FR3086380A1 - PLATE CONSTITUTING A HEAT EXCHANGER AND HEAT EXCHANGER COMPRISING AT LEAST ONE SUCH PLATE - Google Patents

Abstract

The invention relates to a plate (105) constituting a heat exchanger and intended to delimit at least one channel (111) for circulation of a fluid. The plate (105) comprises a bottom (106) and at least one raised edge (107) which surrounds the bottom (106). The plate (105) comprises at least one opening (110) configured to supply the channel (111) with fluid. The plate (105) is provided with protrusions (112) which with at least the bottom (106) and the raised edge (107) define a passage section (S1, S2) of the fluid in the channel (111). The protrusions (112) are divided into at least a first group (G1) of protrusions (112) which determines a first passage section (S1) of the channel (111) comprising at least one top wall (116) of a protuberance ( 112) of the first group (G1) and a second group (G2) of protuberances (112) which determines a second section (S2) for passage of the channel (111) comprising at least one top wall (116) of a protuberance (112 ) of the second group (G2), the first passage section (S1) being larger than the second passage section (S2).

Description

The present invention relates to the constituent plates of a heat exchanger. It relates to such a plate and a heat exchanger comprising at least one such plate.

In the automotive field, it is common to have to modify a temperature of an element, such as an electric motor, a battery, a device for storing calories and / or frigories or the like. To this end, the motor vehicle is equipped with an installation which includes a coolant circuit inside which a coolant circulates and a coolant circuit inside which a coolant circulates. The refrigerant circuit includes a compressor for compressing the refrigerant, a heat exchanger for cooling the refrigerant at constant pressure, an expansion member to allow expansion of the refrigerant and a heat exchanger which is arranged to allow thermal transfer between the coolant and the heat transfer liquid.

The heat exchanger is an exchanger formed from stacked plates and joined together to form a tube delimiting a circulation channel for the refrigerant or heat transfer liquid. The plate includes at least two openings for supplying the circulation channel with heat-transfer liquid or with refrigerant. The circulation channel provides a passage section for the coolant or coolant which is a surface taken perpendicular to a plane in which the plate extends and perpendicular to an axis of longitudinal extension of the plate.

A first problem lies in a poor distribution of the coolant and / or the heat transfer liquid inside the circulation channel. Such a poor distribution reduces the efficiency of the heat transfer between the refrigerant and the heat transfer liquid.

A second problem resides in too high a speed of circulation of the coolant and / or the heat transfer liquid inside the circulation channel, which also minimizes the heat transfer between the coolant and the heat transfer liquid.

It is known to provide protrusions inside the circulation channel to disturb a flow of the coolant and / or the heat transfer liquid inside the circulation channel. The protrusions arise from a deformation of at least one of the plates.

However, there remains a poor distribution of the coolant and / or the coolant inside the circulation channel as well as a too high speed of circulation of the coolant and / or the coolant inside the circulation channel, at least inside an area of the section for the passage of the coolant and / or the heat transfer liquid inside the circulation channel. Generally, it is observed that a central zone of the heat exchanger and / or of the passage section has its temperature less modified than peripheral zones of the heat exchanger and / or of the passage section. , which should be improved.

An object of the present invention is to provide a plate constituting a heat exchanger which allows optimization of a distribution of the coolant and / or the heat transfer liquid inside the circulation channel that partially delimits the plate.

Another object of the present invention is to provide a plate constituting a heat exchanger which decreases a speed of circulation of the coolant and / or the coolant inside the circulation channel, in a particular zone where the distribution is usually inhomogeneous.

Another object of the present invention is to provide a heat exchanger comprising at least one such plate, the heat exchanger being either a heat exchanger between a refrigerant and a heat transfer liquid, such as a heat exchanger interposed between a coolant circuit and a coolant circuit, a heat exchanger between a coolant and an air flow.

Another object of the present invention is to provide a particular arrangement of the plate, the latter being indifferently constitutive of a heat exchanger, a circulation path of which is arranged in a "U" shape, indifferently for a heat exchanger between a fluid coolant and a heat-transfer liquid and for a heat exchanger between a coolant and an air flow, or else a heat exchanger whose circulation path is arranged in an "I" shape, in particular for a heat exchanger between a coolant and air flow.

A plate of the present invention is a plate constituting a heat exchanger and intended to delimit at least one channel for circulation of a fluid. The plate includes a bottom and at least one raised edge which surrounds the bottom. The plate includes at least one opening configured to supply fluid to the channel. The plate is provided with protuberances which, with at least the bottom and the raised edge, define a section for passage of the fluid in the channel.

According to the present invention, the protuberances are divided into at least a first group of protuberances which determines a first passage section of the channel delimited by at least one top wall of a protuberance of the first group and a second group of protuberances which determines a second passage section of the channel delimited by at least one top wall of a protuberance of the second group, the first passage section being larger than the second passage section.

The plate advantageously includes any one of the following technical characteristics, taken alone or in combination:

- A passage section is a surface which is perpendicular to the bottom and to an axis of longitudinal elongation of the plate, the passage section being delimited at least by the bottom and a raised longitudinal edge of the plate, the passage section being also delimited by a top wall of at least one protuberance, and preferably the top walls of a plurality of protrusions,

- the difference between the first passage section and the second passage section may depend on a different number of protrusions which are nevertheless identical from a dimensional point of view. Since the protuberances of the first group and the protuberances of the second group are identical, the number of protuberances of the first group is less than a number of protuberances of the second group per unit area. In other words, a first density of protuberances of the first group is less than a second density of protuberances of the second group.

This difference may also depend on a dimensional difference of a protuberance of the first group compared to a protuberance of the second group. In such a case, the density of protuberances of the first group of protuberances is equal to the density of protuberances of the second group of protuberances, but the protuberances of the first group occupy a first volume in the channel which is less important than a second occupied volume by the protuberances of the second group,

- in the same group, the protuberances are organized into at least one rectilinear row of protuberances,

- the protuberances of the first group and the protuberances of the second group emerge from the same face from the bottom towards the canal,

the protuberances of the first group and the protuberances of the second group are identical, in particular in shape and / or volume, except for the manufacturing tolerance,

the protuberances of the first group and the protuberances of the second group are different from each other, in particular in shape and / or in volume,

- the protuberances of the same group, regardless of the first group or the second group, are identical in shape and / or volume in particular, except for the manufacturing tolerance,

- the protuberances of the same group, regardless of the first group or the second group, are different from each other, in particular in shape and / or volume,

- the raised edge extends in at least one edge plane which is transverse to a bottom plane in which the bottom extends,

- The raised edge comprises at least two longitudinal raised edges arranged opposite one another and at least two lateral raised edges formed opposite each other, the two edges longitudinal raised and the two raised raised edges together forming a peripheral periphery at the bottom,

the lateral raised edges and the longitudinal raised edges extend inside respective planes which each form with the bottom plane an angle which is between 91 ⁰ and 140 °, preferably between 91 ⁰ and 95 ⁰ ,

the plate is made of a metallic material, for example capable of being pressed to form in particular the protuberances by stamping the plate, the metallic material being chosen from thermally conductive metallic materials, aluminum in particular,

the bottom comprises a rib which is arranged so that the channel has a U-shaped profile,

- the rib is parallel to a direction of elongation of the longitudinal raised edges,

- The rib extends between a first longitudinal end and a second longitudinal end, the first longitudinal end being in contact with the raised edge, and preferably in contact with a first lateral raised edge that comprises the raised edge, the second longitudinal end being located at a first non-zero distance from the raised edge,

- The channel is shaped like a U, the branches of which are parallel to the longitudinal raised edges of the plate and the base of which adjoins a second raised lateral edge which is arranged opposite the longitudinal of the first raised lateral edge,

the rib is formed at equal distance from the two longitudinal raised edges of the plate,

- the rib is offset by a second non-zero distance relative to a median plane of the plate, the median plane being orthogonal to the bottom and parallel to the axis of longitudinal extension of the plate,

- at least two protrusions of the same group of protrusions are aligned along an axis of lateral elongation of the plate which is orthogonal to an axis of longitudinal elongation of the plate,

- the plate includes at least two openings,

- The plate comprises at least four openings, which are distributed two-to-two at each longitudinal end of the plate. Two of these openings are configured to communicate with a first branch of the channel formed on one side of the bottom and the other two openings are configured to communicate with a second branch of the channel formed on another side of the bottom,

- the first branch of the canal and the second branch of the canal are separated by the rib,

- the openings are circular,

the second group of protuberances is formed between an opening and the first group of protuberances,

the plate includes a third group of protuberances which determines a third passage section in the channel, the third passage section being delimited by at least one top wall of a protuberance of the third group, the third passage section being smaller than the first passage section,

the first group of protuberances is arranged between the second group of protuberances and the third group of protuberances,

at least one group from the second group of protuberances or the third group of protuberances is formed at a distance from the opening of between 10% and 25% of a length of the plate,

- the distance is measured between a center of the opening and a barycenter of the protuberances of the same group,

- the length of the plate is measured between the two lateral raised edges of the plate parallel to the longitudinal extension axis of the plate,

- at least any one of a protuberance of the first group of protuberances, of a protuberance of the second group of protuberances and / or of a protuberance of the third group of protuberances has a frustoconical shape.

The present invention also relates to a tube constituting a heat exchanger and intended to delimit at least one fluid circulation channel, the tube comprising at least two plates including a first plate and a second plate delimiting the channel, the first plate comprising a bottom and at least one raised edge which surrounds the bottom, the first plate comprising at least one opening configured to supply the channel with fluid, the first plate being provided with protuberances which, with the second plate, at least the bottom and raised edge of the first plate define a section for the passage of the fluid in the channel, the protuberances being distributed in at least a first group of protuberances which determines a first section for the passage of the channel delimited by at least one top wall of a protuberance of the first group and a second group of protrusions which determines a second passage section of the channel limited by at least one top wall of a protuberance of the second group, the first passage section being larger than the second passage section. The second plate may have the same characteristics as the first plate or may be different.

The present invention also relates to a heat exchanger comprising at least one such plate.

The heat exchanger advantageously comprises at least any one of the following technical characteristics, taken alone or in combination:

the exchanger comprises at least one such tube, and preferably a plurality of such tubes,

- two plates are nested one inside the other and a space, which forms the fluid circulation channel, is formed between the two plates,

- According to an alternative embodiment, at least three plates are nested one inside the other and delimit two by two a first channel and a second channel, the first channel being configured to be used by a heat-transfer liquid while the second channel is configured to be used by a refrigerant,

- The heat exchanger comprises a first circulation path participating in a refrigerant circuit inside which circulates a refrigerant fluid and a second circulation path inside which circulates a heat transfer liquid, the first circulation path and the second circulation path being arranged to allow heat exchange between the refrigerant and the heat transfer liquid. To this end, the bottom comprises a first face bordering the first circulation path and a second face bordering the second circulation path,

- the first circulation path and the second circulation path are arranged in "I",

- the first circulation path and the second circulation path are arranged in a "U" shape,

- the heat transfer fluid circuit comprises a heat exchanger capable of exchanging calories with an element to be cooled and / or heated, such as an electric motor, a battery, a device for storing calories and / or frigories or the like.

Other characteristics, details and advantages of the invention will emerge more clearly on reading the description given below by way of indication in relation to the drawings in which:

- Figure i is a schematic view of an installation comprising at least one heat exchanger according to the invention,

FIG. 2 is a schematic view of a first heat exchanger participating in the installation shown in FIG. i,

FIG. 3 is a partial schematic view of the first heat exchanger illustrated in FIG. 2,

FIG. 4 is a schematic front view of a plate constituting the first heat exchanger illustrated in FIGS. 2 and 3, according to a first alternative embodiment of the plate,

- Figure 5 is a schematic view of a plurality of plates illustrated in Figure 4 assembled to form tubes of the present invention,

FIG. 6 is a cross-sectional view of a tube such as those illustrated in FIG. 5, the section being made through a first group of protuberances that comprises at least one plate constituting the tube,

- Figure 7 is a cross-sectional view of the tube illustrated in Figure 6, the section being formed through a second group of protuberances that comprises at least one constituent plate of the tube, the second group of protuberances being configured in a first form of achievement,

- Figure 8 is a cross-sectional view of the tube illustrated in Figure 6, the section being formed through a second group of protuberances that includes at least one plate constituting the tube, the second group of protuberances being configured in a second form of achievement,

FIG. 9 is a schematic view of a second heat exchanger participating in the installation shown in FIG. 1,

FIG. 10 is a schematic front view of a plate constituting the second heat exchanger illustrated in FIG. 9, according to a second variant embodiment of the plate,

- Figure 11 is a schematic view of a plurality of plates illustrated in Figure 10 assembled to form tubes of the present invention,

FIG. 12 is a cross-sectional view of a tube such as those illustrated in FIG. 11, the section being made through a first group of protuberances which comprises said plate constituting the tube,

- Figure 13 is a cross-sectional view of the tube illustrated in Figure 12, the section being formed through a second group of protuberances that comprises at least one constituent plate of the tube, the second group of protuberances being configured in a first form of achievement,

- Figure 14 is a cross-sectional view of the tube illustrated in Figure 12, the section being formed through a second group of protuberances that comprises at least one plate constituting the tube, the second group of protuberances being configured in a second form of achievement.

It should first be noted that the figures show the invention in detail to implement the invention, said figures can of course be used to better define the invention if necessary.

In FIG. 1, a motor vehicle is equipped with an element 1 which should be cooled or warmed, for example to optimize its operation. Such an element 1 is in particular an electric or thermal motor intended to at least partially propel the motor vehicle, a battery provided for storing electric energy, a device for storing calories and / or frigories or the like. To this end, the motor vehicle is equipped with an installation 2 which comprises a refrigerant fluid circuit 3 inside which a refrigerant fluid 4, carbon dioxide for example or the like circulates, and a coolant circuit 5 to 1 'inside which circulates a heat transfer liquid 6, in particular glycol water or the like. The installation 2 comprises at least one heat exchanger 11, 12 according to the present invention. The installation 2 is described below to better understand the present invention but the characteristics of the installation 2 described are in no way restrictive for the heat exchanger 11, 12 of the present invention. In other words, the installation 2 is likely to have different structural characteristics and / or different operating modes than those described without the heat exchanger 11,12 departing from the rules of the present invention.

The refrigerant circuit 3 comprises a compressor 7 for compressing the refrigerant 4, a refrigerant / outdoor air exchanger 8 for cooling the refrigerant 4 at constant pressure, for example placed on the front face of the motor vehicle, an expansion member 9 to allow expansion of the coolant 4 and a first heat exchanger 11 which is arranged to allow a thermal transfer between the coolant 4 and the heat transfer liquid 6. The coolant circuit 3 comprises a second heat exchanger 12 which is arranged to allow heat transfer between the refrigerant 4 and an air flow 10, the air flow 10 circulating for example inside a pipe 13 of a ventilation, heating and / or air conditioning system , before being delivered inside a passenger compartment of the motor vehicle.

To this end, the element 1 is in relation with a heat exchanger 14, the heat exchanger 14 being able to modify a temperature of the element 1, in particular by direct contact formed between the element 1 and the heat exchanger 14 , the heat exchanger 14 constituting the coolant circuit 5.

The coolant circuit 5 includes a pump 15 for circulating the coolant 6 inside the coolant circuit 5. The coolant circuit 5 includes the first heat exchanger 11 which is also part of the coolant circuit 3. The first heat exchanger 11 comprises at least a first circulation path 21 of the coolant 4 and at least a second circulation path 22 of the heat transfer liquid 6, the first circulation path 21 and the second circulation path 22 being arranged to allow a heat exchange between the refrigerant 4 present inside the first circulation path 21 and the heat transfer liquid 6 present inside the second circulation path 22. Preferably, the first heat exchanger 11 comprises several first traffic lanes 21 and several second traffic lanes 22. A first traffic lane circulation 21 is interposed between two second circulation paths 22, and a second circulation path 22 is interposed between two first circulation paths 21. The first heat exchanger 11 thus comprises an alternation of first circulation paths 21 and second circulation paths traffic 22.

Inside the heat transfer liquid circuit 5, the heat transfer liquid 6 circulates from the pump 15 to the first heat exchanger 11, then circulates inside the first heat exchanger 11 using the second circulation paths 22 to exchange calories with the refrigerant 4 present inside the first circulation paths 21, then returns to the pump 15.

Inside the coolant circuit 3, the coolant 4 flows from the compressor 7 to the coolant / outdoor air exchanger 8, then to the expansion member 9.

According to a first operating mode of the refrigerant circuit 3, the refrigerant 4 then circulates inside the first heat exchanger 11 using the first circulation paths 21 inside which the refrigerant 4 exchanges calories with the heat transfer liquid 6 present inside the second circulation paths 22, then returns to the compressor 7.

According to a second operating mode of the refrigerant circuit 3, the refrigerant 4 circulates inside the second heat exchanger 12 by using circulation paths inside which the refrigerant 4 exchanges calories with the flow d air 10, then returns to compressor 7.

In Figure 2, the first heat exchanger n is generally parallelepiped and includes a cheek 100 which is provided with an intake of the heat transfer liquid ιοί by means of which the heat transfer liquid 6 penetrates inside the first heat exchanger not. The cheek 100 is also provided with an evacuation of the heat transfer liquid 102 by means of which the heat transfer liquid 6 is evacuated from the first heat exchanger 11. The second circulation paths 22 extend between the admission of the heat transfer liquid 101 and the evacuation of the heat-transfer liquid 102. The cheek 100 also includes an intake of the refrigerant fluid 103 by means of which the refrigerant fluid 4 penetrates inside the first heat exchanger 11 and an evacuation of the refrigerant fluid 104 by through which the refrigerant 4 is discharged from the first heat exchanger 11. The first circulation paths 21 extend between the inlet of the refrigerant 103 and the discharge of the refrigerant 104.

In FIG. 3, on which the cheek 100 of the first heat exchanger as well as said inlets 101, 103 and outlets 102, 104 have been removed, the first heat exchanger 11 is a plate exchanger which comprises a plurality of plates 105, such as the plate 105 illustrated in FIG. 4. The plate 105 mainly extends along a longitudinal axis of elongation Ai. The plate 105 comprises a bottom 106 and at least one raised edge 107 which surrounds the bottom 106. In other words, the raised edge 107 is formed at the periphery of the bottom 106 and the raised edge 107 surrounds the bottom 106. It is understood that the plate 105 is arranged in a generally rectangular bath, the bottom of the bath being made up of the bottom 106 and the edges of the bath being made up of the raised edge 107. More particularly, the raised edge 107 comprises two longitudinal raised edges 108a, 108b formed in screws -to each other and two raised side edges 109a, 109b formed opposite one another.

The plate 105 comprises four openings 110, in particular circular, which are distributed in pairs at each longitudinal end of the plate 105, and more particularly at each of the corners of the bottom 106 of the plate 105. Two of these openings 110 are configured to communicate with one of the first circulation paths 21 formed on one side of the bottom 106 and the two other openings 110 are configured to communicate with one of the second circulation paths 22 formed on another side of the bottom 106.

Two of the openings 110 formed at the same longitudinal end of the plate 105 are each surrounded by a collar 120, so that these openings 110 surrounded by this collar 120 extend in a plane offset with respect to a bottom plane P4 in which the bottom 106 is inscribed. The two other openings 110 situated at the other longitudinal end of the plate 105 extend in the bottom plane P ₄ .

Two plates 105 are nested one inside the other and in contact with each other at least via their raised edges 107. In other words, two plates 105 are stacked one above the other. 'other and provide between them a space which forms a channel 111 for circulation of the refrigerant 4 or of the heat transfer liquid 6.

The bottom 106 is provided with a plurality of protrusions 112 which, with at least the bottom 106 and the raised edge 107, define a passage section Si, S2 of the coolant 4 or of the heat transfer liquid 6 in the channel 111, illustrated in the figures. 3 and 4.

The bottom 106 comprises a rib 113 which is arranged so that the channel 111 has a U-shaped profile. The rib 113 is parallel to a direction D of elongation of the raised longitudinal edges 108, the direction D of elongation of the raised longitudinal edges 108 preferably being parallel to the longitudinal elongation axis Ai of the plate 105. The rib 113 extends between a first longitudinal end 114 and a second longitudinal end 115, the first longitudinal end 114 being in contact with the raised edge 107, and preferably in contact with a first raised side edge 109a that includes the raised edge 107. The second longitudinal end 115 is located at a first non-zero distance Di from the raised edge 107, the first distance Di being taken between the second longitudinal end 115 and the raised edge 107, measured along the longitudinal elongation axis Ai of the plate 105.

These arrangements are such that the channel 111 is shaped as a U, the branches of the U of which are parallel to the raised longitudinal edges 108a, 108b of the plate 105 and are separated by the rib 113, and the base of the U of which adjoins a second lateral edge. 109b which is formed longitudinally opposite the first lateral edge 109a. The rib 113 is formed at an equal second distance D2 from the two longitudinal edges 108 of the plate 105, the second distance D2 being measured between the rib 113, taken at its center, and one of the raised longitudinal edges 108a, 108b, perpendicularly to the longitudinal elongation axis Ai of the plate 105.

According to an alternative embodiment, the rib 113 is offset by a non-zero distance relative to a median plane Pi of the plate 105, the median plane Pi being orthogonal to the bottom 106 and parallel to the longitudinal elongation axis Al of the plate 105, the distance being measured between the rib 113, taken at its center, and the median plane Pi perpendicular to the latter.

The protuberances 112 are divided into at least a first group of protrusions Gi which determines a first passage section Si of the channel 111 delimited by at least one top wall 116 of a protuberance 112 of the first group of protuberances Gi and a second group of protuberances G2 which determines a second passage section S2 of the channel 111 delimited by at least one top wall 116 of a protuberance 112 of the second group of protuberances G2. The first passage section Si is advantageously larger than the second passage section S2.

The plate 105 comprises a third group G3 of protuberances 112 which determines a third passage section S3 in the channel 111, the third passage section S3 being delimited by a plurality of top walls 116 of protuberances 112 of the third group G3. The third passage section S3 is advantageously smaller than the first passage section Si.

The protrusions 112 of the first group Gi, the protrusions 112 of the second group G2 and the protrusions 112 of the third group G3 are organized in a plurality of rectilinear rows 124 of protrusions 112, the rectilinear rows 124 being parallel to a lateral elongation axis A2 of the plate 105 which is orthogonal to the longitudinal elongation axis Ai of the plate 105.

The protrusions 112 of the first group Gi, the protrusions 112 of the second group G2 and the protrusions 112 of the third group G3 emerge from the same face 118 from the bottom 106 towards the channel 111.

Preferably, the protuberances 112 of the same group, regardless of the first group Gi, the second group G2 or the third group G3, are identical in shape and / or volume in particular, except for the manufacturing tolerance.

According to another embodiment, the protuberances 112 of the same group, regardless of the first group Gi, the second group G2 or the third group G3, are different from each other, in particular in shape and / or in volume.

In FIG. 5, four plates 105 are nested one inside the other so that the raised edge 107 of a plate 105 is embedded inside the raised edge 107 of the plate 105 immediately in succession and so that that the bottom 106 of a plate 105 is in contact with the top walls 116 of the protuberances 112 of the immediately successive plate 105. Such a stacking of the plates 105 is also carried out so that the bottoms 106 of the plates 105 are arranged parallel to one another in a distant and stepped superposition of the bottoms 106. The raised edges 107 of two plates 105 embedded one in the other are in contact and are intended to be brazed with each other to seal the channel 111 thus formed between two adjacent plates 105. Two adjacent plates 105 are also associated so that the grooves 113 of the two adjacent plates 105 are superimposed on each other, the respective median planes Pi of the adjacent plates 105 being juxtaposed with each other. More particularly, an apex 121 of the groove 113 of a plate 105 is in contact with a base 122 of the groove 113 of the immediately successive plate 105, the base 122 of the groove 113 being linked to the bottom 106 of the plate 105.

Two plates 105 thus nested one inside the other jointly delimit a tube 123 which channels a circulation of the refrigerant fluid 4 or else of the heat transfer liquid 6. In other words, the two plates 105 forming the tube 123 jointly delimit the channel 111 dedicated to the circulation of the coolant 4 or of the heat transfer liquid 6. More particularly, one side of a plate 105 borders the channel 111 for circulation of the heat transfer fluid 4 and the other side of the same plate 105 borders the channel 111 for circulation of the liquid coolant 6.

Thus, the plates 105 are arranged together so as to alternately configure the channels 111 for circulation of the coolant 4 and the heat transfer liquid 6. The first passage section Si of the channel 111 is shown in hatching.

Figures 6 to 8 each illustrate a partial cross section of the tube 123 which channels the circulation of the coolant 4 or the heat transfer liquid 6. The cross sections are formed inside a transverse plane P2 which is parallel to the axes of lateral elongation A2 of the plates 105 and orthogonal to the longitudinal elongation axes Ai of the plates 105.

The first passage section Si, illustrated in FIG. 6, and the second passage section S2, illustrated in FIGS. 7 and 8, are respective surfaces which are perpendicular to the bottom 106 of the plates 105 and to the axis of elongation. longitudinal Ai of the plate 105. The passage sections Si, S2 are delimited by the bottoms 106 of the plates 105, a raised longitudinal edge 108a of one of the plates 105 and the rib 113, the passage sections Si, S2 passing through the top walls 116 of the protrusions 112.

In Figure 6, the cross section is made through the top walls 116 of a row 124 of protrusions 112 of the first group Gi. The first passage section Si of channel 111 is shown in hatching. A first plate 105, lower in FIG. 6, comprises two protrusions 112 and a second plate 105, upper in FIG. 6, comprises three protrusions 112, the protuberances 112 of one and the other of the plates 105 being identical in volume. .

In FIG. 7, the cross section is made through the top walls 116 of a row 124 of protuberances 112 of the second group G2. The second passage section S2 of channel 111 is shown in hatching. A first plate 105, lower in FIG. 7, comprises five protrusions 112 and a second plate 105, upper in FIG. 7, also comprises five protrusions 112, the protuberances 112 of one and the other of the plates 105 being identical in volume.

It is understood by comparing Figures 6 and 7 that the difference in area between the first passage section Si and the second passage section S2 depends on a different number of protrusions 112 which are nevertheless identical from a dimensional point of view. In other words, the protuberances 112 of the first group Gi and the protuberances 112 of the second group G2 are identical, in shape and / or volume in particular, except for the manufacturing tolerance. The protuberances 112 of the first group Gi and the protuberances 112 of the second group G2 being identical, the number of protuberances 112 of the first group Gi is less important than the number of protuberances 112 of the second group G2, per unit of comparable area. In other words, a first density of protuberances 112 of the first group Gi is less than a second density of protuberances 112 of the second group G2.

It should be noted that the arrangements described in FIG. 7 for the protrusions 112 of second group G2 are fully transposable for the protrusions 112 of third group G3, so that the difference in area between the first passage section Si and the third section passage S3 is explained by the same reasons which prevail for the difference in surface area between the first passage section Si and the second passage section S2.

In FIG. 8, the cross section is made through the top walls 116 of a row 124 of protuberances 112 of the second group G2. The second passage section S2 of channel 111 is shown in hatching. A first plate 105, lower in FIG. 8, comprises three protrusions 112 and a second plate 105, upper in FIG. 8, comprises two protrusions 112, the protuberances 112 of one and the other of the plates 105 being identical in volume . Note that the protrusions 112 of the plates 105 illustrated in FIG. 8 have a section taken in the transverse plane P2 which is greater than a section taken in the transverse plane P2 of the protrusions 112 of the plates 105 illustrated in FIG. 6.

It is understood by comparing Figures 6 and 8 that the difference in area between the first passage section Si and the second passage section S2 depends on a dimensional difference of a protuberance 112 of the first group Gi compared to a protuberance 112 of the second group G2. The protrusions 112 of the first group Gi and the protrusions 112 of the second group G2 are different from each other in volume. In such a case, the density of protuberances 112 of the first group Gi of protuberances 112 is equal to the density of protuberances 112 of the second group of protuberances G2, but the protuberances 112 of the first group Gi occupy a first volume in the channel 111 which is less important than a second volume occupied by the protuberances 112 of the second group G2.

It should be noted that the arrangements described in FIG. 8 for the protrusions 112 of second group G2 are fully transposable for the protrusions 112 of third group G3, so that the difference in area between the first passage section Si and the third section passage S3 is explained by the same reasons which prevail for the difference in surface area between the first passage section Si and the second passage section S2.

In FIGS. 6 to 8, the raised edge 107 extends in an edge plane P3 which is transverse to the bottom plane P4 in which the bottom 106 extends. The raised side edges 109a, 109b and the raised longitudinal edges 108a , 108b extend inside respective edge planes P3 which each form with the bottom plane P4 an angle a which is between 91 ⁰ and 140 °, preferably between 91 ⁰ and 95 ⁰ .

The plate 105 is made of a metallic material, capable of being pressed to form in particular the protrusions 112 and the rib 113 by stamping the plate 105, the metallic material being chosen from thermally conductive metallic materials, aluminum or aluminum alloy in particular. .

Referring again to FIG. 4, it is noted that the second group G2 of protuberances 112 is formed between an opening 110 and the first group Gi of protuberances 112. Thus, due to a greater number of protuberances 112 than the second group G2 comprises with respect to a number of protuberances 112 of the first group Gi or else due to a greater volume of protuberances 112 of the second group G2 compared to the protuberances 112 of the first group Gi, the second group G2 of protuberances 112 forms at the outlet of the opening 110, a more substantial disturbance against a laminar flow of the coolant 4 or of the coolant 6, than a disturbance formed by the protrusions 112 of the first group Gi. The disturbance formed by the protrusions 112 of the second group G2 causes diffusion of the coolant 4 or the heat transfer liquid 6 over the entire width of the channel 111 taken in the transverse plane P2 between the rib 113 and the raised longitudinal edge 108b. These arrangements make it possible to improve, along the lateral elongation axis A2 of the plate 105, a distribution of the coolant 4 or of the heat transfer liquid 6 in the channel 111, and to reduce a speed of circulation of the coolant 4 or heat transfer liquid 6 in the channel 111.

It is also noted that the third group G3 of protuberances 112 is formed between the other opening 110 and the first group Gi of protuberances 112. Thus, due to a greater number of protuberances 112 than the third group G3 of protuberances 112 comprises by relative to a number of protuberances 112 of the first group Gi of protuberances 112 or else due to a larger volume of protuberances 112 of the third group G3 compared to the protuberances 112 of the first group Gi, the third group G3 of protuberances 112 forms, at the outlet of the first circulation path 21, a plug more substantial against a laminar flow of the coolant 4 or of the heat transfer liquid 6, than a plug formed by the protuberances 112 of the first group Gi. The plug formed by the protrusions 112 of the third group G3 causes a temporary reflux of the refrigerant 4 or the heat transfer liquid 6 towards the protrusions 112 of the first group Gi. These arrangements make it possible to improve, along the lateral elongation axis A2 of the plate 105, a distribution of the coolant 4 or of the heat transfer liquid 6 in the channel 111, and to reduce a speed of circulation of the coolant 4 or heat transfer liquid 6 in the channel 111.

To this end, the first group Gi of protuberances 112 is arranged between the second group G2 of protuberances 112 and the third group G3 of protuberances 112.

The second group G2 of protuberances 112 and / or the third group G3 of protuberances 112 are formed at a third distance D3 from the opening 110 to which they are assigned which is between 10% and 25% of a length L of the plate 105. The third distance D3 is measured between a center C of the opening and a barycenter B of the protuberances 112 of the same group G2, G3. The length L of the plate 105 is measured between the two lateral edges 109a, 109b of the plate

105 parallel to the longitudinal extension axis Ai of the plate 105.

Preferably, the protuberances 112 of the first group Gi of protuberances 112, of the second group G2 of protuberances 112 and of the third group G3 of protuberances 112 have in the transverse plane P2 a frustoconical shape.

In FIG. 9, the second heat exchanger 12 is generally parallelepipedic and comprises a cheek 200 which is provided with an inlet for the refrigerant fluid 203 by means of which the coolant fluid 4 penetrates inside the second heat exchanger 12 and an evacuation of the refrigerant 104 by means of which the refrigerant 4 is evacuated from the second heat exchanger 12. The first circulation paths extend between the admission of the refrigerant 203 and the evacuation of the fluid refrigerant 204.

The second heat exchanger 12 comprises tubes 223 which channel the first circulation paths arranged in "I". The tubes 223 are formed by two plates 205 such as those illustrated in FIG. 10. Such a second heat exchanger 12 is arranged so that the air flow 10 circulates through the heat exchanger 12 between two tubes 223 successive.

The plate 205 mainly extends along a longitudinal axis of elongation A1. The plate 205 comprises a bottom 206 and at least one raised edge 207 which surrounds the bottom 206. In other words, the raised edge 207 is formed at the periphery of the bottom 206 and the raised edge 207 surrounds the bottom 206. It is understood that the plate 205 is arranged in a generally rectangular bath, the bottom of the bath being made up of the bottom 206 and the edges of the bath being made up of the raised edge 207. More particularly , the raised edge 207 comprises two longitudinal raised edges 208a, 208b formed opposite one another and two lateral raised edges 209a, 209b formed opposite one another.

The plate 205 comprises two openings 210, in particular circular, which are distributed at each longitudinal end of the plate 205. One of the openings 210 is surrounded by a collar 220, so that this opening 210 surrounded by this collar 220 extends in a plane offset from the plane in which the bottom 206. The other opening 210 located at the other longitudinal end of the plate 205 extends in a plane which coincides with the plane in which the bottom 206.

Two plates 205 are nested one inside the other and in contact with each other at least via their raised edges 207. In other words, two plates 205 are stacked one above the other. 'other and provide between them a space which forms a channel 211 for circulation of the coolant 4.

The bottom 206 is provided with a plurality of protrusions 212 which with at least the bottom 206 and the raised edge 207 define a passage section Si, S2 of the refrigerant 4 in the channel 211.

The protrusions 212 are divided into at least a first group of protrusions Gi which determines a first passage section Si of the channel 211 delimited by at least one top wall 216 of a protuberance 212 of the first group of protuberances Gi and a second group of protuberances G2 which determines a second passage section S2 of the channel 211 delimited by at least one top wall 216 of a protuberance 212 of the second group of protuberances G2. The first passage section Si is advantageously larger than the second passage section S2.

The plate 205 comprises a third group G3 of protuberances 212 which determines a third passage section S3 in the channel 211, the third passage section S3 being delimited by a plurality of top walls 216 of protuberances 212 of the third group G3. The third passage section S3 is advantageously smaller than the first passage section Si.

The protrusions 212 of the first group Gi, the protrusions 212 of the second group G2 and the protrusions 212 of the third group G3 are organized in a plurality of straight rows 224 of protrusions 212, the straight rows 224 being parallel to a lateral elongation axis A2 of the plate 205 which is orthogonal to the longitudinal elongation axis Ai of the plate 205.

The protrusions 212 of the first group Gi, the protrusions 212 of the second group G2 and the protrusions 212 of the third group G3 emerge from the same face 218 from the bottom 206 towards the channel 211.

Preferably, the protuberances of the same group, regardless of the first group Gi, the second group G2 or the third group G3, are identical in shape and / or volume in particular, except for the manufacturing tolerance.

According to another embodiment, the protrusions 212 of the same group, regardless of the first group Gi, the second group G2 or the third group G3, are different from each other, in particular in shape and / or volume.

In FIG. 11, four plates 205 are nested one inside the other so that the raised edge 207 of a plate 205 is embedded inside the raised edge 207 of the plate 205 immediately in succession and so that that the bottom 106 of a plate 205 is in contact with the top walls 216 of the protuberances 212 of the plate 205 immediately successive. Such a stacking of the plates 205 is also carried out so that the bottoms 206 of the plates 205 are arranged parallel to one another in a distant and stepped superposition of the bottoms 206. The raised edges 207 of two plates 205 embedded one in the other are in contact and are intended to be brazed with each other to seal the channel 211 thus formed between two adjacent plates 105. Two adjacent plates 205 are also associated so that the respective median planes Pi of the adjacent plates 205 are juxtaposed with each other.

Two plates 205 thus nested one inside the other jointly delimit the tube 223 which channels a circulation of the refrigerant fluid 4. In other words, the two plates 205 forming the tube 223 jointly delimit the channel 211 dedicated to the circulation of the refrigerant fluid 4 More particularly, one side of a plate 205 borders the channel 211 for circulation of the coolant 6 and the other side of the same plate 205 borders the space formed between two tubes 223 where air flow circulates 10. The first passage section Si of channel 211 is shown in hatching.

FIGS. 12 to 14 each illustrate a partial cross section of the tube 223 which channels the circulation of the refrigerant fluid 4. The cross sections are formed inside a transverse plane P2 which is parallel to the axes of lateral extension A2 of the plates 205 and orthogonally to the longitudinal elongation axes Ai of the plates 205.

The first passage section Si, illustrated in FIG. 12, and the second passage section S2, illustrated in FIGS. 13 and 14, are surfaces which are perpendicular to the bottom 206 of the plates 205 and to the longitudinal elongation axis. Ai of the plate 205. The passage sections Si, S2 are delimited by the bottoms 206 of the plates 205 and the raised edge 207 of one of the plates 205, the passage sections Si, S2 passing through the top walls 216 of the protuberances 212.

In Figure 12, the cross section is made through the top walls 216 of a row 224 of protrusions 212 of the first group Gi. The first passage section Si of channel 211 is shown in hatching. A first plate 205, lower in FIG. 12, comprises two protrusions 212 and a second plate 205, upper in FIG. 12, comprises three protrusions 212, the protuberances 212 of one and the other of the plates 205 being identical in volume. .

In FIG. 13, the cross section is made through the top walls 216 of a row 224 of protuberances 212 of the second group G2. The second passage section S2 of channel 211 is shown in hatching. A first plate 205, lower in FIG. 13, includes five protrusions 212 and a second plate 205, upper in FIG. 13, also includes five protrusions 212, the protrusions 212 of one and the other of the plates 205 being identical in volume.

It is understood by comparing Figures 12 and 13 that the difference in area between the first passage section Si and the second passage section S2 depends on a different number of protrusions 212 which are nevertheless identical from a dimensional point of view. In other words, the protrusions 212 of the first group Gi and the protrusions 212 of the second group G2 are identical, in shape and / or volume in particular, to the manufacturing tolerance. The protrusions 212 of the first group Gi and the protrusions 212 of the second group G2 being identical, the number of protrusions 212 of the first group Gi is less important than the number of protrusions 212 of the second group G2, per unit of comparable area. In other words, a first density of protuberances 212 of the first group Gi is less than a second density of protuberances of the second group G2.

Note that the arrangements described in FIG. 13 for the protrusions 212 of second group G2 are fully transposable for the protrusions 212 of third group G3, so that the difference in area between the first passage section Si and the third section passage S3 is explained by the same reasons which prevail for the difference in surface area between the first passage section Si and the second passage section S2.

In FIG. 14, the cross section is made through the top walls 216 of a row 224 of protuberances 212 of the second group G2. The second passage section S2 of channel 211 is shown in hatching. A first plate 205, lower in FIG. 14, comprises five protrusions 212 and a second plate 105, upper in FIG. 14, also comprises five protrusions 212, the protrusions 212 of one and the other of the plates 205 being identical in volume. Note that the protrusions 212 of the plates 205 illustrated in FIG. 14 have a section taken in the transverse plane P2 which is greater than a section taken in the transverse plane P2 of the protrusions 212 of the plates 205 illustrated in FIG. 12.

It is understood by comparing FIGS. 12 and 14 that the difference in area between the first passage section Si and the second passage section S2 depends on a dimensional difference of a protuberance 212 of the first group Gi compared to a protuberance 212 of the second group G2. The protrusions 212 of the first group Gi and the protrusions 212 of the second group G2 are different from each other in volume. In such a case, the density of protuberances 212 of the first group Gi of protuberances 212 is equal to the density of protuberances 212 of the second group of protuberances G2, but the protuberances 212 of the first group Gi occupy a first volume in the channel 211 which is less important than a second volume occupied by the protrusions 212 of the second group G2.

Note that the arrangements described in FIG. 14 for the protrusions 212 of second group G2 are fully transposable for the protrusions of third group G3, so that the difference in area between the first passage section Si and the third passage section S3 is explained by the same reasons which prevail for the difference in surface area between the first passage section Si and the second passage section S2.

In FIGS. 12 to 14, the raised edge 207 extends in an edge plane P3 which is transverse to a bottom plane P4 in which the bottom 206 extends. The raised side edges 209a, 209b and the raised longitudinal edges 208a, 208b extend inside respective planes which each form with the bottom plane P4 an angle a which is between 91 ⁰ and 140 °, preferably between 91 ° and 95 ⁰ .

The plate 205 is made of a metallic material, capable of being stamped to form in particular the protrusions 212 by stamping the plate 205, the metallic material being chosen from thermally conductive metallic materials, aluminum or aluminum alloy in particular.

Referring again to FIG. 10, it is noted that the second group G2 of protuberances 212 is formed between an opening 210 and the first group Gi of protuberances 212. Thus, due to a greater number of protuberances 212 than the second group G2 comprises with respect to a number of protuberances 212 of the first group Gi or else due to a larger volume of protuberances 212 of the second group G2 compared to the protuberances 212 of the first group Gi, the second group G2 of protuberances 212 forms at the outlet of the opening 210, a more substantial disturbance against a laminar flow of the coolant 4 than a disturbance formed by the protrusions 212 of the first group Gi. The disturbance formed by the protrusions 212 of the second group G2 causes the refrigerant 4 to diffuse over the entire width of the channel 211 taken in the transverse plane P2 between the raised longitudinal edges 108a, 108b. These arrangements make it possible to improve, along the lateral extension axis A2 of the plate 205, a distribution of the refrigerant 4 in the channel 211, and to reduce a speed of circulation of the refrigerant 4 in the channel 211.

It is also noted that the third group G3 of protuberances 212 is formed between the other opening 210 and the first group Gi of protuberances 212. Thus, due to a greater number of protuberances 212 that the third group G3 comprises with respect to a number of protrusions 212 of the first group Gi or else due to a larger volume of protrusions 212 of the third group G3 compared to the protrusions 212 of the first group Gi, the third group G3 of protrusions 212 forms, at the exit of the first path circulation, a larger plug against a laminar flow of the coolant 4 compared to a plug formed by the protrusions 212 of the first group Gi. The plug formed by the protrusions 212 of the third group G3 causes a temporary reflux of the refrigerant 4 towards the protrusions 212 of the first group Gi. These arrangements make it possible to improve, along the lateral extension axis A2 of the plate 205, a distribution of the refrigerant 4 in the channel 211, and to reduce a speed of circulation of the refrigerant 4 in the channel 211.

To this end, the first group Gi of protuberances 212 is arranged between the second group G2 of protuberances 212 and the third group G3 of protuberances 212.

The second group G2 of protuberances 212 and / or the third group G3 of protuberances 212 are formed at a third distance D3 from the opening 210 to which they are assigned which is between 10% and 25% of a length L of the plate 205. The third distance D3 is measured between a center C of the opening and a barycenter B of the protrusions 212 of the same group G2, G3. The length L of the plate 205 is measured between the two lateral edges 209a, 209b of the plate 205 parallel to the longitudinal extension axis Ai of the plate 205.

Preferably, the protuberances 212 of the first group Gi of protuberances 212, of the second group G2 of protuberances 212 and of the third group G3 of protuberances 212 have in the transverse plane P2 a frustoconical shape.

As it has just been described, the invention achieves well the goals which it had set itself, by making it possible to homogenize the heat exchanges over the entire width of the plate, thus avoiding the zones of least exchange, for example along the rib 113 or along the longitudinal raised edges 108a, 108b, 208a, 208b.

The invention cannot however be limited to the means and configurations exclusively described and illustrated, and also applies to all means or configurations, equivalent and to any combination of such means or configurations. In particular, if the invention has been described here in its application to a coolant / heat transfer fluid or air heat exchanger, it goes without saying that it applies to any shape and / or size of the plate or to any type of fluid flowing along the plate according to the invention.

Claims (10)

1. Plate (105, 205) constituting a heat exchanger (11, 12) and intended to delimit at least one channel (111, 211) for circulation of a fluid (4, 6), the plate (105, 205) comprising a bottom (106, 206) and at least one raised edge (107, 207) which surrounds the bottom (106, 206), the plate (105, 205) comprising at least one opening (110, 210) configured to supplying the channel (111, 211) with fluid, the plate (105, 205) being provided with protuberances (112, 212) which with at least the bottom (106, 206) and the raised edge (107, 207) delimit a section passage (Si, S2) of the fluid (4, 6) in the channel (m, 211), in which the protrusions (112, 212) are distributed in at least a first group (Gi) of protrusions (112, 212) which determines a first passage section (Si) of the channel (111, 211) delimited by at least one top wall (116, 216) of a protuberance (112, 212) of the first group (Gi) and a second group (G2 ) of protuberances (112, 212) which det erminates a second section (S2) for passage of the channel (111, 211) delimited by at least one top wall (116, 216) of a protuberance (112, 212) of the second group (G2), the first passage section ( Si) being larger than the second passage section (S2). 2. Plate (105, 205) according to claim 1, wherein the bottom (106, 206) comprises a rib (113) which is arranged so that the channel (111, 211) has a U-shaped profile. 3. Plate (105, 205) according to any one of the preceding claims, in which the plate (105, 205) comprises at least two openings (110, 210). 4. Plate (105, 205) according to any one of the preceding claims, in which the second group (G2) of protuberances (112, 212) is formed between an opening (110, 210) and the first group (Gi) of protrusions (112, 212). 5. Plate (105, 205) according to any one of the preceding claims, in which the plate (105, 205) comprises a third group (G3) of protuberances (112, 212) which determines a third passage section (S3) in the channel (111, 211), the third passage section (S3) being delimited by at least one top wall (116, 216) of a protuberance (112, 212) of the third group (Gs), the third section of passage (S3) being smaller than the first passage section (Si). 6. Plate (105, 205) according to claim 5, in which the first group (Gi) of protuberances (112, 212) is disposed between the second group (G2) of protuberances (112, 212) and the third group (G3 ) of protuberances (112, 212). 7. Plate (105, 205) according to any one of claims 5 and 6, characterized in that at least one group from the second group (G2) of protuberances (112, 212) or the third group (G3) of protrusions (112, 212) is formed at a distance (D3) from the opening (110) between 10% and 25% of a length (L) of the plate (105, 205). 8. Plate (105, 205) according to any one of claims 5 to 7, in which any at least of a protuberance (112, 212) of the first group of protuberances (Gi), of a protuberance ( 112, 212) of the second group of protuberances (G2) and / or of a protuberance (112, 212) of the third group of protuberances (G3) has a frustoconical shape. 9. Plate (105, 205) according to any one of claims 5 to 8, in which at least two protuberances (112, 212) of the same group of protuberances (G1, G2, G3) are aligned along a lateral elongation axis (A2) of the plate (105) which is orthogonal to a longitudinal elongation axis (A1) of the plate (105, 205). 10. Heat exchanger (11,12) comprising at least one plate (105, 205) according to any one of the preceding claims.