Heat exchanger comprising a plurality of stacked plates

Abstract

Heat exchanger comprising a plurality of stacked plates. The present invention relates to a heat exchanger (11) comprising a plurality of stacked plates (300, 302), one of these plates (300, 302) being configured to delimit at least one circulation channel (306, 307) for a fluid (4, 6). The plate has at least one pair of fluid openings (310, 311, 410) configured so that the fluid (4, 6) enters and exits the circulation channel (310, 311). The plate extends primarily along a longitudinal axis (A10) between a first end (312) and a second end (314). The plate (300, 302) includes, in the channel (306, 307) between the fluid openings (310, 311), at least one low pressure drop zone (320) and at least one high pressure drop zone (330), these zones being configured to promote a balanced distribution of the fluid over the entire width of this channel. [Fig. 10]

Description

Title of the invention: Heat exchanger comprising a plurality of stacked plates

[0001] The present invention relates to a heat exchanger comprising a plurality of stacked plates.

[0002] In the automotive field, it is common to have to modify the temperature of a component, such as an electric motor, a battery, a heat and / or cooling storage device, or the like. For this purpose, the motor vehicle is equipped with a system comprising a refrigerant circuit through which a refrigerant circulates and a heat transfer fluid circuit through which a heat transfer fluid circulates. The refrigerant circuit includes a compressor to compress the refrigerant, a heat exchanger to cool the refrigerant at constant pressure, an expansion valve to allow the refrigerant to expand, and a heat exchanger arranged to allow heat transfer between the refrigerant and the heat transfer fluid.

[0003] The heat exchanger is an exchanger formed of plates stacked and joined together to form tubes delimiting circulation channels for the refrigerant or heat transfer fluid.

[0004] Each circulation channel provides a passage section for the heat transfer fluid or the refrigerant fluid, the passage section being a surface perpendicular to the plane in which the plate extends and secant to an axis of longitudinal elongation of the plate.

[0005] The heat exchanger is a heat exchanger in which the flow paths of the refrigerant and the heat transfer fluid are arranged in a "U" or "I" shape.

[0006] For this purpose, the plate may be provided with a rib which delimits the branches of the "U" and which is interposed between the branches of the "U" or may be devoid of such a rib so as to form the traffic path in "I".

[0007] One problem lies in the poor distribution of the refrigerant and / or heat transfer fluid within the circulation channel. Such poor distribution reduces the efficiency of heat transfer between the refrigerant and the heat transfer fluid.

[0008] An object of the present invention is in particular to avoid areas under-supplied with heat transfer fluid and / or refrigerant fluid, and therefore to reduce a bad distribution of the heat transfer fluid and / or refrigerant fluid inside a circulation channel, with a view to increasing the efficiency of heat transfer.

[0009] The invention thus relates to a heat exchanger comprising a plurality of stacked plates, one of these plates being configured to delimit at least one fluid circulation channel,

[0010] the plate includes at least one pair of fluid openings configured so that the fluid enters and exits the circulation channel,

[0011] the plate extending mainly along a longitudinal elongation axis between a first end and a second end,

[0012] the plate comprising, in the channel between the openings at least one zone of low pressure loss and at least one zone of high pressure loss, these zones being configured to promote a balanced distribution of the fluid over the entire width of this channel.

[0013] The term “fluid” means the refrigerant or heat transfer fluid intended to circulate in the circulation channel.

[0014] The terms "low pressure loss zone" and "high pressure loss zone" refer to areas that generate different pressure losses. The "higher pressure loss zone" relative to the "lower pressure loss zone" can, for example, be achieved by using a higher density of the flow disturbance pattern in the "higher pressure loss zone" or by using at least one pattern that creates more resistance to flow.

[0015] The consequence is then a modification of the fluid flow in the plate. For example, if the fluid enters an area of ​​high pressure drop, part of the flow will bypass this area, supplying more of the fluid to the area of ​​lower pressure drop. This modification corresponds to pressure equalization across the fluid passage.

[0016] In the case where the area of ​​high pressure loss is arranged over the entire width of the passage section or the width of the channel, the fluid will tend to distribute itself homogeneously over this entire width corresponding to the state where the pressure in this section is homogeneous.

[0017] Thanks to the invention, the fluid is distributed in a balanced way over the entire width of the channel between the fluid openings.

[0018] A "balanced fluid distribution" is understood to mean a uniform distribution of the fluid over the entire width of a fluid flow zone of the plate.

[0019] The term "fluid flow zone of the plate" refers to the area where the fluid is present on the plate. The fluid flow zone of the plate may, for example, be free of areas where fluid openings are present. The fluid flow zone of the plate may, for example, have a substantially rectangular shape with a length x_tot and a width z_tot.

[0020] In this way, the fluid can be distributed from areas where the flow is abundant, for example in areas near a fluid opening, to areas where the flow is insufficient, for example towards outer corners of the plate.

[0021] Thus, the invention makes it possible to have a satisfactory flow of fluid over the entire width of the fluid flow zone of the plate and to have better heat exchange over a larger surface of the plate, in particular on the outside corners of the plate.

[0022] In this way, poor fluid distribution within the circulation channel is reduced. Consequently, the efficiency of heat transfer between the refrigerant and the heat transfer fluid is increased.

[0023] According to one aspect of the invention, the area of ​​high pressure loss is surrounded, in particular upstream and downstream, by areas of low pressure loss.

[0024] According to one aspect of the invention, the area of ​​high pressure loss extends over the entire width of the channel.

[0025] According to one aspect of the invention, the area of ​​high pressure loss extends over a portion of the width of the channel.

[0026] According to one aspect of the invention, the high pressure loss zone extends over a portion of the channel width whose width is between 50 and 90% of the channel width, preferably between 60 and 80% of the channel.

[0027] According to one aspect of the invention, the first and second ends are connected to each other by two raised edges of the plate.

[0028] According to one aspect of the invention, the two openings are located on a bottom of the plate.

[0029] According to one aspect of the invention, the plate includes a rib between the pair of fluid openings to create a U-shaped circulation between the pair of fluid openings.

[0030] According to one aspect of the invention, the rib has a wavy shape.

[0031] According to one aspect of the invention, the rib has a rectangular shape.

[0032] According to one aspect of the invention, the plate comprises at least the areas of high pressure loss which is distributed on both sides of the rib.

[0033] According to one aspect of the invention, the areas of high pressure loss are symmetrical with respect to the rib.

[0034] According to one aspect of the invention, the areas of high pressure loss are aligned perpendicularly to the main axis of the rib.

[0035] According to one aspect of the invention, the high pressure loss zones on either side of the rib are offset from each other along the main axis of the rib.

[0036] According to one aspect of the invention, the offset between the high pressure loss zones is between 5 and 100% of the dimensions of the high pressure loss zone, preferably between 10 and 50% of the dimensions of the high pressure loss zone.

[0037] According to one aspect of the invention, the low pressure loss zone comprises a plurality of flow perturbators, in particular in the form of protrusions.

[0038] Thus, the heat exchanger allows for a homogenization of the fluid circulation velocity within the circulation channel. In this way, heat transfer is optimized, for example between the refrigerant and the heat transfer fluid.

[0039] According to one aspect of the invention, the area of ​​high pressure loss has undulating reliefs, called corrugations.

[0040] According to one aspect of the invention, the wavy reliefs are made in a single piece with the plate.

[0041] According to one aspect of the invention, the high pressure loss zone comprises fins, in particular flat fins, and / or louvered fins.

[0042] According to one aspect of the invention, the high pressure loss zone comprises flow disruptors with a higher concentration compared to the low pressure loss zone.

[0043] According to one aspect of the invention, the fins are parts added to the plate, in particular welded or brazed to the plate.

[0044] According to one aspect of the invention, the high pressure loss zone comprises alternating crenellation reliefs, in particular called offsets.

[0045] According to one aspect of the invention, the reliefs of alternating crenellations are pieces added to the plate, in particular welded or brazed to the plate.

[0046] According to one aspect of the invention, the high pressure loss zone comprises undulating reliefs, fins and / or alternating crenellated reliefs.

[0047] According to one aspect of the invention, at least one of the low pressure loss zones is surrounded, particularly upstream and downstream, by high pressure loss zones.

[0048] According to one aspect of the invention, the low pressure loss zone is located on the outside of the bend of the U-shaped channel.

[0049] According to one aspect of the invention, the high pressure loss zone comprises a plurality of flow disruptors.

[0050] According to one aspect of the invention, the low pressure loss zone is free from flow disruptors.

[0051] According to one aspect of the invention, the plate has at least three low pressure loss zones, called bypass zones.

[0052] According to one aspect of the invention, two of the three low pressure loss zones are located at opposite raised edges of the plate.

[0053] According to one aspect of the invention, two of the three low pressure drop zones are located opposite each other.

[0054] According to one aspect of the invention, two of the three low pressure loss zones are offset from each other with respect to a main axis of the rib.

[0055] According to one aspect of the invention, one of the opposite edges of the plate has at least two low pressure loss zones.

[0056] According to one aspect of the invention, the two low pressure loss zones of the same opposite edge are aligned with respect to the longitudinal elongation axis.

[0057] According to one aspect of the invention, the other of the three low pressure loss zones is located at one of the two ends of the plate, namely the first or second end of the plate.

[0058] According to one aspect of the invention, the low pressure loss zone has a shape chosen from polygonal, ellipsoidal and circular shapes.

[0059] According to one aspect of the invention, the low pressure drop zone has a rectangular shape.

[0060] According to one aspect of the invention, the ratio between the horizontal length, x_bypass, of the low pressure loss zone when said zone is oriented parallel to the longitudinal elongation axis and the total length of a fluid flow zone of the plate, x_tot, is greater than 20% (x_bypass / x_tot *100 > 20%)

[0061] According to one aspect of the invention, the ratio between the vertical length, z_bypass, of the low pressure loss zone when said zone is oriented perpendicular to the longitudinal elongation axis and the total width of the fluid flow zone of the plate, z_tot, is greater than 20% (z_bypass / z_tot *100 > 20%).

[0062] According to one aspect of the invention, the ratio between the width of the low pressure loss zone, y_bypass, when said zone is oriented parallel to the longitudinal elongation axis and the channel width, y_tot, is between 5% and 20%.

[0063] According to one aspect of the invention, the heat exchanger comprises:

[0064] - a first plate configured to delimit the first circulation channel of a first fluid, and

[0065] - a second plate configured to delimit the second traffic channel of a second fluid.

[0066] The first fluid can be, for example, a refrigerant and the second fluid can be a heat transfer fluid. Of course, the first fluid can be a heat transfer fluid and the second fluid can be a refrigerant.

[0067] According to one aspect of the invention, the first and second plates each have a pair of openings configured so that the first fluid and the second fluid enters and exits respectively the first circulation channel and the second circulation channel.

[0068] According to one aspect of the invention, the main axis of the rib of the first plate and the main axis of the rib of the second plate are arranged so as to overlap.

[0069] According to one aspect of the invention, the fluid openings of the first and second plate are arranged symmetrically from the first plate to the second plate with respect to the plane perpendicular to the main axis of the rib of one of the plates.

[0070] According to one aspect of the invention, the heat exchanger forms an evaporator.

[0071] The invention also relates to a plate of a heat exchanger, said plate being intended to delimit at least one fluid circulation channel,

[0072] the plate includes at least one pair of fluid openings configured so that the fluid enters and exits the circulation channel,

[0073] the plate extending mainly along a longitudinal elongation axis between a first end and a second end,

[0074] the plate comprising, in the channel between the openings at least one zone of low pressure loss and at least one zone of high pressure loss, these zones being configured to promote a balanced distribution of the fluid over the entire width of this channel.

[0075] According to an independent aspect or in combination with the foregoing, a plate constituting a heat exchanger is provided, intended to delimit at least a first circulation channel for a first fluid and a second circulation channel for a second fluid. The plate extends primarily along a longitudinal axis between a first lateral raised edge and a second lateral raised edge constituting a raised edge of the plate. The longitudinal axis is orthogonal to a median lateral plane dividing the plate into a first zone comprising the first lateral raised edge and a second zone. The plate comprises at least one bottom having at least two pairs of openings configured for the fluids to enter and exit the channels. The bottom has a rib extending longitudinally between a first end connected to the first lateral raised edge and a second end.

[0076] According to the present invention, the two pairs of openings are arranged inside the first zone.

[0077] The plate advantageously comprises at least one of the following characteristics, taken alone or in combination:

[0078] - the first zone has a first length measured between the first raised edge lateral and median lateral plane parallel to the longitudinal elongation axis,

[0079] - the second zone is of a second length measured between the second raised lateral edge and median lateral plane parallel to the longitudinal elongation axis,

[0080] - the first length and the second length are equal,

[0081] - the second zone comprises the second lateral edge,

[0082] - a pair of first openings is configured so that the first fluid enters and sort of the first channel,

[0083] - a pair of second openings is configured so that the second fluid enters and exits from the second channel.

[0084] - the pair of first openings and the pair of second openings are located within the first zone,

[0085] - the second zone is free of openings,

[0086] - the first fluid is a refrigerant fluid,

[0087] - the second fluid is a heat transfer fluid,

[0088] - the rib is formed at an equal distance, within + / - 5%, from the two raised edges longitudinal edges of the plate, the distance being measured between a center of the rib and one of the longitudinal edges of the plate,

[0089] - the rib is offset by a non-zero distance from the longitudinal plane median of the plate,

[0090] - the median longitudinal plane is orthogonal to a background plane in which the bottom of the plate and parallel to the longitudinal elongation axis of the plate,

[0091] - the two pairs of openings are aligned along an alignment axis which is parallel to the median lateral plane,

[0092] - the respective centers of the two first-type openings and the two openings of The second type are aligned along the alignment axis.

[0093] - a first gap maintained between the alignment axis and the first raised lateral edge is less than 50% of the first length,

[0094] - the first deviation is less than 30% of the first length,

[0095] - the openings are arranged inside a third zone which is free from protuberance,

[0096] - the third zone is longitudinally bordered by the first raised lateral edge and a first separation line, the first separation line being parallel to the first raised lateral edge and being positioned at a second gap, provided between the first raised lateral edge and the separation line, which is less than 60% of the first length,

[0097] - the second deviation is less than 40% of the first length,

[0098] - the plate is a first-type plate whose second end of the rib is a free end exempt from contact with the raised edge,

[0099] - the second longitudinal end is located at a distance of one-seventh non-zero of the raised rim, the seventh distance being taken between the second longitudinal end and the second raised lateral edge, measured along the longitudinal elongation axis of the first type plate,

[0100] - the rib is arranged so that the first channel and / or the second channel presents a U-shaped profile,

[0101] - the first channel and / or the second channel is U-shaped, the branches of which are parallel to the longitudinal raised edges of the plate and whose base adjoins the second lateral raised edge which is located longitudinally opposite the first lateral raised edge,

[0102] - the first type plate has a fourth zone bordered by the second a lateral raised edge and a second dividing line, the second dividing line being parallel to the second lateral raised edge and being disposed at a third gap, provided between the second lateral raised edge and the second dividing line, which is less than 60% of the first length, a first density of protuberances inside the fourth zone being less than a second density of protuberances inside a fifth zone which is interposed between the fourth zone and the third zone,

[0103] - the third deviation is less than 40% of the first length,

[0104] - the second separation line includes the second end of the rib,

[0105] - the plate is a second type plate whose second longitudinal end is in contact with the raised edge,

[0106] - the second longitudinal end is in contact with the second raised edge lateral,

[0107] - the second type plate has a sixth zone which is bordered by the a second raised lateral edge and a third dividing line, the third dividing line being parallel to the second raised lateral edge and being positioned at a fourth gap, provided between the second raised lateral edge and the second dividing line, which is less than 60% of the first length, the sixth zone being free of protuberance,

[0108] - the fourth deviation is less than 40% of the first length,

[0109] - the plate is made of a metallic material, for example suitable for stamping to form, in particular, the rib and protrusions by stamping the plate, the metallic material being chosen from thermally conductive metallic materials, notably aluminum or aluminum alloy,

[0110] The plate extends in a plane and is shaped into a quadrilateral.

[0111] The plate includes at least four openings to allow the heat transfer fluid or refrigerant to enter and exit the circulation channels located on either side of the same plate.

[0112] The four openings are distributed at a respective corner of the plate.

[0113] The heat exchanger may include at least one such plate.

[0114] The heat exchanger advantageously comprises any one or more of the following features, taken alone or in combination:

[0115] - two plates are nested one inside the other and a space, which forms the first The circulation channel for the first fluid, or the second circulation channel for the second fluid, is provided between the two plates.

[0116] - at least three plates are nested one inside the other and delimit two to two channels, the first channel and the second channel, the first channel being configured to be used by a heat transfer fluid while the second channel is configured to be used by a refrigerant fluid,

[0117] - the heat exchanger includes a first circulation path participating of a refrigerant circuit within which a refrigerant circulates and a second circulation path within which a heat transfer fluid circulates, the first and second circulation paths being arranged to allow heat exchange between the refrigerant and the heat transfer fluid. To this end, the base comprises a first face bordering the first circulation path and a second face bordering the second circulation path.

[0118] - the heat exchanger comprises a plurality of such first-type plates and a first cheek equipped with a heat transfer fluid inlet, a heat transfer fluid outlet, a refrigerant inlet and a refrigerant outlet,

[0119] - the admission of the second fluid, the evacuation of the second fluid, the admission of the The first fluid and the first fluid evacuation are aligned along a second alignment axis which is parallel to the median lateral plane.

[0120] - the heat exchanger comprises such a second type plate,

[0121] - the cheek is equipped with two external channels,

[0122] - the inlet and outlet of the second fluid are arranged inside the first zone of the plate and the inlet of the first fluid and the outlet of the first fluid are arranged inside the second zone of the plate.

[0123] Other features, details and advantages of the invention will become apparent from the description given below by way of example in conjunction with drawings in which:

[0124] - [Fig. 1] is a schematic view of an installation comprising at least one heat exchanger according to the invention,

[0125] - [Fig.2] is a schematic view of a first variant embodiment of the heat exchanger participating in the installation shown in [Fig.1],

[0126] - [Fig.3] is a schematic front view of a constituent plate of the first type of the heat exchanger illustrated in [Fig.2],

[0127] - [Fig.4a], [Fig.4b], [Fig.4c] and [Fig.4d] are schematic illustrations respective of four variants of the realization of the first type plate shown in [Fig.3],

[0128] - [Fig.5] is a schematic front view of a constituent plate of the second type of the heat exchanger illustrated in [Fig.2],

[0129] - [Fig.6a], [Fig.6b], [Fig.6c] and [Fig.6d] are schematic illustrations respective of four variants of the second type of plate shown in [Fig.5],

[0130] - [Fig.7] is a schematic view of a second embodiment variant of the heat exchanger participating in the installation shown in [Fig.1],

[0131] - [Fig.8] is a schematic view of a third embodiment variant of the heat exchanger participating in the installation shown in [Fig.1],

[0132] - [Fig.9] is a schematic illustration of a cheek constituting the heat exchanger heat represented in [Fig.8],

[0133] - [Fig. 10] illustrates, schematically and partially, a heat exchanger according to a method of implementation,

[0134] - [Fig. 11] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0135] - [Fig. 12] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0136] - [Fig. 13] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0137] - [Fig. 14] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0138] - [Fig. 15] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0139] - [Fig. 16] illustrates, schematically and partially, a heat exchanger according to another method of implementation,

[0140] It should first be noted that the figures set out the invention in detail to implement the invention, said figures being of course able to serve to better define the invention where appropriate.

[0141] In [Fig. 1], a motor vehicle is equipped with a component 1 that needs to be cooled or heated, for example, to optimize its operation. Such a component 1 is, in particular, an electric or internal combustion engine intended to propel the motor vehicle, at least partially, a battery intended to store electrical energy, a heat and / or cooling storage device, or the like. For this purpose, the motor vehicle is equipped with an installation 2 that includes a refrigerant circuit 3 through which a first fluid 4, hereinafter referred to as the refrigerant 4, such as carbon dioxide or the like, circulates, and a heat transfer fluid circuit 5 through which a second fluid 6, hereinafter referred to as the heat transfer fluid 6, such as glycol water or the like, circulates. The installation 2 includes at least one heat exchanger 11 according to the present invention.Installation 2 is described below for a better understanding of the present invention, but the characteristics of the installation 2 described are in no way restrictive for the heat exchanger 11 of the present invention. In other words, installation 2 may have distinct structural characteristics and / or different operating modes than those described without the heat exchanger 11 deviating from the rules of the present invention.

[0142] The refrigerant circuit 3 includes a compressor 7 for compressing the refrigerant 4, a refrigerant / outside air exchanger 8 for cooling the refrigerant 4 at constant pressure, for example placed at the front of the motor vehicle, an expansion device 9 for allowing expansion of the refrigerant 4 and a heat exchanger 11 which is arranged to allow heat transfer between the refrigerant 4 and the heat transfer fluid 6.

[0143] Element 1 is related to a heat exchanger 14, the heat exchanger 14 being capable of modifying a temperature of element 1, in particular by direct contact provided between element 1 and heat exchanger 14, heat exchanger 14 being part of the heat transfer fluid circuit 5.

[0144] The heat transfer fluid circuit 5 includes a pump 15 for circulating the heat transfer fluid 6 within the heat transfer fluid circuit 5. The heat transfer fluid circuit 5 includes the heat exchanger 11, which is also part of the refrigerant circuit 3. The heat exchanger 11 includes at least one first circulation path 21 for the refrigerant 4 and at least one second circulation path 22 for the heat transfer fluid 6, the first circulation path 21 and the second circulation path 22 being arranged to allow heat exchange between the refrigerant 4 present within the first circulation path 21 and the heat transfer fluid 6 present within the second circulation path 22. Preferably, the heat exchanger 11 includes several first circulation paths 21 and several second circulation paths. 22. A first traffic path 21 is interposed between two second traffic paths 22, and a second traffic path 22 is interposed between two first traffic paths 21. The heat exchanger 11 thus comprises an alternation of first traffic paths 21 and second traffic paths 22.

[0145] It should be noted that in [Fig. 1], the first traffic paths 21 and the second traffic paths 22 are shown in counter-current flow. According to another embodiment, the traffic paths 21 and 22 are capable of being co-current.

[0146] Inside the heat transfer fluid circuit 5, the heat transfer fluid 6 flows from the pump 15 to the heat exchanger 11, then flows inside the heat exchanger 11 using the second circulation paths 22 to exchange heat with the refrigerant 4 present inside the first circulation paths 21, then flows inside the heat exchanger 14, then returns to the pump 15.

[0147] Inside the refrigerant circuit 3, the refrigerant 4 flows from the compressor 7 to the refrigerant / outside air heat exchanger 8, then to the expansion device 9. The refrigerant 4 then flows inside the heat exchanger 11 through the first circulation paths 21 in which the refrigerant 4 exchanges heat with the heat transfer fluid 6 present in the second circulation paths 22, then returns to the compressor 7.

[0148] It is noted at this stage of the description that, while the refrigerant 4 and the heat transfer fluid 6 are not interchangeable in what has just been said for obvious reasons of operation of the installation 2, in the rest of the description, what is said for the refrigerant is interchangeable with what is said for the heat transfer fluid, with regard to the inlets, outlets, circulation paths, etc... In other words, a refrigerant inlet inside the heat exchanger 11 can be transposed into a heat transfer fluid inlet.

[0149] According to a first variant of the heat exchanger 11 illustrated in [Fig.2], the heat exchanger 11 is globally parallelepiped-shaped and is bordered by a first cheek 100a and a second cheek 100b. The cheeks 100a and 100b are end walls of the heat exchanger 11. The first cheek 100a has a heat transfer fluid inlet 101 through which the heat transfer fluid 6 enters the heat exchanger 11. The first cheek 100a also has a heat transfer fluid outlet 102 through which the heat transfer fluid 6 is discharged from the heat exchanger 11. The second flow paths 22 extend between the heat transfer fluid inlet 101 and the heat transfer fluid outlet 102. The first cheek 100a also includes a refrigerant inlet 103 through which the refrigerant 4 enters the interior of the heat exchanger 11 and a refrigerant outlet 104 through which the refrigerant 4 is discharged from the heat exchanger 11. The first circulation paths 21 extend between the refrigerant inlet 103 and the refrigerant outlet 104.

[0150] The first cheek 100a and the second cheek 100b are generally rectangular. The first cheek 100a comprises two short sides 100c, 100g, including a first short side 100c and a second short side 100g, and two long sides lOOd. The first short side 100c extends between a first corner '00e and a second corner lOOf of the first cheek 100a. The inlet of the heat transfer fluid 101 is located near the first corner '00e and the outlet of the heat transfer fluid 102 is located near the second corner lOOf. We understand by proximity of the intake of the heat transfer fluid 101 and the first corner '00e the fact that a first distance Dl, taken between the first corner '00e and a center of the intake of the heat transfer fluid 101, is less than one third of a width L of the first cheek 100a, the width L corresponding to the length of the first short side 100c measured between the two corners 100c, lOOd of the first short side 100c.Similarly, the proximity of the heat transfer fluid outlet 102 and the second corner lOOf means that a second distance D2, taken between the second corner lOOf and a center of the heat transfer fluid outlet 102, is less than one third of said width L. Preferably, the first distance Dl and the second distance D2 are equal.

[0151] The refrigerant inlet 103 and the refrigerant outlet 104 are located near the second short side 100g. The proximity of the refrigerant inlet 103 to the second short side 100g means that a third distance D3, taken orthogonally between the second short side 100g and a center of the refrigerant inlet 103, is less than one-third of said width L. Similarly, the proximity of the refrigerant outlet 104 to the second short side 100g means that a fourth distance D4, taken orthogonally between the second short side 100g and a center of the refrigerant outlet 104, is less than one-third of said width L. Preferably, the third distance D3 and the fourth distance D4 are equal.

[0152] The refrigerant inlet 103 and the refrigerant outlet 104 are located near and on either side of a median longitudinal plane P6. The median longitudinal plane P6 extends parallel to the long sides 100d of the first cheek 100a, dividing the first cheek 100a into two equal portions. The proximity of the refrigerant inlet 103 and the median longitudinal plane P6 is understood to be The fact that a fifth distance D5, taken orthogonally between the median longitudinal plane P6 and the center of the refrigerant inlet 103, is less than one third of said width L. Similarly, it is understood by proximity of the refrigerant outlet 104 and the median longitudinal plane P6 that a sixth distance D6, taken orthogonally between the median longitudinal plane P6 and the center of the refrigerant outlet 104, is less than one third of said width L. Preferably, the fifth distance D5 and the sixth distance D6 are equal.

[0153] At this stage of the description, it is noted that the inlet of the heat transfer fluid 101 and the outlet of the heat transfer fluid 102 on the one hand and the inlet of the refrigerant fluid 103 and the outlet of the refrigerant fluid 104 on the other hand are located on either side of a median lateral plane P7 which divides the heat exchanger 11 into two equal portions, the median lateral plane P7 being parallel to the short sides 100c, 100g of the first cheek 100a.

[0154] The heat exchanger 11 is a plate heat exchanger comprising a plurality of plates 105a, 105b, including a first-type plate 105a, which is immediately adjacent to the first cheek 100a, and a plurality of second-type plates 105b. It is understood that the first-type plate 105a is adjacent to the first cheek 100a and rests against it. In other words, the first-type plate 105a is interposed between the first cheek 100a and a second-type plate 105b, the heat exchanger 11 then comprising, in the stack, only second-type plates 105b up to the second cheek 100b. Two plates 105a, 105b are nested one inside the other to jointly delimit a tube 123 which channels a circulation of the refrigerant fluid 4 or of the heat transfer fluid 6.Three plates 105a, 105b are nested one inside the other to jointly delimit two tubes 123, one tube 123 which channels a circulation of the refrigerant fluid 4 and one tube 123 which channels a circulation of the heat transfer fluid 6. .

[0155] In other words, the two plates 105a, 105b forming the tube 123 jointly delimit a channel 111a, 111b, of which a first channel 111a is dedicated to the circulation of the refrigerant fluid 4 and a second channel 111b is dedicated to the circulation of the heat transfer fluid 6. More particularly, one face of a plate 105a, 105b borders the first channel 111a for the circulation of the heat transfer fluid 4 and the other face of the same plate 105a, 105b borders the second channel 111b for the circulation of the heat transfer fluid 6. Thus, the plates 105a, 105b are arranged in such a way as to alternately configure the channels 111a for the circulation of the refrigerant fluid 4 and the channels 111b for the circulation of the heat transfer fluid 6.

[0156] In Figures 3 and 5, which respectively illustrate a first-type plate 105a and a second-type plate 105b, each plate 105a, 105b extends mainly along a longitudinal elongation axis Al. The plate 105a, 105b comprises a base 106 and at least one raised rim 107 surrounding the bottom 106. The bottom 106 extends within a bottom plane P5. The raised rim 107 is formed at the periphery of the bottom 106 and surrounds the bottom 106. The raised rim 107 intersects the bottom plane P5. It is understood that the plate 105a, 105b is arranged in a generally rectangular bathtub, the bottom of the bathtub being formed by the bottom 106 and the edges of the bathtub being formed by the raised rim 107.

[0157] Such plates 105a, 105b are intended to be stacked so that the bottoms 106 of the plates 105a, 105b are arranged parallel to each other in a distant and stepped superposition of the bottoms 106. The raised edges 107 of two plates 105a, 105b embedded one into the other are in contact and are intended to be brazed together to ensure a seal of the channel 111 thus provided between two adjacent plates 105a, 105b.

[0158] More specifically, the raised rim 107 comprises two longitudinal raised edges 108a, 108b, of which a first longitudinal raised edge 108a and a second longitudinal raised edge 108b are arranged opposite each other. The raised rim 107 also comprises two lateral raised edges 109a, 109b, of which a first lateral raised edge 109a and a second lateral raised edge 109b are arranged opposite each other.

[0159] The first raised lateral edge 109a extends in a first plane PI which intersects the bottom plane P5 and is secant with the longitudinal elongation axis AL. Opposite longitudinally to the first raised lateral edge 109a is the second raised lateral edge 109b which extends in a second plane P2, the second plane P2 intersecting the bottom plane P5 and being secant with the longitudinal elongation axis AL.

[0160] The first longitudinal raised edge 108a extends into a third plane P3 which intersects the bottom plane P5 and is secant with a lateral elongation axis A2 of the plate 105a, 105b, the lateral elongation axis A2 being orthogonal to the longitudinal elongation axis A1 and parallel to the bottom plane P5. The second longitudinal raised edge 108b extends into a fourth plane P4 which intersects the bottom plane P5 and is secant with the lateral elongation axis A2 of the plate 105a, 105b.

[0161] By way of example, the first plane P1 forms a first angle α with the background plane P5, which is between 91° and 140°, preferably between 91° and 95°. The second plane P2 forms a second angle θ with the background plane P5, which is between 91° and 140°, preferably between 91° and 95°. The third plane P3 forms a third angle θ with the background plane P5, which is between 91° and 140°, preferably between 91° and 95°. The fourth plane P4 forms a fourth angle θ with the background plane P5, which is between 91° and 140°, preferably between 91° and 95°. According to an alternative embodiment, the first angle a, second angle [3, third angle y and fourth angle ô are equal, within manufacturing tolerances.

[0162] The plate 105a, 105b, whether of the first or second type, comprises four openings 110a, 110b, of which two are of the first type 110a and two are of the second type 110b, which are ovoid or circular or of some other shape. The two first-type openings 110a are configured to communicate with one of the first traffic paths 21 provided on one side of the bottom 106, and the second-type openings 110b are configured to communicate with one of the second traffic paths 22 provided on the other side of the bottom 106.

[0163] The first type openings 110a are each surrounded by a collar 120, so that these first type openings 110a surrounded by this collar 120 extend in a plane offset from the bottom plane P5 in which the bottom 106 is inscribed. The second type openings 110b, free of collar, extend in the bottom plane P5.

[0164] The base 106 is provided with a plurality of protrusions 112 to disrupt the flow of the refrigerant 4 or the heat transfer fluid 6 in the first channel 11a. These protrusions 112 form obstacles to the laminar flow of the refrigerant 4 or the heat transfer fluid 6 in the first channel 11a. Preferably, the protrusions 112 have a frustoconical profile in cross-section in a lateral plane parallel to the median lateral plane P7 and / or in a plane parallel to the median longitudinal plane P6.

[0165] The base 106 includes a rib 113 which is arranged so that the first channel 111a has a U-shaped profile. The rib 113 is parallel to a first direction D of elongation of the longitudinal upturned edges 108a, 108b, the first direction D of elongation of the longitudinal upturned edges 108a, 108b being preferentially parallel to the longitudinal elongation axis Al of the plate 105a, 105b.

[0166] On [Fig.3], which illustrates a first type plate 105a, 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 first lateral upturned edge 109a which comprises the upturned rim 107. The second longitudinal end 115 is located at a non-zero seventh distance D7 from the upturned rim 107, the seventh distance D7 being taken between the second longitudinal end 115 and the second lateral upturned edge 109b, measured along the longitudinal elongation axis Al of the first type plate 105a. The first longitudinal end 114 of rib 113 and the second longitudinal end 115 of rib 113 are aligned along the first direction D parallel to the longitudinal elongation axis Al of the first-type plate 105a. In other words, the second longitudinal end 115 of the rib 113 is a free end free from contact with the raised edge 107.

[0167] These arrangements are such that the first channel 11a is formed into a U whose branches of the U are parallel to the longitudinal raised edges 108a, 108b of the first type plate 105a and are separated by the rib 113, and whose base of the U adjoins the second lateral edge 109b which is provided longitudinally opposite the first lateral edge 109a. The rib 113 is provided at an equal eighth distance D8 from the two longitudinal edges 108a, 108b of the plate 105a, 105b, the eighth distance D8 being measured between the rib 113, taken at its center, and one of the longitudinal raised edges 108a, 108b, perpendicular to the longitudinal elongation axis Al of the first type plate 105a.

[0168] According to one embodiment, the rib 113 is offset by a non-zero distance from the median longitudinal plane P6 of the first type plate 105a, the median longitudinal plane P6 being orthogonal to the bottom 106 and parallel to the longitudinal elongation axis Al of the first type plate 105a, the distance being measured between the rib 113, taken at its center, and the median longitudinal plane P6 perpendicular to the latter.

[0169] The median lateral plane P7 divides the first type plate 105a into a first zone ZI comprising the first raised lateral edge 109a and a second zone Z2 comprising the second raised lateral edge 109b. According to the present invention, the first zone ZI advantageously comprises the four openings 110a, 110b, that is to say the two first type openings 110a and the two second type openings 110b.

[0170] The first zone ZI has a first length L1 which is equal to a second length L2 of the second zone Z2, the first length L1 being measured between the first raised lateral edge 109a and the median lateral plane P7, the second length L2 being measured between the second raised lateral edge 109b, parallel to the longitudinal elongation axis AL

[0171] The two first-type openings 110a and the two second-type openings 110b are aligned along a first alignment axis A3, which is preferably parallel to the median lateral plane P7. It is understood that the respective centers of the two first-type openings 110a and the two second-type openings 110b are aligned along the first alignment axis A3.

[0172] The first alignment axis A3 is located at a first gap El between the first alignment axis A3 and the first lateral raised edge 109a which is less than 50% of the first length Ll, preferably less than 30%.

[0173] The openings 110a, 110b are arranged inside a third zone Z3 which is free of protrusion. Longitudinally, the third zone Z3 is bordered by the first raised lateral edge 109a and a first separation line XI which is parallel to the first raised lateral edge 109a and which is disposed at a second gap E2, provided between the first raised lateral edge 109a and the first separation line XI, which is less than 60% of the first length Ll, preferably less than 40%.

[0174] The first type plate 105a has a fourth zone Z4 which is bordered by the second raised lateral edge 109b and a second separation line X2. The second separation line X2 is parallel to the second raised lateral edge 109b and is located at a third gap E3, provided between the second raised lateral edge 109b and the second separation line X2, which is less than 60% of the first length L1, preferably less than 40%. Preferably, the second separation line X2 includes the second end 115 of the rib 113.

[0175] Within the fourth zone Z4, a first density of protuberances The density of protrusions 112 in zone Z4 is lower than that of a second protrusion density 112 in a fifth zone Z5, which is interposed between the fourth zone Z4 and the third zone Z3. It will be understood that the variation in protrusion density 112 from one zone to another is obtained either by increasing or decreasing the number of protrusions per unit area within one of the zones, or by modifying the volume of at least one protrusion within one of the zones. For example, the first protrusion density 112 in zone Z4 is 50% lower than the second protrusion density 112 in zone Z5.

[0176] Figures 4a, 4b, 4c and 4d illustrate respective variants of the first type plate 105a shown in [Fig.3], to show the different possible distributions of the openings 110a, 110b along the first alignment axis A3.

[0177] On [Fig.4a], the first type openings 110a, provided with the collar 120, are interposed between the second type openings 110b, which are collarless.

[0178] On [Fig.4b], the second type openings 110b, without a collar, are interposed between the first type openings 110a, provided with the collar 120.

[0179] On [Fig.4c] and 4d, the first type openings 110a and the second type openings 110b are aligned in alternating succession from one type to the other type.

[0180] In [Fig. 5], which illustrates a second-type plate 105b, the rib 213 extends between a first longitudinal end 214 and a second longitudinal end 215, the first longitudinal end 214 being in contact with the first raised lateral edge 109a that comprises the raised rim 107. The second longitudinal end 215 is in contact with the raised rim 107, and more particularly with the second raised lateral edge 109b. In other words, the rib 213 extends longitudinally between the two lateral edges 109a, 109b. The first longitudinal end 214 of rib 213 and the second longitudinal end 215 of rib 213 are aligned along the first direction D parallel to the longitudinal elongation axis Al of the second type plate 105b.

[0181] These arrangements are such that the first channel 211a delimited by the second type plate 105b and the first cheek 100a is formed into a double I. In other words, this first channel 21la of the heat exchanger 11, and only this one, comprises two parallel and sealed branches 21le, 21Id U. The branches 21le, 21Id are parallel to the longitudinal raised edges 108a, 108b of the second type plate 205a and are separated longitudinally by the rib 213.

[0182] According to an alternative embodiment, the rib 213 is offset by a non-zero distance from the median longitudinal plane P6 of the second type plate 105b, the median longitudinal plane P6 being orthogonal to the bottom 106 and parallel to the longitudinal elongation axis Al of the second type plate 105b, the distance being measured between the rib 113, taken at its center, and the median longitudinal plane P6 perpendicular to the latter.

[0183] The median lateral plane P7 divides the second type plate 105b into a first zone ZI comprising the first raised lateral edge 109a and a second zone Z2 comprising the second raised lateral edge 109b. According to the present invention, the first zone ZI advantageously comprises the four openings 110a, 110b, that is to say the two first type openings 110a and the two second type openings 110b.

[0184] The first zone ZI has a first length L1 which is equal to a second length L2 of the second zone Z2, the first length L1 being measured between the first raised lateral edge 109a and the median lateral plane P7, the second length L2 being measured between the second raised lateral edge 109b, parallel to the longitudinal elongation axis AL

[0185] The two first-type openings 110a and the two second-type openings 110b are aligned along a first alignment axis A3, which is preferably parallel to the median lateral plane P7. It is understood that the respective centers of the two first-type openings 110a and the two second-type openings 110b are aligned along the first alignment axis A3.

[0186] The first alignment axis A3 is located at a first gap El between the first alignment axis A3 and the first raised lateral edge 109a which is less than 50% of the first length Ll, preferably less than 30%.

[0187] The openings 110a, 110b are arranged within a third zone Z3 which is free of protrusion. Longitudinally, the third zone Z3 is bounded by the first lateral raised edge 109a and a first separation line XI which is parallel to the first lateral raised edge 109a and which is arranged at a second gap E2, located between the first raised lateral edge 109a and the first separation line XI, which is less than 60% of the first length Ll, preferably less than 40%.

[0188] The second type plate 105b has a sixth zone Z6 which is bordered by the second raised lateral edge 109b and a third separation line X3. The third separation line X3 is parallel to the second raised lateral edge 109b and is located at a fourth gap E4, formed between the second raised lateral edge 109b and the second separation line X2, which is less than 60% of the first length L1, preferably less than 40%. Preferably, the second separation line X2 includes the second end 115 of the rib 113. Inside the sixth zone Z6, the bottom 106 of the second type plate 105b is free of protrusion.

[0189] Figures 6a, 6b, 6c and 6d illustrate respective variants of the second type plate 105b shown in [Fig.5], to show the different possible distributions of the openings 110a, 110b along the alignment axis A3.

[0190] In [Fig. 6a], the first type openings 110a, fitted with the collar 120, are interposed between the second type 110b openings, free of collar.

[0191] On [Fig.6b], the second type openings 110b, without a collar, are interposed between the first type openings 110a, provided with the collar 120.

[0192] On [Fig.6c] and 6d, the first type openings 110a and the second type openings 110b are aligned in alternating succession from one type to the other type.

[0193] According to a second embodiment of the heat exchanger 11 illustrated in [Fig.7], the heat exchanger 11 is globally parallelepiped-shaped and is bordered by a first cheek 100a and a second cheek 100b. The cheeks 100a, 100b are end walls of the heat exchanger 11. The first cheek 100a is provided with a heat transfer fluid inlet 101 through which the heat transfer fluid 6 enters the interior of the heat exchanger 11. The first cheek 100a is also provided with a heat transfer fluid outlet 102 through which the heat transfer fluid 6 is discharged from the heat exchanger 11. The second flow paths 22 extend between the heat transfer fluid inlet 101 and the heat transfer fluid outlet 102.The first cheek 100a also includes a refrigerant inlet 103 through which the refrigerant 4 enters the heat exchanger 11 and a refrigerant outlet 104 through which the refrigerant 4 is discharged from the heat exchanger 11. The first flow paths 21 extend between the refrigerant inlet 103 and the refrigerant outlet 104.

[0194] The first cheek 100a and the second cheek 100b are generally rectangular. The first cheek 100a comprises two short sides 100c, 100g, including a first short side 100c and a second short side 100g, and two long sides lOOd. The first short side 100c extends between a first corner '00e and a second corner lOOf of the first cheek 100a. The inlet of the heat transfer fluid 101 is located near the first corner '00e and the outlet of the heat transfer fluid 102 is located near the second corner lOOf. We understand by proximity of the intake of the heat transfer fluid 101 and the first corner '00e the fact that a first distance Dl, taken between the first corner '00e and a center of the intake of the heat transfer fluid 101, is less than one third of a width L of the first cheek 100a, the width L corresponding to the length of the first short side 100c measured between the two corners 100c, lOOd of the first short side 100c.Similarly, the proximity of the heat transfer fluid outlet 102 and the second corner lOOf means that a second distance D2, taken between the second corner lOOf and a center of the heat transfer fluid outlet 102, is less than one third of said width L. Preferably, the first distance Dl and the second distance D2 are equal.

[0195] The refrigerant inlet 103 and the refrigerant outlet 104 are located near the second short side 100g. Proximity of the refrigerant inlet 103 and the second short side 100g means that a third distance D3, taken orthogonally between the second short side 100g and a center of the refrigerant inlet 103, is less than one-third of said width L. Similarly, proximity of the refrigerant outlet 104 and the second short side 100g means that a fourth distance D4, taken orthogonally between the second short side 100g and a center of the refrigerant outlet 104, is less than one-third of said width L. Preferably, the third distance D3 and the fourth distance D4 are equal.

[0196] The refrigerant inlet 103 and the refrigerant outlet 104 are arranged close to and on either side of a median longitudinal plane P6. The median longitudinal plane P6 extends parallel to the long sides 100d of the first cheek 100a, dividing the first cheek 100a into two equal portions. The proximity of the refrigerant inlet 103 to the median longitudinal plane P6 means that a fifth distance D5, taken orthogonally between the median longitudinal plane P6 and the center of the refrigerant inlet 103, is less than one-third of said width L. Similarly, the proximity of the refrigerant outlet 104 to the median longitudinal plane P6 means that a sixth distance D6, taken orthogonally between the median longitudinal plane P6 and the center of the refrigerant fluid evacuation 104, is less than one third of said width L. Preferably, the fifth distance D5 and the sixth distance D6 are equal.

[0197] At this stage of the description, it is noted that the inlet of the heat transfer fluid 101 and the outlet of the heat transfer fluid 102 on the one hand and the inlet of the refrigerant fluid 103 and the outlet of the refrigerant fluid 104 on the other hand are located on either side of a median lateral plane P7 which divides the heat exchanger 11 into two equal portions, the median lateral plane P7 being parallel to the short sides 100c, 100g of the first cheek 100a.

[0198] It is also noted that the first cheek 100a is provided with two external channels lOOh, lOOi, of which a first external channel lOOh extends between the inlet of the heat transfer fluid 101 and a first inlet opening lOOj of the heat transfer fluid 6 inside the heat exchanger 11 and of which a second external channel lOOi extends between a first outlet opening 100k of the heat transfer fluid 6 outside the heat exchanger 11 and the outlet of the heat transfer fluid 102. Preferably, the first external channel lOOh and the second external channel lOOi are brazed onto the first cheek 100a. Compared with the first embodiment of the heat exchanger described above, the external channels lOOh, lOOi externally provide the same function as branches 21 le, 21 Id of the heat exchanger 11 according to the first embodiment.

[0199] The heat exchanger 11 is a plate heat exchanger comprising a plurality of first plates 105a, such as those described above. In other words, according to the second embodiment of the heat exchanger 11, the heat exchanger 11 does not include any second-type plates. Reference can therefore be made to the descriptions in Figures 3, 4a, 4b, 4c, and 4d, which also describe the plates 105a of the heat exchanger 11 according to both the first and second embodiments.

[0200] According to a third embodiment of the heat exchanger 11 illustrated in figures 8 and 9, the heat exchanger 11 is globally parallelepiped-shaped and is bordered by a first cheek 100a and a second cheek 100b. The cheeks 100a, 100b are end walls of the heat exchanger 11. The first cheek 100a is provided with a heat transfer fluid inlet 101 through which the heat transfer fluid 6 enters the interior of the heat exchanger 11. The first cheek 100a is also provided with a heat transfer fluid outlet 102 through which the heat transfer fluid 6 is discharged from the heat exchanger 11. The second flow paths 22 extend between the heat transfer fluid inlet 101 and the heat transfer fluid outlet 102.The first cheek 100a also includes a refrigerant fluid inlet 103 through which the refrigerant fluid 4 enters the interior of the heat exchanger 11 and a refrigerant fluid outlet 104 through which the refrigerant fluid. 4 is discharged from the heat exchanger 11. The first circulation paths 21 extend between the refrigerant inlet 103 and the refrigerant outlet 104.

[0201] The first cheek 100a and the second cheek 100b are generally rectangular. The first cheek 100a comprises two short sides 100c, 100g, of which a first short side 100c and a second short side 100g, and two long sides 100d.

[0202] The inlet of the heat transfer fluid 101, the outlet of the heat transfer fluid 102, the inlet of the refrigerant 103 and the outlet of the refrigerant 104 are aligned along a second alignment axis A4 which is preferably parallel to the median lateral plane P7. It is understood that the respective centers of the inlet of the heat transfer fluid 101, the outlet of the heat transfer fluid 102, the inlet of the refrigerant 103 and the outlet of the refrigerant 104 are aligned along the second alignment axis A4.

[0203] On [Fig.9], the second alignment axis A4 is located at a fifth gap E5 provided between the second alignment axis A4 and the first second small side 100g which is less than 50% of the first length Ll, preferably less than 30%.

[0204] It is noted that, in the illustrated example, the first inlet opening lOOj of the heat transfer fluid 6 and the first outlet opening 100k are collarless, while a second inlet opening 1001 of the refrigerant fluid 4 and a second outlet opening 100m of the refrigerant fluid 4 are provided with a collar 120. The second inlet opening 1001 of the refrigerant fluid 4 is in fluidic relationship with the inlet of the refrigerant fluid 103 and the second outlet opening 100m is in fluidic relationship with the outlet of the refrigerant fluid 104.

[0205] The heat exchanger 11 is a plate heat exchanger comprising a plurality of first plates 105a, such as those described above. In other words, according to the third embodiment of the heat exchanger 11, the heat exchanger 11 does not include any second-type plates. Reference can therefore be made to the descriptions in Figures 3, 4a, 4b, 4c, and 4d, which also describe the plates 105a of the heat exchanger 11 according to the first and third embodiments.

[0206] According to all the above variants, the plate 105a, 105b is made of a metallic material, suitable for being stamped to form in particular the protrusions 112 and the rib 113 by stamping the plate 105a, 105b, the metallic material being chosen from thermally conductive metallic materials, in particular aluminium or aluminium alloy.

[0207] We will now describe, with reference to figures 10 to 16, a heat exchanger 11 conforming to embodiments of the invention.

[0208] In these embodiments of the invention, the heat exchanger 11 comprises a plurality of stacked plates 300, 302, 304, one of these plates 300, 302, 304 being configured to delimit a circulation channel 306, 307, 309 of a fluid 4, 6.

[0209] The plate 300, 302, 400 each has a pair of openings 310, 311, 410 configured so that the fluid 4, 6 enters and exits the circulation channel 306, 307, 406.

[0210] The plate 300, 302, 400 extends mainly along a longitudinal elongation axis A10 between a first end 312, 412 and a second end 314, 414.

[0211] The first and second ends 312, 412 and 314, 414 are connected to each other by two raised edges 317, 417 of the plate 300, 302, 400.

[0212] The plate 300, 302, 400 comprises, in the channel 306, 307, 309 between the fluid openings 310, 311, 410, a plurality of low pressure loss zones 320, 420, and a plurality of high pressure loss zones 330, 331, 332, 430, these zones being configured to promote a balanced distribution of the fluid over the entire width of this channel 306, 307, 309.

[0213] The term “fluid” means the refrigerant fluid 4 or the heat transfer fluid 6 intended to circulate in the circulation channel.

[0214] The "low pressure loss zone" 320, 420 and the "high pressure loss zone" 330, 331, 332, 430 are zones which generate different pressure losses.

[0215] The "highest pressure loss" zone 330, 331, 332, 430 relative to the "lowest pressure loss" zone 320, 420 can be achieved for example by using a higher density of the flow disturbance pattern 350, 450 in the "highest pressure loss" zone or by using at least one pattern creating more resistance to flow.

[0216] The consequence is then a modification of the fluid flow in the plate 300, 302, 400. For example, if the fluid 4, 6 arrives in a zone of high pressure drop 330, 331, 332, 430, part of the flow will bypass this zone, supplying more of the zone of lower pressure drop 320, 420. This modification corresponds to the pressure balancing over the passage cross-section or channel width y_tot of the fluid 4, 6. In the case where the zone of high pressure drop 330, 331, 332, 430 is located over the entire width of the passage cross-section, the fluid 4, 6 will tend to distribute itself homogeneously over this entire width y_tot, corresponding to the state where the pressure in this section is homogeneous.

[0217] Thanks to the invention, the fluid 4, 6 is distributed in a balanced way over the entire width of the channel y_tot between the fluid openings 310, 311, 410.

[0218] A "balanced distribution" of the fluid 4, 6 over the entire width of the plate 300, 302, 400 is understood to mean a uniform distribution of the fluid 4, 6 over the entire width of a The flow zone of plate 301, 401. With reference in particular to [Fig. 13], the flow zone of plate 301, 401 may be free of areas where fluid openings 410 are present. The flow zone of plate 301, 401 may have a substantially rectangular shape with a length x_tot and a width z_tot.

[0219] In this way, the fluid 4, 6 can be distributed from areas where the flow is abundant, for example in areas near fluid opening to areas where the flow is insufficient, for example towards outer corners 340, 440 of the plate 300, 302, 400.

[0220] Thus, the invention makes it possible to have a satisfactory flow of fluid over the entire width of the fluid flow zone of the plate 301, 401 and to have better heat exchange over a larger surface of the plate 300, 302, 400 in particular on external corners 340, 440 of the plate 300, 302, 400.

[0221] In this way, poor fluid distribution within the circulation channel 306, 307, 406 is reduced. Consequently, the efficiency of heat transfer between the refrigerant 4 and the heat transfer fluid 6 is increased.

[0222] As illustrated in particular in Figures 10 to 12, the heat exchanger 11 comprises:

[0223] - a first plate 300 configured to delimit the first traffic channel 306 of a first fluid 4, and

[0224] - a second plate 302 configured to delimit the second channel of circulation 307 of a second fluid 6.

[0225] The first fluid 4 can be, for example, a refrigerant fluid 4 and the second fluid 6 can be a heat transfer fluid 6. Of course, the first fluid 6 can be a heat transfer fluid 6 and the second fluid 4 can be a refrigerant fluid 4.

[0226] The first and second plates 300, 302 each have a pair of openings 310, 311 configured so that the first fluid 4, 6 and the second fluid 4, 6 enter and exit respectively from the first circulation channel 306 and the second circulation channel 307.

[0227] Still in the examples of figures 10 to 12, the high pressure loss zones 330, 331, 332 are surrounded, upstream and downstream, by low pressure loss zones 320. The low pressure loss zones 320 comprise a plurality of flow perturbators 350 in the form of protrusions 350.

[0228] Thus, the heat exchanger 11 allows for a homogenization of the fluid circulation velocity within the circulation channel 306, 307, 406. In this way, heat transfer is optimized, for example between the refrigerant 4 and the heat transfer fluid 6.

[0229] As particularly illustrated in figures 10 to 11, the high pressure loss zones 330, 331 extend over the entire width of the channel 306.

[0230] As seen in [Fig. 10], the high pressure loss zones 330 have undulating reliefs 370, called corrugations 370. These undulating reliefs 370 are made in one piece with the plate 300, 302.

[0231] As illustrated in [Fig.1 1], the high pressure loss zones 331 have flat fins 371. The fins 371 are added parts on the plate 300, 302, in particular welded or brazed to the plate 300, 302.

[0232] As illustrated in [Fig.12], the high pressure loss zone 332 extends over a portion of the width of the channel 306.

[0233] Still in the example of [Fig. 12], the high pressure loss zone 332 extends over a portion of the width of the channel 306 whose width is between 50 and 90% of the width of the channel 306, preferably between 60 and 80% of the channel.

[0234] It can be predicted that the high pressure loss zone 330, 331, 332 includes the undulating reliefs 730, the fins 731 and / or the alternating crenellated reliefs 732.

[0235] The high pressure loss zone 332 has alternating crenellation reliefs, called offsets 372. These alternating crenellation reliefs 372 are added parts on the plate 300, 302, welded or brazed onto the plate 300, 302.

[0236] As can be seen in figures 10 to 16, the plate 300, 302, 400 includes a rib 313, 413 between the pair of fluid openings 310, 311, 410 to create a U-shaped circulation between the pair of fluid openings 310, 311, 410.

[0237] As illustrated in Figures 10 to 12, the rib 313 has a wavy shape. The main axis of the rib of the first plate 300 and the main axis of the rib of the second plate 302 are arranged so as to overlap.

[0238] The fluid openings 310, 311 of the first and second plates 300, 302 are arranged symmetrically from the first plate 300 to the second plate 302 with respect to the plane P10 perpendicular to the main axis of the rib NI of one of the plates 300, 302.

[0239] With reference to figures 10 and 12, the plate 300, 302 has the high pressure loss zones 330, 332 which are distributed on either side of the rib 313.

[0240] In particular with reference to [Fig. 10], the high pressure loss zones 330 are aligned perpendicularly to the main axis of the NI rib.

[0241] Still in the examples of figures 10 and 12, the high pressure loss zones 330, 332 are symmetrical with respect to the rib 313.

[0242] With reference to [Fig. 11], the high pressure loss zones 331 on either side of the rib are offset from each other along the principal axis of the rib NI. The offset between the high pressure loss zones 331 is between 5 and 100% of the dimensions of the high pressure loss zones 331, preferably between 10 and 50% of the dimensions of the high pressure loss zones 331.

[0243] Figures 13 to 16 show other embodiments of the heat exchanger 11.

[0244] The plate 400 has a plurality of low pressure loss zones 420, called bypass zones 420. With reference to Figures 13, 15 and 16, the plate 400 has three low pressure loss zones 420.

[0245] These low pressure drop zones 420 have a rectangular shape.

[0246] Referring for example to figures 13 to 16, the low pressure loss zones 420 are surrounded, upstream and downstream, by high pressure loss zones 430.

[0247] The high pressure loss zones 430 include a plurality of flow perturbators 450.

[0248] Of course, referring to figures 10 to 12, it can be predicted that the high pressure loss zones 330, 331, 332 also include a plurality of flow perturbators 350.

[0249] The rib 413 has a rectangular shape. This rib 413 has a main axis N2. These low pressure loss zones 420 are located on the outside of the bend of the U-shaped channel 406 and these low pressure loss zones 420 are free of flow disruptors 450.

[0250] The two of the low pressure loss zones 420 are located at the opposite raised edges 417 of the plate 400.

[0251] With particular reference to Figures 14 and 15, the two of the low pressure loss zones 420 are located opposite each other.

[0252] With reference to [Fig. 14], the plate 400 has four low pressure loss zones 420. One of the opposite edges 417 of the plate 400 has at least two low pressure loss zones 420. These two low pressure loss zones 420 of the same opposite edge 417 are aligned with respect to the longitudinal elongation axis A10.

[0253] With particular reference to Figures 13 and 16, the two of the low pressure loss zones 420 are offset from each other with respect to the main axis of rib N2.

[0254] One of the low pressure loss zones 420 is located at one of the two ends of the plate 414, namely the second end of the plate 414.

[0255] The ratio between the horizontal length, x_bypass, of the low pressure loss zone when said zone is oriented parallel to the longitudinal elongation axis A10 and the total length of a fluid flow zone of the plate, x_tot, is greater than 20% (x_bypass / x_tot *100 > 20%)

[0256] The ratio between the vertical length, z_bypass, of the low pressure loss zone when said zone is oriented perpendicular to the longitudinal elongation axis A10 and the total width of the plate's fluid flow zone, z_tot, is greater than 20% (z_bypass / z_tot *100 > 20%).

[0257] The ratio between the width of the low pressure loss zone 420, y_bypass, when said zone 420 is oriented parallel to the longitudinal elongation axis A10 and the channel width, y_tot, is between 5% and 20%.

[0258] For all embodiments described in the application, the heat exchanger 11 can form an evaporator.

[0259] As just described, the invention achieves the goals it set for itself, by making it possible to homogenize heat exchanges on the circulation paths of the refrigerant and the heat transfer fluid, by eliminating in particular the restrictions on the passage of the refrigerant and the heat transfer fluid of the plates of the prior art.

[0260] The invention is not limited, however, to the means and configurations exclusively described and illustrated, and also applies to all equivalent means or configurations and to any combination of such means or configurations. In particular, although the invention has been described here in its application to a refrigerant / heat transfer fluid heat exchanger, it is understood 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

Demands

1. A heat exchanger (11) comprising a plurality of stacked plates (300, 302, 400), one of these plates (300, 302, 400) being configured to delimit at least one circulation channel (306, 307, 406) for a fluid (4, 6), the plate (300, 302, 400) comprising at least one pair of fluid openings (310, 311, 410) configured for the fluid (4, 6) to enter and exit the circulation channel (310, 311, 410), the plate (300, 302, 400) extending principally along a longitudinal elongation axis (A10) between a first end (312, 412) and a second end (314, 414), the plate (300, 302, 400) comprising, in the channel (306, 307, 406) between the fluid openings (310, 311, 410), at least one low pressure loss zone (320, 420) and at least one high pressure loss zone (330, 331, 332, 430), these zones being configured to promote a balanced distribution of the fluid (4, 6) over the entire width of this channel (306, 307, 406).characterized in that the ratio between the horizontal length, x_bypass, of the low pressure loss zone (420) when said zone is oriented parallel to the longitudinal elongation axis and the total length of a fluid flow zone (301, 401) of the plate, x_tot, is greater than 20% (x_bypass / x_tot *100 > 20%).

2. Exchanger (11) according to claim 1, wherein the plate (300, 302, 400) includes a rib (313, 413) between the pair of fluid openings (310, 311, 410) to create a U-shaped circulation between the pair of fluid openings (310, 311, 410).

3. Exchanger (11) according to any one of the preceding claims, wherein the ratio between the vertical length, z_bypass, of the low pressure loss zone when said zone is oriented perpendicular to the longitudinal elongation axis and the total width of the fluid flow zone (301, 401) of the plate, z_tot, is greater than 20% (z_bypass / z_tot *100 > 20%).

4. Exchanger (11) according to any one of the preceding claims, wherein the high pressure loss zone (330, 331, 332) comprises the undulating reliefs (730), the fins (731) and / or the alternating crenellated reliefs (732).

5. Heat exchanger (11) according to any one of the preceding claims, wherein the low pressure drop zone (420) has a rectangular shape.

6. Exchanger (11) according to the preceding claim, wherein the ratio between the width of the low pressure loss zone (420), y_bypass, when said zone (420) is oriented parallel to the longitudinal elongation axis (A 10) and the channel width, y_tot, is between 5% and 20%.

7. Exchanger (11) according to any one of the preceding claims, wherein the high pressure drop zone (330, 331, 332, 430) comprises a plurality of flow disruptors (350; 450).

8. Exchanger (11) according to any one of the preceding claims, wherein the high pressure loss zone (330, 331, 332) is surrounded, in particular upstream and downstream, by low pressure loss zones (320).

9. Exchanger (11) according to claim 8, wherein the low pressure drop zone (320) comprises a plurality of flow disruptors (350), in particular in the form of protrusions (350).

10. Heat exchanger (11) according to any one of claims 1 to 7, wherein at least one of the low pressure loss zones (420) is surrounded, in particular upstream and downstream, by high pressure loss zones (430).

11. Exchanger (11) according to claim 10, wherein the low pressure drop zone (420) is free from flow disruptors (450).

Images