Heat exchanger plate with fluid flow disrupting elements

Abstract

The present invention relates to a plate (10) of a heat exchanger (1) having two opposite longitudinal edges connected to one another by two lateral edges (16), these longitudinal and lateral edges (16) surrounding a bottom wall (24), an angle (α, α1, α2) measured between this bottom wall (24) and any one of the edges (16) being comprised between 103.5° and 109.5°, a thickness of the plate (10) being comprised between 0.20 mm and 0.45 mm, the bottom wall (24) being equipped with fluid flow disrupting elements (40), these fluid flow disrupting elements (40) having a vertical dimension (D, D1, D2) comprised between 0.75 mm and 1.15 mm.

Description

[0001] Plate for heat exchanger with fluid flow disruptors

[0002] The present invention relates to the field of heat exchangers, and more particularly to such heat exchangers which are equipped with fluid flow disruptors.

[0003] These heat exchangers can, for example, be fitted to a vehicle. They are then arranged within this vehicle to allow the thermal regulation of a first fluid circulating in a first space thanks to the circulation of a second fluid in a second space separate from the first space, so that the two fluids do not mix. The fluids can in particular be a refrigerant circulating within an air conditioning loop of the vehicle or a coolant intended to regulate the temperature of a thermal engine.

[0004] Within heat exchangers and the thermodynamic circuits to which they are attached, fluids circulate by dissipating or absorbing thermal energy. The efficiency of heat exchangers and thermodynamic circuits is mainly determined by the heat exchanges between the fluids flowing through them. Therefore, the design of heat exchangers in which the heat exchanges between the fluids circulating within them are optimized is sought. To this end, it is known to equip heat exchangers with fluid flow disturbance devices, so as to increase the heat exchanges between the fluids.

[0005] One type of heat exchanger used in the automotive industry is a plate heat exchanger, consisting of a stack of plates that are joined together by brazing and in which the spaces remaining between two adjacent plates after brazing define fluid circulation zones. These circulation zones are normally adapted to the fluids that flow through them, which implies the existence of several different types of plates. A technical problem lies in the fact that the means of production and storage of these plates are different, which complicates the logistical management during the manufacture of these plate heat exchangers.The present invention aims to overcome this drawback by proposing a heat exchanger plate whose fluid flow disturbance devices are configured to optimize the disturbance of the circulation of fluids on the one hand, while offering improved mechanical resistance within the heat exchanger with which the plate is fitted, the dimensions of these plates being configured so that they adapt, in particular by deformation, to the height of the fluid circulation space which is in particular defined by the disturbance devices.

[0006] The main subject of the present invention is thus a heat exchanger plate having a bathtub shape with two opposite longitudinal edges connected to each other by two lateral edges, these longitudinal and lateral edges surrounding a bottom wall of the plate, an angle measured between this bottom wall and any one of the edges being between 103.5 0and 109.5°, a thickness of the bottom wall being between 0.20 mm and 0.45 mm, the bottom wall being equipped with fluid flow disruptors, at least one of these fluid flow disruptors having a vertical dimension measured within a volume delimited by the bottom wall and the edges between 0.75 mm and 1.15 mm.

[0007] The heat exchanger plate according to the invention is configured for fluid circulation, such circulation making it possible to optimize heat exchanges via the fluid flow disruptors. The fluid flow disruptors are deformations of the bottom wall. The fluid circulates within a volume of the heat exchanger plate, which is delimited on the one hand by a bottom wall, from which the fluid flow disruptors protrude, and on the other hand by longitudinal and lateral edges which extend in planes intersecting the bottom wall. These intersecting planes are not necessarily perpendicular to the bottom wall, which gives the heat exchanger plate its bathtub shape.

[0008] More particularly, an angle measured between the bottom wall and any one of the edges, i.e. either a longitudinal edge or a lateral edge, is between 103.5 0 and 109.50 ; preferably, this angle is between 105 0 and 108 0 ; still preferably, this angle is between 105.5 0 and 107.5 °-

[0009] The bottom wall has a determined thickness, this thickness corresponding to its vertical dimension measured between a first face of the plate and a second face of the plate. Such a dimension is measured along a vertical direction which extends perpendicular to a plane in which the bottom wall mainly extends. Preferably, the thickness of the plate is between 0.20 mm and 0.45 mm, and it is ideally between 0.27 mm and 0.35 mm.

[0010] A vertical dimension of the fluid flow disruptors, which corresponds to their size measured in the vertical direction, is also predetermined. It is thus between 0.75 mm and 1.15 mm. It is understood that the fluid flow disruptors protrude from a plane in which the bottom wall extends and extend within a space delimited between the longitudinal and lateral edges, i.e. within the volume of the heat exchanger plate.

[0011] According to a characteristic of the invention, the vertical dimension of the fluid flow disruptors is a first vertical dimension between 0.75 mm and 0.85 mm.

[0012] According to another characteristic of the invention, the vertical dimension of the fluid flow disruptors is a second vertical dimension between 1.05 mm and 1.15 mm.

[0013] Thus, the fluid flow disruptors may have either a first vertical dimension, between 0.75 and 0.85 mm, or a second vertical dimension, between 1.05 and 1.15 mm; it is understood that these two distinct vertical dimensions, which correspond to the heights of the fluid flow disruptors, relate to two possible embodiments of the heat exchanger plate.

[0014] According to one feature, the bottom wall is equipped with at least four fluid distribution openings, each of these fluid distribution openings being arranged in the vicinity of a junction between a longitudinal edge and a lateral edge. These fluid distribution openings have the role of conveying or discharging fluid to / from the volume of the heat exchange plate. These fluid distribution openings are arranged on the plate such that there is a fluid distribution opening at each corner of this plate.

[0015] According to a feature of the invention, the fluid flow disruptors comprise at least one truncated dome extending between a base and a top.

[0016] Such a shape of the truncated domes is appreciated according to a sectional view, which here corresponds to a vertical cutting plane. These truncated domes extend between a base and a top, their base corresponding to their portion which joins the bottom wall while their top is the portion most distant from this plane, the top forming a free end of the truncated dome, before brazing of the heat exchanger. The top of the truncated dome is a flat part, preferably extending parallel to the bottom wall.

[0017] Fluid flow disruptors are deformations, for example by stamping, of the bottom wall. The mechanical strength of the heat exchanger plate is particularly dependent on the material thinning obtained during the deformation of the bottom wall to obtain these fluid flow disruptors.

[0018] According to one characteristic, a maximum diameter of the truncated dome measured at its base is 4.5 mm.

[0019] According to another characteristic of the invention, a minimum diameter of the truncated dome measured at its summit is 2 mm.

[0020] We understand here that the base of the truncated domes, that is to say their foundation, is circular and potentially has a diameter greater than its summit, which is also circular.

[0021] According to one feature, the bottom wall is equipped with a separating strip which extends from one of the side edges towards the other side edge, without however being in contact with the latter. According to one feature, the separating strip has a sinusoidal shape.

[0022] Like fluid flow disruptors, the separation strip has the effect of optimizing heat exchanges within the heat exchanger plate by increasing the path of the fluid in the volume of this plate.

[0023] The invention further relates, according to a first embodiment, to a heat exchanger configured to carry out a heat exchange between a first fluid and a second fluid, this heat exchanger comprising first plates as mentioned previously, i.e. having the first vertical dimension, and second plates as mentioned previously, i.e. having the second vertical dimension.

[0024] According to one aspect of the invention, the first and second fluids carrying out a heat exchange could be, respectively, a heat transfer fluid, of the dielectric type, a cooling fluid such as water or a mixture of water and ethylene glycol, and a refrigerant fluid, such as Ri34a, Ri234yf or R744.

[0025] The first plates and second plates then constitute a heating body within the heat exchanger, this heating body corresponding to its portion where the fluids circulate and therefore where the heat exchanges take place. Within the heat exchanger according to this first embodiment, a first fluid and another second fluid circulate respectively between two adjacent plates, for example so as to achieve an alternation between the circulation zone of the first fluid and the circulation zone of the second fluid, these circulation zones being delimited vertically by the bottom walls of the adjacent plates. Such a heat exchanger here has first plates whose height of the fluid flow disruptors is between 0.75 and 0.85 mm, and second plates whose height of the fluid flow disruptors is between 1.05 and 1.15 mm, installed alternately.Within a single heat exchanger, the spacings between the plates constituting it therefore have variable vertical dimensions. Such a combination of first and second plates offers the heat exchanger dimensional flexibility with regard to its circulation zones. It is thus possible, for example, to obtain a circulation zone for the first fluid greater than a circulation zone for the second fluid, or vice versa.

[0026] According to this first embodiment, the angle measured between the bottom wall and any one of the edges is between 105 0 and 108°.

[0027] Preferably, this angle is between 105.5 0 and 107.5°- Such an angle provides flexibility which allows the edge of the plates having the first vertical dimension or the second vertical dimension to be deformed, while ensuring sealing between these plates at least at their edge.

[0028] Alternatively and according to a second embodiment, the invention relates to a heat exchanger configured to carry out a heat exchange between a first fluid and a second fluid, this heat exchanger comprising a heating body consisting solely of plates as mentioned previously, that is to say having the first vertical dimension.

[0029] Here, the heat exchanger has a heating body, that is to say a portion dedicated to heat exchanges, consisting exclusively of first plates, that is to say plates whose fluid flow disruptors have a vertical dimension of between 0.75 and 0.85 mm.

[0030] According to this second embodiment, the angle measured between the bottom wall and any one of the edges is between 106.5 0and 109.5° - This angle is particularly suitable for ensuring the stacking of plates presenting the first vertical dimension, as well as the sealing between two plates, at least at the level of their edges.

[0031] According to a third embodiment, the invention intends to cover a heat exchanger configured to carry out a heat exchange between a first fluid and a second fluid, this heat exchanger comprising a heating body consisting solely of plates as mentioned previously, that is to say having the second vertical dimension.

[0032] Here, the heat exchanger has a heating body, that is to say a portion dedicated to heat exchanges, consisting exclusively of second plates, that is to say plates whose fluid flow disruptors have a vertical dimension of between 1.05 and 1.15 mm.

[0033] According to this third embodiment, the angle measured between the bottom wall and any of the edges is between 103.5 0 and 106.5° - This angle is particularly suitable for ensuring the stacking of plates with the second vertical dimension, as well as the sealing between two plates, at least at their edges.

[0034] According to another feature, the plates are assembled by brazing.

[0035] Brazing ensures the sealing of the heat exchanger, the first fluid and the second fluid thus having separate and non-communicating circulation zones, these zones also being sealed from the external environment of the heat exchanger.

[0036] According to one feature, the plates are stacked in a stacking direction, the fluid flow disruptors of two adjacent plates in the stacking direction being arranged in a staggered manner.

[0037] The stacking direction corresponds to the vertical direction; this is the direction in which the plates are superimposed on each other so that their respective longitudinal and lateral edges are in contact. Here, the term “arranged in a staggered pattern” means that the fluid flow disruptors of a given plate are not vertically aligned with the fluid flow disruptors of the plate(s) adjacent to it, in particular when these plates are viewed along a vertical section that passes through three fluid flow disruptors. In other words, the fluid flow disruptors of one plate do not overlap the fluid flow disruptors of the adjacent plate when these plates are viewed from above. According to another characteristic, the tops of the fluid flow disruptors of a plate are in contact with the bottom wall of the plate adjacent to it in the stacking direction.

[0038] The fluid flow disruptors are thus points of contact between two adjacent plates. Such a connection also helps to delimit a path for the circulation of the fluid within the circulation zone of the heat exchanger plate, and therefore disrupts the flow of this fluid in the volume of the plate. Furthermore, the contact between the fluid flow disruptors of a first plate and the bottom wall of a plate superimposed on it contributes to the mechanical reinforcement of the heat exchanger, ensuring the joining of the two plates and allowing a distribution of forces over all the points of contact formed by the fluid flow disruptors.

[0039] Other characteristics, details and advantages of the invention will emerge more clearly on reading the description which follows on the one hand, and examples of embodiment given for informational and non-limiting purposes with reference to the appended drawings on the other hand, in which:

[0040] [Fig. 1] illustrates, schematically, a heat exchanger according to the invention, in a perspective view;

[0041] [Fig. 2] is a sectional view of the exchanger of Figure 1, according to a first embodiment;

[0042] [Fig. 3] is a perspective view of two plates of the heat exchanger of Fig. 1;

[0043] [Fig. 4] is a sectional view of the exchanger of Figure 1 according to the first embodiment, in a close-up view;

[0044] [Fig. 5] is a sectional view of the exchanger of Figure 1 according to a second embodiment, in a close-up view;

[0045] [Fig. 6] is a sectional view of the exchanger of Figure 1 according to a third embodiment, in a close-up view.

[0046] The features, variants and different embodiments of the invention may be combined with each other in various combinations, provided that they are not incompatible or mutually exclusive. In particular, variants of the invention may be conceived comprising only a selection of features described below in isolation from the other features described, if this selection of features is sufficient to confer a technical advantage and / or to differentiate the invention from the prior art.

[0047] In the figures, elements common to several figures retain the same reference.

[0048] In the detailed description which follows, the terms “longitudinal”, “transverse” and “vertical” refer to the orientation of the heat exchanger plate according to the invention. A longitudinal direction corresponds to a main extension direction of this plate, this longitudinal direction being parallel to a longitudinal axis L of a reference frame L, V, T illustrated in the figures. A vertical direction corresponds to a direction measured at right angles to a plane in which the bottom wall of the heat exchanger plate mainly extends, this vertical direction being parallel to a vertical axis V of the reference frame L, V, T and this vertical axis V being perpendicular to the longitudinal axis L. Finally, a transverse direction corresponds to a direction parallel to a transverse axis T of the reference frame L, V, T, this transverse axis T being perpendicular to the longitudinal axis L and to the vertical axis V.

[0049] Figures 1 and 2 thus illustrate a heat exchanger 1 according to the invention, this heat exchanger 1 being intended to equip a motor vehicle. Figure 1 is a perspective view while Figure 2 is a sectional view along section AA of Figure 1. The heat exchanger 1 participates in the heating or cooling of at least one element of the motor vehicle with which it is equipped. For this purpose, it is configured to carry out a heat exchange, that is to say an exchange of calories, between a first fluid and a second fluid which both pass through it. This other fluid may for example be a heat transfer liquid such as glycolated water or oil. The heat exchanger i extends mainly in a longitudinal direction L. It comprises a plurality of plates 10 which extend mainly in a plane including the longitudinal direction L and the transverse direction T.More particularly, the heat exchanger i is formed by a stack of plates 10, which are superimposed on each other in a stacking direction E perpendicular to a plane in which the longitudinal direction L is inscribed and which corresponds to a vertical direction V.

[0050] As can be seen particularly in Figure 2, the stack of plates 10 is covered by a cheek 2, which constitutes an end plate of the heat exchanger 1. This cheek 2 is not shown in Figure 1. It has a rectangular shape and its surface is smooth. With the exception of the cheek 2 and a possible other cheek arranged opposite it in the stacking direction E, the set of plates 10 constitutes a heating body of the heat exchanger 1, that is to say a portion within which the heat exchanges between the first fluid and the second fluid take place.

[0051] As seen in Figure 1, the heat exchanger 1 comprises at a first of its longitudinal ends two connecting pipes 4, 6 and at a second of its longitudinal ends a connecting block 8. These pipes and connecting block 4, 6, 8 allow the fluids to be conveyed to fluid distribution openings of the heat exchanger 1 as well as their evacuation from these fluid distribution openings.

[0052] Two of the plates 10 of the heat exchanger 1 according to the invention are shown in isolation in Figure 3, in a perspective view. These two plates 10 are adjacent and superimposed in the stacking direction E, one of the plates 10 having been pivoted half a turn relative to the other. The stacking of the plates 10 within the heat exchanger 1 is such that the first fluid circulates between two directly adjacent plates 10, the second fluid circulating between each of these two plates 10 and other plates which are directly adjacent to them. Each plate 10 of the heat exchanger 1 is intended to be assembled by brazing to the plates 10 which are adjacent to it in the stacking direction E and / or to the cheek 2, in order to ensure the sealing of the heat exchanger i.

[0053] One of the plates 10 of the heat exchanger i will now be described in more detail, the characteristics of this plate 10 being applicable to each of the plates 10 forming the heating body of the heat exchanger i.

[0054] The plate 10 has a substantially rectangular shape as well as four rounded corners. The plate 10 is delimited by two longitudinal edges 12, 14 opposite one another and which extend in the longitudinal direction L, and two lateral edges 16, 18 opposite one another and perpendicular to these longitudinal edges 12, 14. One of the lateral edges 16, 18 is thus arranged at a first longitudinal end 20 of the plate 10, the other of these lateral edges 16, 18 being arranged at a second longitudinal end 22 thereof. It is understood here that the longitudinal edges 12, 14 and lateral edges 16, 18 constitute a periphery or raised edge of the plate 10.

[0055] The longitudinal edges 12, 14 and lateral edges 16, 18 delimit between them a volume of the plate 10. The volume of the plate 10 is further delimited in particular by a bottom wall 24, which extends mainly in a longitudinal-transverse plane. This bottom wall 24 is connected to each of the longitudinal edges 12, 14 and lateral edges 16, 18. More precisely, the bottom wall 24 is connected to these longitudinal edges 12, 14 and lateral edges 16, 18 so that an angle a measured between this bottom wall 24 and any one of the edges 12, 14, 16, 18 is between 103.5 ° and 109.5 °. Preferably, such an angle a is between 105 0 and 108°. The longitudinal edges 12, 14 and lateral edges 16, 18 thus extend in intersecting planes but not perpendicular to the longitudinal-transverse plane in which the bottom wall 24 extends, thereby giving the plate 10 a bathtub shape.

[0056] The plate 10 also has a determined thickness, such a thickness corresponding to its dimension which is measured along the vertical direction V taken at the level of the bottom wall 24. According to the invention, the thickness of this bottom wall 24 of the plate 10 is between 0.20 mm and 0.45 mm, preferably between 0.27 mm and 0.35 mm. As mentioned previously, the fluids are conveyed to fluid distribution openings of the heat exchanger i. These fluid distribution openings are here arranged in the vicinity of each of the four corners of the plate 10, that is to say on the bottom wall 24 at the junction between their longitudinal edges 12, 14 and lateral edges 16, 18.It is thus understood that there are here four fluid distribution openings, with a first fluid distribution opening 26, a second fluid distribution opening 28, a third fluid distribution opening 30 and a fourth fluid distribution opening 32, i.e. two fluid distribution openings 26, 28 at the first longitudinal end 20 and two fluid distribution openings at the second longitudinal end 22. These fluid distribution openings 26, 28, 30, 32 are intended to deliver or evacuate fluid to / from each of the zones delimited by two adjacent plates 10 of the heat exchanger 1. They extend in particular in the extension of the connection pipes 4, 6 or of the connection block 8.The two fluid distribution openings 30, 32 which are arranged in the vicinity of the second longitudinal end 22 have a collar 33, which corresponds to a deformation by stamping of the material constituting the bottom wall 24 on the contour of these fluid distribution openings 30, 32. Conversely, the two fluid distribution openings 26, 28 arranged at the first longitudinal end 26, 28 are devoid of such a collar 33.

[0057] There exists, between two adjacent plates 10 or between an end plate 10 and the cheek 2, a circulation zone 34 dedicated to the circulation of the first fluid or the second fluid. This circulation zone 34 is delimited, when it is defined by two adjacent plates 10, on the one hand between the longitudinal edges 12, 14 and lateral edges 16, 18 of one of the two adjacent plates 10 and vertically on the other hand between the bottom walls 24 of each of these two adjacent plates 10. When the circulation zone 34 is between a plate 10 and the cheek 2, it is delimited vertically by the bottom wall 24 of the plate 10 and by the cheek 2. This circulation zone 34 is in fluid communication with the fluid distribution openings 26, 28, 30, 32. The fluid circulation zones 34 are therefore spaces between two adjacent plates 10 in the stacking direction E where fluid circulates.

[0058] Each plate 10 may comprise a separation strip 38 which extends from the first longitudinal end 20 and towards the second longitudinal end 22. This separation strip 38 projects from the bottom wall 24 of the plate 10 substantially equidistant from its longitudinal edges 12, 14. The separation strip 38 has, for example, a sinusoidal shape which contributes to disturbing a flow of the fluid within the fluid circulation zone 34. The separation strip 38 thus makes it possible to lengthen the path of the fluid, which carries out a U-shaped circulation within this fluid circulation zone 34.

[0059] The plate 10 has fluid flow disruptors 40, which are particularly visible in Figures 3 to 6, Figures 4 to 6 being section views AA of the heat exchanger 1. The fluid flow disruptors 40 are protrusions or asperities which are deformations of the bottom wall 24 of the plate 10. Such deformations can in particular be obtained by stamping the bottom wall 24, towards the inside of the volume of the plate 10 delimited by its longitudinal edges 12, 14 and lateral edges 16, 18. Unlike the cheek 2 whose surface is flat, the plates 10 therefore have an irregular surface which prevents the laminar flow of the fluid concerned within the circulation zone 34.

[0060] A fluid flow disruptor 40 is here a truncated dome 41 which projects from a plate 10. In the presence of several truncated domes 41, these are distributed in a regular pattern and at a predefined pitch.

[0061] As particularly visible in Figures 4 to 6, these truncated domes 41 extend between a base 42, as close as possible to the longitudinal-transverse plane in which the bottom wall 24 mainly extends, and a top 44 at a distance from it. The top 44 of each of the truncated domes 41 is a flat part, preferably extending parallel to the bottom wall 24.

[0062] According to the invention, the fluid flow disruptors 40 have a vertical dimension D, i.e. their dimension measured between their base 42 and their apex 44, of between 0.75 mm and 1.15 mm. Such a vertical dimension corresponds to a height of the truncated domes 41. Furthermore, a maximum diameter of the truncated domes 41 measured at their base 42 is 4.5 mm, while a minimum diameter of these truncated domes 41 measured at their apex 44 is 2 mm. The truncated dome 41 has a circular profile, seen from above, just like the apex 44 and / or the base 42.

[0063] When two adjacent plates 10 along the stacking direction E are assembled in order to form a heat exchanger 1, the tops 44 of the fluid flow disruptors 40 of one of these plates 10 are in contact with the bottom wall 24 of the other plate 10. Each plate 10 being equipped with multiple fluid flow disruptors 40, it is therefore understood that there are several points of contact between two adjacent plates 10 when they are stacked. Such points of contact are particularly visible in Figures 4 to 6.

[0064] Due to these contact points, the fluid flow disruptors 40 constitute a holding device during crushing of the plates 10 for the purpose of assembling the heat exchanger 1. During this assembly, the plates 10 are in fact stacked in the stacking direction E before being crushed and then brazed, which helps to guarantee the sealing of the heat exchanger 1. The holding is particularly ensured by the tops 44 of the truncated domes 41 which, as mentioned previously, come into contact with the bottom wall 24 of the adjacent plate 10. Furthermore, the crushing of the plates 10 causes their deformation, for example an inclination, at the level of their longitudinal edges 12, 14 and lateral edges 16, 18. Such deformation is, as will be explained later, dependent on the angle a measured between these longitudinal edges 12, 14 and lateral edges 16, 18 and the bottom wall 24.

[0065] In Figures 4 to 6, it is also illustrated that the fluid flow disruptors 40 of two adjacent plates 10 along the stacking direction E are arranged in a staggered manner. In other words, there is an offset between the respective fluid flow disruptors 40 of two adjacent plates 10, such an offset being observed according to a sectional view along a longitudinal-vertical plane. Figures 4 to 6, which correspond to three distinct embodiments of the heat exchanger 1 according to the invention, will now be described successively. The embodiment shown in Figure 4 corresponds to a first embodiment of the heat exchanger 1 according to the invention. The plates 10 stacked under the cover 2 along the stacking direction E, which correspond to the heating body, are here first plates 10A interposed with second plates 10B.First plates 10A and second plates 10B are distinguished in particular according to the vertical dimension D of their respective fluid flow disruptors 40; thus, the fluid flow disruptors 40 of the first plates 10A have a vertical dimension D of between 0.75 mm and 0.85 mm, i.e. a first vertical dimension Di, while the fluid flow disruptors 40 of the second plates 10B have a vertical dimension D of between 1.05 and 1.15 mm, i.e. a second vertical dimension D2. In other words, the heat exchanger 1 according to the first embodiment is produced by repeating an alternation between a first plate 10A of the first vertical dimension Di and a second plate 10B of the second vertical dimension D2. It is understood here that this heat exchanger 1 has fluid flow disruptors 40 of variable dimensions from one plate 10 to another.Thus, the fluid circulation zone 34 defined between two given adjacent plates 10 may be larger than the fluid circulation zone 34 delimited by one of these two plates 10 and another plate 10 adjacent to it.

[0066] Furthermore, in this first embodiment the angle a measured between any one, advantageously all, of the longitudinal edges 12, 14 or lateral edges 16, 18 on the one hand and the bottom wall 24 on the other hand is here a first angle al which is between 105 0and 108°. Such a first angle ai is chosen to ensure, during assembly of the heat exchanger 1 and more particularly during deformation of the plates 10 comprising it, a capacity of the longitudinal edges 12, 14 and lateral edges 16, 18 to deform in such a way that the tops 44 of each of the fluid flow disruptors 40 of a given plate 10 come into contact with the bottom wall 24 of the plate 10 which is adjacent to it. The first angle ai also contributes to ensuring a seal between the longitudinal edges 12, 14 and lateral edges 16, 18 of two adjacent plates 10, even though these have fluid flow disruptors 40 of variable dimensions, that is to say both along the first dimension Di and the second dimension D2.

[0067] Unlike the heat exchanger 1 according to the first embodiment, the heat exchanger 1 according to the second embodiment illustrated in FIG. 5 comprises a heating body consisting solely of first plates 10A. It is thus understood that according to this second embodiment, the heat exchanger 1 has a stack of plates 10 all having fluid flow disruptors 40 along the first dimension Di. In other words, the heat exchanger 1 here comprises exclusively fluid flow disruptors 40 whose vertical dimension D is between 0.75 and 0.85 mm.

[0068] In this second embodiment, the angle a is a second angle a2, which is between 106.5 0and 109.5°- This second angle a2 is suitable for the assembly of plates 10 all having fluid disturbers 40 along the first dimension Di. It is understood here that this angle a2 allows the first plates 10A to be deformed to guarantee both contact between the fluid flow disturbers 10 of a first plate 10A and the bottom wall 24 of the first plate 10A which is adjacent to it, and also the sealing of the heat exchanger 1 comprising only such first plates 10A.

[0069] In the third embodiment shown in Figure 6, the heating body of the heat exchanger 1 comprises only second plates 10B; all the fluid flow disruptors 40 of this heat exchanger 1 therefore have the second vertical dimension D2, that is to say between 1.05 and 1.15 mm. For this third embodiment, the angle α between the bottom plate 24 and either one of the longitudinal edges 12, 14, or one of the lateral edges 16, 18 is a third angle θC3 between 103.5° and 106.5°. The third angle θ13 allows adequate deformation of the second plates 10B so that their fluid flow disruptors 40 along the second dimension D2 come into contact with the bottom walls 24 of the adjacent second plates 10B during assembly of the heat exchanger 1 according to the third embodiment.Such an angle 013 also contributes to the sealing of the second plates 10B after they have been stacked and brazed, in particular at their longitudinal edges 12, 14 and lateral edges 16, 18.

[0070] The present invention thus provides a heat exchanger plate and an associated heat exchanger comprising several of these plates, their fluid flow disturbance devices being configured to optimize the disturbance of the circulation of fluids within the heat exchanger and to offer it improved mechanical resistance, the plate being able to deform to absorb dimensional differences when the heating body is exclusively made up of plates along the first vertical dimension, of an alternation of plates along the first vertical dimension and along the second vertical dimension or of plates along the second vertical dimension.

[0071] The present invention cannot, however, be limited to the means and configurations described and illustrated here and it also extends to any equivalent means and configuration as well as to any technically effective combination of such means.

Claims

DEMANDS 1. Heat exchanger plate (10) (i) having a tub-like shape with two opposing longitudinal edges (12, 14) connected to each other by two lateral edges (16, 18), these longitudinal (12, 14) and lateral (16, 18) edges surrounding a bottom wall (24) of the plate (10), an angle (a, ai, a2, a3) measured between this bottom wall (24) and any one of the edges (12, 14, 16, 18) being between 103.5 0 and 109.5°, a bottom wall thickness (24) being between 0.20 mm and 0.45 mm, the bottom wall (24) being equipped with fluid flow disruptors (40), at least one of these fluid flow disruptors (40) having a vertical dimension (D, Di, D2) measured inside a volume delimited by the bottom wall (24) and the edges (12, 14, 16, 18) of between 0.75 mm and 1.15 mm.

2. Heat exchanger plate (10) according to the preceding claim, wherein the vertical dimension (D, Di, D2) of the fluid flow disruptors (40) is a first vertical dimension (Di) between 0.75 mm and 0.85 mm.

3. Heat exchanger plate (10) according to claim 1, wherein the vertical dimension (D, Di, D2) of the fluid flow disruptors (40) is a second vertical dimension (D2) between 1.05 mm and 1.15 mm.

4. Heat exchanger plate (10) according to any one of the preceding claims, wherein the bottom wall (24) is equipped with at least four fluid distribution openings (26, 28, 30, 32), each of these fluid distribution openings (26, 28, 30, 32) being disposed in the vicinity of a junction between a longitudinal edge (12, 14) and a lateral edge (16, 18).

5. Heat exchanger plate (10) according to any one of the preceding claims, wherein the fluid flow disruptors (40) comprise at least one truncated dome (41) extending between a base (42) and a top (44).

6. Heat exchanger plate (io) according to the preceding claim, wherein a maximum diameter of the truncated dome (41) measured at its base (42) is 4.5 mm.

7. Heat exchanger plate (10) according to any one of the preceding claims in combination with claim 5, wherein a minimum diameter of the truncated dome (41) measured at its apex (44) is 2 mm.

8. Heat exchanger (1) configured to operate a heat exchange between a first fluid and a second fluid, this heat exchanger (1) comprising first plates (10A) according to claim 2 and / or second plates (10B) according to claim 3.

9. Heat exchanger (1) according to the preceding claim, wherein the angle (a, ai) measured between the bottom wall (24) and any one of the edges (12, 14, 16, 18) is between 105 0 and 108°.

10. Heat exchanger (1) according to the preceding claim in combination with claim 5, wherein the peaks (42) of the fluid flow disruptors (40) of a plate (10) are in contact with the bottom wall (24) of the plate (10) which is adjacent to it in the stacking direction (E).

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