tubes 1 of the invention are stacked in-between a plurality of dissipation devices 18. Both heat exchanger tubes 1 and dissipation devices 18 are oriented in parallel, according to a longitudinal plan A of one of the heat exchanger tubes 1.

(13) Heat exchanger tubes 1 and dissipation devices 18 are integrated inside a heat exchanger 19 and alternately staked between two side mounting flanges 20, 21. Theses side mounting flanges 20, 21 also extend in a plan parallel to the longitudinal plan A of one of the heat exchanger tubes 1. Heat exchanger tubes 1 and dissipation devices 18 from a core 47 of the heat exchanger 19, said core 47 being the part which is crossed by an air flow AF and where the refrigerant fluid RF flows.

(14) A first side mounting flange 20 is blind. A second side mounting flange 21, opposed to the first side mounting flange 20 versus the core 47, comprise two mouths 22, 23 at a same distal extremity 24 of the second side mounting flange 21. One mouth is a first mouth 22 that receives an input plug 25, the other mouth is a second mouth 23 that receives an output plug 26. The input plug 25 and the output plug 26 are intended to join the heat exchanger tubes 1 to a refrigerant circuit. The refrigerant fluid RF enter the heat exchanger 19 in liquid form thanks to the input plug 25. The refrigerant fluid RF is progressively vaporized inside heat exchanger tubes 1. The refrigerant fluid RF exit the heat exchanger 19 in gaseous form thanks to the output plug 26.

(15) Each heat exchanger tube 1 has a globally flat shape. This shape optimize the heat exchange between heat exchanger tubes 1 and dissipation devices 18. Indeed, it ensure a good contact between heat exchanger tubes 1 and dissipation devices 18, since heat exchanger tubes 1 also supports the corrugated dissipation devices 18.

(16) In the heat exchanger 19, heat exchange happened between the refrigerant fluid RF and the air flow AF crossing along the dissipation devices 18. The air flow AF licks heat exchanger tubes 1 and dissipation devices 18. The corrugated shape of dissipation devices 18 optimizes the heat transfer from the air flow AF to the refrigerant fluid RF, since it increases considerably heat exchange surfaces comparing to a non-corrugated device.

(17) Circulating through the heat exchanger tubes 1 of the heat exchanger 19 operating as an evaporator, the refrigerant fluid RF collect calories from the air flow AF, and consequently cools this air flow AF down.

(18) FIG. 2 illustrates the heat exchanger tube 1 according to the present invention and two adjacent dissipation devices 18.

(19) The heat exchanger tube 1 has two plates 3, 4, a first plate 3 and a second plate 4, adapted to be joined and brazed. This two plates 3, 4 are constitutive of a pair 2 of plates 3, 4. The first plate 3 and the second plate 4 extend their wider dimension toward a longitudinal axis X of the pair 2 of plates 3, 4. This longitudinal axis X is included in the longitudinal plan A of the heat exchanger tube 1. The first plate 3 and the second plate 4 fit each other. Complementary protrusions 27, 28 extended crosswise the longitudinal plan A of the heat exchanger tube 1.

(20) Each plate 3, 4 is veined with ridges 12, 13 that also extend toward the longitudinal axis X of the pair 2 of plates 3, 4. These ridges 12, 13 are continuous and straight lines. They form a pair 11, 14 of ridges 12, 13 when the first plate 3 and the second plate 4 are assembled one in contact on the other, in order to be brazed.

(21) A plate 3, 4 has at least two openings 29, 30, a first opening 29 and a second opening 30, located at a same first distal extremity 31 of the heat exchanger tube 1. The first opening 29 and the second opening 30 are respectively surrounded by a first collar 32 and a second collar 33, in the manner of an eyelet, both the first collar 32 and the second collar 33 protruding from the longitudinal plan A of the heat exchanger tube 1. A second distal extremity 36 of the heat exchanger tube 1, visible on FIG. 3, comprise a third opening and a fourth opening 38 that are respectively surrounded by a third collar, and a fourth collar.

(22) The first opening 29 and the second opening 30 are dedicated to refrigerant fluid RF circulation in order to connect different pairs 2 of plates 3, 4. For this purpose, the first collar 32 and the second collar 33 of a plate 3, 4 of pair 2 of plates 3, 4 match with the immediate adjacent first collar 32 and second collar 33 of an immediate adjacent plate 2 of another pair 2 of plates 3, 4. Then, first collars 32 and second collars 33 are in contact and brazed to seal an inner area dedicated to refrigerant fluid RF circulation, this inner area being called a collector.

(23) The dissipation device 18 extends it wider dimension toward the longitudinal axis X of the pair 2 of plates 3, 4. Two dissipation devices 18 are distributed one both sides of the heat exchanger tube 1, in order to have a contact area between the plate 2 and the dissipation device 18. This contact area covers almost the entire plate 2, except at the first distal extremity 31 of the heat exchanger tube 1, on order to have, the first opening 29, the second opening 30, the first collar 32 and a second collar 33 free to face the other first opening 29, second opening 30, first collar 32 and second collar 33 of the immediate adjacent plates 2.

(24) The dissipation device 18 is a single component that extends in a plan B parallel to the longitudinal plan A of the heat exchanger tube 1. The dissipation device 18 is regular in shape, with corrugations. The corrugated shape of a dissipation device 18 has periodic corrugation crests 34, 35 and a defined pitch F. Crests 34 face a plate 2 and crests 35 is design to face another plate 2. The periodic corrugation crests 34, 35 are symmetrical in relation to the plan B of the dissipation device 18. The pitch F is the distance between two adjacent corrugation crests 34, 35 on opposite sides of the plan B of the dissipation device 18. In other words, the pitch F is the half of a distance between two adjacent corrugation crests 34 or crest 35, crests 34 or crest 35 considered on the same side of the plan B of the dissipation device 18. The pitch F is measured according to the longitudinal axis X of the pair of plates between two adjacent corrugation crests 34 or crest 35.

(25) FIG. 3 considers a pair 2 of plates 3, 4 of the heat exchanger tube 1 according to the present invention in the first embodiment illustrated in FIG. 2. As a result of the view angle, only one plate 3 of the pair 2 is visible. In this first embodiment, the plate 3 as an inner area 5 divided in six nearly identical straight channels 6. The sense followed by the refrigerant fluid RF is illustrated thanks to arrows.

(26) The heat exchanger tube 1 extends toward the longitudinal axis X of the pair 2 of plate 3, 4. This heat exchanger tube 1 has two distal extremities, the first distal extremity 31, and the second distal extremity 36. Without considering the refrigerant fluid RF circulation, a plate 3 is symmetrical regarding to a plan passing throughout the longitudinal axis X and perpendicular to the longitudinal plan A of the heat exchanger tube 1, apart from a peripheral region 41 of plates 3, 4 that comprises the protrusions 27, 28.

(27) The refrigerant fluid RF goes from first opening 29 and fourth opening 38 to, respectively, third opening 37 and second opening 30. The refrigerant fluid RF uses a straight path: from the first opening 29 to the third opening 37 and from the fourth opening 38 to the second opening 30, the refrigerant fluid RF is divided into three individualized flows, in three different channels 6.

(28) The first opening 29, the second opening 30, the third opening 37 and the fourth opening 38 are respectively surrounded by the first collar 32, the second collar 33, the third collar 39, and the fourth collar 40. They are found at each distal extremities: the first opening 29 and the second opening 30 at the first distal extremity 31 of the heat exchanger tube 1, and the third opening 37 and the fourth opening 38 at the second distal extremity 36 of the heat exchanger tube 1. The first opening 29 and the second opening 30 are on each sides of the longitudinal axis X. The third opening 37 and the fourth opening 38 are also on each sides of the longitudinal axis X.

(29) The first opening 29 and the second opening 30, or the third opening 37 and the fourth opening 38 are connected thanks to the straight channels 6. Three channels 6 connect the first opening 29 to the third opening 37. Three channels 6 connect the second opening 30 to the fourth opening 38.

(30) Channels 6 are continuous lines, individualized lengthwise from each other. They are separated thanks to straight and continuous ridges 12. A ridge is larger than other ridges 12, measured in a plan perpendicular to the longitudinal plan A of the heat exchanger tube 1. This large ridge 12 is a ridge 12 named medial ridge 120. The medial ridge 120 is central, located on the longitudinal axis X.

(31) The peripheral region 41 of the first plate 3 and of the second plate 4 of the heat exchanger tube 1 correspond to regions of contact of the first plate 3 with the second plate 4. This region of contact extends partially around the collars 32, 33, 39, 40, and also extend until the medial ridge 120. The peripheral region 41, the region of contact around collars 32, 33, 39, 40, the medial ridge 120 and other ridges 12 intend to be brazed to hermetically close the inner area 5 of the heat exchanger tube 1.

(32) FIG. 4 details the pair 2 of plates 3, 4 of the heat exchanger tube 1 according to the present invention in the first embodiment illustrated in FIG. 3, according to a section view B-B transversally oriented regarding to the longitudinal plan A of the heat exchanger tube 1.

(33) The heat exchanger tube 1 is made of the first plate 3 and of the second plate 4 brazed together. There are different zones of contact of the two plates 3, 4 contact zones 15 defined by a width C and the peripheral region 41 surrounding the pair 2 of plates 3, 4. This width C is measured perpendicularly to the longitudinal axis X, in the longitudinal plan A of the heat exchanger tube 1 at the level of the considered contact zone 15.

(34) Thanks to these zones of contact 15, 41, the heat exchanger tube 1 houses six channels 6. Contact zones 15, 41 extend throughout the longitudinal plan A. More especially, contact zones 15, 41 extend throughout a mid-longitudinal plan M of the heat exchanger tube 1 collocated with the longitudinal plan A. The mid-longitudinal plan M correspond to a longitudinal plan of symmetry of the heat exchanger tube 1, apart from the peripheral region 41 of plates 3, 4 that comprises the protrusions 27, 28.

(35) Each plate 2, 3 has an internal wall 7 and an external wall 8. Internal walls 7 of plates 3, 4 of a pair 2 of plates 3, 4 are face to face to couple their ridges 12, 13, in order to delimit channels 6. Each external walls 8 is dedicated to face a dissipation device 18 to promote thermal conductivity between the pair 2 of plates 3, 4 and the dissipation device 18.

(36) The first plate 3 and the second plate 4 face their internal wall 7, opposed to their external wall 8. Zones of contact 15, 41 are on the internal wall 7 side. The first plate 3 and the second plate 4 are defined by the same thickness T measured between the internal wall 7 of said plate 3, 4 and the external wall 8 of said plate 3, 4. In the example illustrated in FIG. 4, the thickness T is 0.27 mm. Alternately, thickness of the first plate 3 may be different from the thickness of the second plate 4, as long as those thickness respect the range as claimed.

(37) The internal wall 7 delimits the six channels 6. The channel 6 is then defined by a cross section area S delimited by the first plate 3 and the second plate 4. The channel 6 has the same cross section area S lengthwise, at any location of the heat exchanger tube 1.

(38) All six channels 6 are almost identical surrounded by two flared shape ridges 12, 13, except the two channels 6 who are along an edge of the heat exchanger tube 1. These one are surrounded by a flared shape ridge 12, 13 and the peripheral region 41. Accurately, a first pair 11 of ridges 12, 13 and a second pair 14 of ridges 12, 13 surround four of the six channels 6.

(39) A pair 11, 14 of ridges 12, 13 includes a ridge 12 of the first plate 3 matching with a ridge 13 of the second plate 4. All ridges 12, 13 are flared shape, widening from the contact zone 15 to a flat portion 9 of the first plate 3 or a flat portion 10 of the second plate 4.

(40) The medial ridge 120 has a larger width C than other ridges 12. For example, the medial ridge 120 has a width C equal to 1.04 mm, and other ridges 12 have a width C equal to 0.6 mm. A group 42 of three channels 6 are aside the medial ridge 120 on one side of the longitudinal axis X, and another group 43 of three other channels 6 are aside the medial ridge 120 on the other side of the longitudinal axis X. In each channels 6 of any group 42, 43 of three channels 6, refrigerant fluid RF is circulating according to a unique trajectory. If comparing the refrigerant fluid RF trajectory inside the two groups 42, 43 of channels 6, the refrigerant fluid RF is circulating according to opposite trajectories in each group 42, 43.

(41) Individually, for the channels 6 surrounded by two ridges 12, 13, we consider the following. The part of the ridge 12 of the first plate 3 connecting the contact zone 15 to the flat portion 9 of the first plate 3 is a first ridge binding part 16. The part of the ridge 13 of the second plate 4 connecting the contact zone 15 to the flat portion 10 of the second plate 4 is a second ridge binding part 17. In consequence, the said channel 6 is defined by a cross section area S delimited by the first binding part 16 of the first pair 11 of ridges 12, 13 of the first plate 3, the flat portion 9 of the first plate 3, the first ridge binding part 16 of the second pair 14 of ridges 12, 13 of the first plate 3, the second ridge binding part 17 of the first pair 11 of ridges 12, 13 of the second plate 4, the flat portion 10 of the second plate 4 and the second ridge binding part 17 of the second pair 14 of ridges 12, 13 of the second plate 4.

(42) For the channels 6 surrounded by a pair of ridge 11, 14 and the peripheral region 41, we consider the following. The flat portion 9 of the first plate 3 and the flat portion 10 of the second plate 4 of this channel 6 are connected to the pair 11, 14 of ridge 12, 13 as above. The peripheral region 41 of the first plate 3 is linked to the flat portion 9 of the first plate 3 thanks to a first peripheral binding part 44. The peripheral region 41 of the second plate 4 is linked to the flat portion 10 of the second plate 4 thanks to a second peripheral binding part 45. In consequence, one of these channels 6, considered as a first peripheral channel 60, is defined by a cross section area S delimited by the first binding part 16 of the first pair 11 of ridges 12, 13 of the first plate 3, the flat portion 9 of the first plate 3, the first peripheral binding part of 44 the peripheral region 41 of the first plate 3, the second binding part 17 of the first pair 11 of ridges 12, 13 of the second plate 4, the flat portion 10 of the second plate 4 and the second peripheral binding part 45 of the peripheral region 41 of the second plate 4. The other channel 6, considered as a second peripheral channel 61, is defined by a cross section area S delimited by the first peripheral binding part 44 of the peripheral region 41 of the first plate 3, the flat portion 9 of the first plate 3, the first ridge binding part 16 of the second pair 14 of ridges 12, 13 of the first plate 3, the second peripheral binding part 45 of the peripheral region 41 of the second plate 4, the flat portion 10 of the second plate 4 and the second ridge binding part 17 of the second pair 14 of ridges 12, 13 of the second plate 4.

(43) In addition, the cross section area S of a channel has a length L. The length L is measured along the longitudinal axis X of the pair of plates 3, 4 and in the longitudinal plan A of the heat exchanger tube 1 and of a plan passing through flat portion 9, 10 surrounded said channel 6, along a direction parallel to the longitudinal plan. The length L is the length of flat portions 9, 10 between binding parts:between the first peripheral binding part 44 and the first ridge binding part 16 or between the second peripheral binding part 45 and the second ridge binding part 17 or between the first ridge binding part 16 and the second ridge binding part 17. Here, the length L is regular for all channels 6 and is for example equal to 3.9 mm. Then, with a thickness T of 0.27 mm, the length L/thickness T ratio R is 14.44.

(44) The cross section area S of a channel has also a height H. The height H is measured perpendicularly the longitudinal axis X in the plan perpendicular to the longitudinal plan A of the heat exchanger tube 1. The height H is a distance between the two internal walls 7 of a channel 6. Here, the height H is regular for all channels 6 and is for example equal to 1.34 mm.

(45) The peripheral region 41 of both first plate 3 and second plate 4 ends with the complementary protrusions 27, 28. A complementary protrusion 27 of the first plate 3 extended crosswise the longitudinal plan A of the heat exchanger tube 1 in order to border the peripheral region 41 of the second plate 4. A complementary protrusion 28 of the second plate 4 extended crosswise the longitudinal plan A of the heat exchanger tube 1 in order to border the peripheral region 41 of the first plate 3. The complementary protrusion 28 of the second plate 4 extended in an opposed direction compared with the complementary protrusion 27 of the first plate 3.

(46) A width P of the plate is measured according to the longitudinal plan A of the pair 2 of plates 3, 4 and perpendicularly to the longitudinal axis X, between the external wall 8 of the complementary protrusion 27 of the first plate 3 and the external wall 8 of the complementary protrusion 28 of the second plate 4. In the example of FIG. 4, width P is equal to 38 mm.

(47) FIG. 5 shows a plate 3 of a pair 2 of plates 3, 4 of a second embodiment of the invention. In this second embodiment, the plate 3 as a U-shaped inner area 5 divided in height nearly identical straight channels 6 connected two by tow thanks to individual turn portions 46. The sense followed by the refrigerant fluid RF is illustrated thanks to arrows.

(48) Except the number and shape of channels 6 and ridges 12, and the number and position of first openings 29, and second opening 30, the heat exchanger tube 1 describes in FIG. 5 is similar to the one described in FIG. 3. Then, to illustrate the FIG. 5, only differences with FIG. 3 will now be considered. For implementations, the reader has to refer to FIG. 3.

(49) The first openings 29 and second opening 30 are surrounded respectively by the collar 32, 33. Openings 29, 30 are to be founded only at the first distal extremity 31 of the heat exchanger tube 1. There is no other opening, especially at the second distal extremity 36. The first openings 29 and second opening 30 are on each sides of the longitudinal axis X.

(50) Ridges 12 divide the inner area 5 in eight nested parts, each parts having a U-shape. All ridges 12 have also a U-shape in the longitudinal plan A and go from the first opening 29 to the second opening 30, except for the ridge that is central which is straight and end to the second distal extremity 36.

(51) The first openings 29 and second opening 30 are connected thanks to nested parts of the inner area 5. A nested part include two straight channels 6 linked by the turn portion 46. Then, a refrigerant fluid RF uses following U-path: entry thanks to the first opening 29, divided into four individualized flows, a flow goes through a channel 6, a turn portion 46 and another channel 6, before exiting the second opening 30 at the same first distal extremity 31.

(52) Regarding the dimensions, the width P is equal to 38 mm, the thickness T is equal to 0.27 mm and the height H is equal to 1.4 mm. The width C is identical for all ridges and is equal to 0.5 mm.

(53) The length L is variable, and so is the ratio R. The first peripheral channel 60 and the second peripheral channel 61 have both a length L equal to 2.1 mm then the length L/thickness T ratio R is 7.82. Both channels 6 on both sides of the medial ridge 120 have a length L equal to 2.29 mm then the length L/thickness T ratio R is 8.48. And the four other channels 6 have a length L equal to 2.59 mm, then the length L/thickness T ratio R is 9.59.

(54) FIG. 6 details the pair 2 of plates 3, 4 of the heat exchanger tube 1 according to the present invention in the second embodiment illustrated in FIG. 5, according to a section view D-D transversally oriented regarding to the longitudinal plan A of the heat exchanger tube 1.

(55) Except the number of channels 6, height instead of six, and ridges 12, 13, seven instead of five, the heat exchanger tube 1 viewed in cross section describes in FIG. 6 is similar to the one described in FIG. 4. We consider that the width C is almost identical for all pair 11, 14 of ridges 12, 13. Then, to illustrate the FIG. 6 and for implementations, the reader has to refer to FIG. 5.

(56) We understand thanks to the above description, that the present invention proposes a simple design of heat exchanger tube for use in heat exchanger used as evaporator in a motor vehicle. This heat exchanger tube is easily manufactured, at a low cost. It allows good thermal exchange performances and reduce the refrigerant fluid pressure drop thanks to individualized channels constituting the inner. Furthermore, this design is resistant at working pressure and burst pressure, for a long term sustainability. This heat exchanger tube is dedicated to heat exchanger and can be found in a Heating, Ventilation and Air-Conditioning device of the vehicle. This kind of heat exchanger can be easily integrated into vehicle air conditioning systems in order to optimize the heat exchange between the air flow dedicated to the passenger compartment cool down and the refrigerant fluid circulating inside heat exchanger tubes of the invention.

(57) However, the invention is not limited to resources and patterns described and illustrated here. It also include all equivalent resources or patterns and every technical associations including such resources. More particularly, the shape of the heat exchanger tube do not affect the invention, insofar as the heat exchanger tube for use in a motor vehicle, in fine, has the same functionality as describes in this document.