Heat sink for electrical equipment

Abstract

The invention relates to a heat sink comprising:-an inlet and an outlet for a heat transfer fluid,-an exchange surface extending between the inlet and the outlet and intended to exchange heat with the heat transfer fluid, the exchange surface comprising an inlet region, an outlet region and at least one intermediate region, all regions of the exchange surface having the same surface area, -a plurality of fins protruding from the exchange surface in each of these zones and having a leading edge, a trailing edge, and an angle of incidence measured between a shortest distance section connecting the leading edge to the trailing edge and a main direction of the fluid, the fins in the inlet region, the intermediate region, and the outlet region have an average inlet angle of incidence, an average intermediate angle of incidence, and an average outlet angle of incidence, respectively, the average inlet angle of incidence being less than the average intermediate angle of incidence, the average intermediate angle of incidence being less than the average outlet angle of incidence.

Description

Technical Field

[0001] The present invention relates to the field of electrical equipment that needs to be cooled by a heat transfer fluid, in particular to electrical and power electronic machines (such as power converters) for electric or hybrid vehicles.

[0002] The present invention more particularly relates to radiators for cooling such electrical equipment and to heat transfer (such as heat elimination, absorption, and / or dissipation). Background Art

[0003] It is known from the prior art that the temperature of electrical equipment rises during operation of the electrical equipment. Therefore, the increase in temperature will cause significant damage to the electrical equipment.

[0004] For example, in a rotating electric machine, electrical energy is converted into kinetic energy, or vice versa. The losses generated cause the components of the electric machine to heat up during its operation. To avoid excessive heating of its components (such as the stator and rotor), a radiator, which can also be referred to as a cooling device, must be provided in the electric machine. The heat generated by the circulation of the current through the windings of the stator can be discharged through a radiator (such as a cooling chamber provided in a bearing and through which a heat transfer fluid circulates). Document US8629587 discloses that the cooling chamber extends in the circumferential direction of the stator, and fins project from the surface of the cooling chamber into the chamber to allow for more efficient cooling.

[0005] In the case of power electronics devices, for example for an inverter, the power modules experience an increase in temperature during their operation. The increase in temperature will cause significant damage to the modules themselves and other elements of the electrical assembly. To limit these thermal effects, it is known to use a cooling circuit to cool the power electronics devices. As disclosed in document EP 3902382, the cooling circuit is provided below or above the power module. In this document, projections of tubular shape project from the exchange surface.

[0006] The addition of the projections makes it possible to increase the exchange surface area in order to achieve greater heat transfer and thus better cooling. However, it should be noted that the cooling requirements between the inlet and the outlet of the radiator are not the same. In fact, in the cited document, since the arrangement of the projections is always the same along the exchange surface of the radiator, the heat transfer coefficient is constant. Due to the natural warming of the heat transfer fluid between the inlet and the outlet of the radiator, the heat exchange capacity is reduced and an uneven temperature model is created.

[0007] The present invention aims to remedy the above problems by providing a radiator that creates a uniform temperature model. Summary of the Invention

[0008] Accordingly, the present invention aims to provide a radiator, in particular a radiator for electrical equipment, which radiator comprises:

[0009] an inlet and an outlet for a heat transfer fluid,

[0010] an exchange surface which extends between the inlet and the outlet and is intended to exchange heat with the heat transfer fluid, said surface comprising an inlet zone in communication with the fluid inlet, an outlet zone in communication with the fluid outlet, and at least one intermediate zone provided between the inlet zone and the outlet zone, all zones of the exchange surface having the same area,

[0011] a plurality of fins which project from said exchange surface in each of these zones, each fin having a leading edge, a trailing edge, and an angle of incidence measured between the minimum distance segment connecting the leading edge to the trailing edge and the main direction of the heat transfer fluid between the inlet and the outlet,

[0012] wherein the fins in the inlet zone, the intermediate zone, and the outlet zone have an average inlet angle of incidence, an average intermediate angle of incidence, and an average outlet angle of incidence respectively, said average inlet angle of incidence being less than the average intermediate angle of incidence, which average intermediate angle of incidence is less than the average outlet angle of incidence.

[0013] By modifying the geometric design parameters between the fluid inlet and the outlet in this way, the resulting turbulence will be greater and the heat transfer coefficient will also be greater. With this arrangement, the present invention thus makes it possible to adapt the heat transfer coefficient along the exchange surface of the radiator (the heat transfer coefficient in the outlet zone being greater than the heat transfer coefficient in the inlet zone) to the heat transfer fluid in order to achieve a uniform temperature between the inlet and the outlet.

[0014] In the present invention, the term "electrical equipment" is intended to denote electric machines and power electronic devices.

[0015] In a manner known per se, an electric machine, in particular a rotating electric machine, comprises a stator and a rotor fixed to a shaft. The rotor can be fixed to a drive and / or a driven shaft and can be in the form of an alternator, an electric motor, or a reversible electric machine capable of operating in two modes.

[0016] In certain types of motor vehicle drive trains, a high-power reversible rotating electric machine is coupled to the vehicle's gearbox or to the vehicle's axle system. Thus, the electric machine is capable of operating in alternator mode to supply energy in particular to the battery and / or to the vehicle's on-board network, and in electric motor mode to not only start the combustion engine but also to power the vehicle (either on its own or in combination with the combustion engine).

[0017] Power electronic devices refer to, for example, power converters (on-vehicle chargers, DC / DC converters, inverters), and these power converters include power modules for receiving an electric power signal or delivering an electric power signal to an electrical phase of a winding of an electric machine. In the case of an inverter, for example, the power module forms a bridge voltage rectifier for converting an AC voltage generated by a phase of a stator into a DC voltage and / or, conversely, for converting a DC voltage into an AC voltage to be fed to a phase of the stator. The inverter further includes a control section, which includes a control module, which is particularly used for regulating the voltage injected into the rotor and providing an interface with a computer external to the vehicle.

[0018] The radiator is thus configured to dissipate the heat output by the electrical equipment.

[0019] The main direction of the fluid should be considered as the direction of the shortest path along which the fluid travels between the fluid inlet and the outlet.

[0020] The "average incident angle of a zone" is intended to represent the sum of the incident angles of the fins in the zone divided by the number of fins in that zone.

[0021] Advantageously, the leading edge and the trailing edge of each fin are in contact with the heat exchange surface.

[0022] Advantageously, the incident angle lies in a plane parallel to the exchange surface.

[0023] Within the scope of the present invention, in each zone, a plurality of fins project.

[0024] Advantageously, all the fins in a single zone have the same incident angle.

[0025] Advantageously, the fins have a parallelepiped shape, an oval shape or a substantially oval shape. The term "substantially oval" is intended to mean a fin including at least one oval portion.

[0026] Advantageously, the fins in the inlet zone have a maximum incident angle smaller than the minimum incident angle of the fins in the intermediate zone, and the fins in the intermediate zone have a maximum incident angle smaller than the minimum incident angle of the fins in the outlet zone.

[0027] Advantageously, the fins extend at an average inlet height, an average intermediate height and an average outlet height in the inlet zone, the intermediate zone and the outlet zone respectively, and the average inlet height of the fins is less than the average intermediate height of the fins, and the average intermediate height is less than the average outlet height of the fins.

[0028] Thus, this makes it possible to adapt the heat exchange coefficient with the heat transfer fluid along the exchange surface of the radiator via the increased average height of the fins between the inlet zone and the outlet zone, in order to achieve a uniform temperature between the inlet and the outlet. By increasing the average height of the fins, the contact surface area between the heat transfer fluid and the radiator increases, and the heat exchange coefficient also increases.

[0029] Each fin extends in height between a base and a tip that are arranged on the exchange surface, and the fin projects from this exchange surface.

[0030] The "average height of the fins in the zone" is intended to represent the sum of the heights of the fins in the zone divided by the number of fins in that zone.

[0031] Advantageously, all the fins in a single zone extend at the same height. Thus, the average height of the fins in the zone corresponds to the height of any fin in that same zone.

[0032] Advantageously, the maximum height of the fins in the inlet zone is smaller than the minimum height of the fins in the intermediate zone, and the maximum height of the fins in the intermediate zone is smaller than the minimum height of the fins in the outlet zone.

[0033] Advantageously, the number of fins in the inlet zone is less than the number of fins in the intermediate zone, and the number of fins in the intermediate zone is less than the number of fins in the outlet zone. This arrangement makes it possible to adapt the heat exchange coefficient along the exchange surface of the radiator (the heat exchange coefficient in the outlet zone being greater than the heat exchange coefficient in the inlet zone) with the heat transfer fluid, in order to achieve a uniform temperature between the inlet and the outlet. By increasing the number of fins, the contact surface area between the heat transfer fluid and the radiator increases, and the heat exchange coefficient also increases. In addition, the fins increase the effectiveness of heat transfer by converting laminar flow into turbulent flow.

[0034] The fins have both the function of hydraulic resistance and the function of a heat device. The hydraulic resistance corresponds to the pressure drop experienced by the heat transfer fluid within the radiator. The greater the number of fins on the exchange surface of the radiator, the greater the pressure drop and thus the hydraulic resistance. The heat device is intended to increase the contact surface area with the heat transfer fluid in order to increase convective exchange and thus increase the transfer of heat. The fins are advantageously thermally conductive.

[0035] Advantageously, all the fins in a single zone have the same shape.

[0036] Advantageously, the shape of the fins varies from one zone to another.

[0037] Advantageously, the fins project radially from the exchange surface.

[0038] Advantageously, the fins are made integrally with the exchange surface from which they project.

[0039] Advantageously, the exchange surface has a planar surface which preferably has a rectangular shape. In a variant, the exchange surface may have a circumferential shape.

[0040] Advantageously, the exchange surface is formed of a solid heat-conducting material such as steel, aluminum or copper.

[0041] Advantageously, the radiator includes an additional exchange surface preferably disposed beside the exchange surface, which extends between an inlet and an outlet and is intended to exchange heat with a heat-transfer fluid. The additional surface includes an inlet zone in communication with the fluid inlet, an outlet zone in communication with the fluid outlet, and at least one intermediate zone disposed between the inlet zone and the outlet zone. All zones of the additional exchange surface have the same area.

[0042] Advantageously, a plurality of additional fins project from the additional exchange surface in each of the zones, and

[0043] in each of the zones, the additional fins extend at an average inlet height, an average intermediate height and an average outlet height in the inlet zone, the intermediate zone and the outlet zone respectively. The average inlet height of the additional fins is less than the average intermediate height, which is less than the average outlet height, and / or

[0044] the number of additional fins in the inlet zone is less than the number of additional fins in the intermediate zone, which is less than the number of additional fins in the outlet zone, and / or

[0045] Each additional fin has a leading edge, a trailing edge, and an incident angle measured between the minimum distance segment connecting the leading edge to the trailing edge and the main direction of the heat-transfer fluid between the inlet and the outlet. The additional fins in the inlet zone, the intermediate zone and the outlet zone have an average inlet incident angle, an average intermediate incident angle and an average outlet incident angle respectively. The average inlet incident angle is less than the average intermediate incident angle, which is less than the average outlet incident angle.

[0046] Thus, the two surfaces at least partially form a cooling chamber in which the heat-transfer fluid flows. One of these surfaces is an inner surface, and the other surface is an outer surface of the electrical equipment cooled by the radiator.

[0047] The fins project from the exchange surface or the additional exchange surface in the direction of the other exchange surface without reaching the latter.

[0048] Advantageously, the heat-transfer fluid can be liquid or gaseous. Preferably, the heat-transfer fluid is water such as ethylene glycol water, oil or air.

[0049] The present invention also relates to a machine component, which comprises an electrical equipment and a radiator according to the present invention. Preferably, the electrical equipment is selected from an electric motor and power electronics. Power electronics refers to, for example, a power converter, such as an on-vehicle charger, a DC / DC converter, an inverter.

[0050] The present invention also relates to the use of the machine component according to the present invention in a motor vehicle. Description of the Drawings

[0051] The present invention will be better understood by reading the following description and checking the drawings. These drawings are provided only by way of a completely non-limiting illustration of the present invention.

[0052] Figure 1 is a perspective view of a machine component (radiator + power electronics) according to the present invention.

[0053] Figure 2 is a top view of a part of the radiator according to the first embodiment.

[0054] Figure 3 is a top view of a part of the radiator according to the second embodiment.

[0055] Figure 4 is Figure 2 or Figure 3 an enlarged view of the first cooling fin shape of the radiator in

[0056] Figure 5 shows a second fin shape that can be used in the present invention.

[0057] Figure 6 is a perspective view of a part of the radiator, showing variable fin heights.

[0058] Figure 7 is Figure 6 a longitudinal sectional view of the exchange surface and the fins in

[0059] Figure 8 is a view similar to Figure 7 according to another embodiment.

[0060] Figure 9 is Figure 8 the same view with different zoning as

[0061] Figure 10 is a view similar to Figure 6 according to another embodiment, showing variable fin density.

[0062] Identical, similar or like elements are retained with the same reference numerals in the various figures. Detailed Description of the Invention

[0063] Figure 1 The machine assembly 110 is shown including an electrical equipment 100 and a radiator 1.

[0064] In the example considered, the electrical equipment 100 refers to three power modules 101 of a power electronic device, in particular an inverter for receiving a power signal or delivering a power signal to the electrical phases of the windings of an electric motor. A thermal interface material for discharging the heat generated by the power module 101 to the radiator 1 may be provided at the interface between the two elements. The thermal interface material is, for example, a thermal adhesive, a grease or a paste.

[0065] The radiator 1 includes an inlet 31 and an outlet 32 for a heat transfer fluid and an exchange surface 5 that extends between the inlet 31 and the outlet 32 and is intended to exchange heat with the heat transfer fluid. In all the figures, the dashed arrows indicate the main direction of the fluid between the inlet 31 and the outlet 32 of the radiator 1.

[0066] As can be seen in Figure 2 or Figure 3 , the surface 5 includes an inlet zone 51 in communication with the fluid inlet 31, an outlet zone 53 in communication with the fluid outlet 32, and an intermediate zone 52 provided between the inlet zone 51 and the outlet zone 53. Thus, the heat transfer fluid follows the following path: inlet 31 of the radiator 1, inlet zone 51, intermediate zone 52, outlet zone 53, and then the outlet 32 of the radiator.

[0067] The intermediate zone 52 separates the inlet zone 51 from the outlet zone 53. Thus, in order to transfer from the inlet zone 51 to the outlet zone 53, the fluid passes through the intermediate zone 52.

[0068] Within the scope of the present invention, all zones 51, 52, 53 of the exchange surface 5 have the same corresponding area a 1 , a 2 , a 3 . That is to say, the area a 1 of the inlet zone 51 = the area a 2 of the intermediate zone 52 = the area a 3 of the outlet zone 53.

[0069] In the example considered, the surfaces 51, 52, 53 also have the same shape, but they may have different shapes as long as these surfaces have equal areas.

[0070] A plurality of fins 20 project from the exchange surface 5. Preferably, the fins 20 project radially from the exchange surface 5, that is to say, project perpendicularly to the exchange surface 5.

[0071] The fins 20 are arranged in a plurality of longitudinal rows and a plurality of transverse rows. In Figure 2In the example considered, the fins 20 are arranged in six longitudinal rows and fifteen transverse rows. The number of these rows is adapted to the radiator and, in particular, to the size of the exchange surface 5.

[0072] As can be seen in more detail in Figure 4 and Figure 5 each fin 20 has a leading edge 25 and a trailing edge 26. These edges are defined relative to the main direction of the heat transfer fluid. The angle of incidence α is measured between the minimum distance segment 27 connecting the leading edge 25 to the trailing edge 26 and the main direction of the heat transfer fluid indicated by the dashed arrow between the inlet 31 and the outlet 32. The angle α can also be considered as the angle between the longitudinal axis of the fin 20 (i.e., the axis along the length of the fin 20) and the main direction of the fluid.

[0073] In Figure 2 and Figure 3 the fins 20 have a parallelepiped shape, as shown in Figure 4 In a variant, the fins 20 may have an oval shape, as shown in Figure 5 shown.

[0074] The fins 20 in the inlet zone 51, the intermediate zone 52 and the outlet zone 53 have an average inlet angle of incidence α m1 , an average intermediate angle of incidence α m2 and an average outlet angle of incidence α m3 . Thus, the average angle of incidence α m corresponds to the sum of the angles of incidence α of the fins 20 in a zone divided by the number of fins 20 in that zone.

[0075] Within the scope of the present invention, the average inlet angle of incidence α m1 is less than the average intermediate angle of incidence α m2 , which average intermediate angle is less than the average outlet angle of incidence α m3 . In other words, α m1 < α m2 < α m3 .

[0076] In these examples, the fins 20 in the inlet zone 51 have a maximum angle of incidence α that is smaller than the minimum angle of incidence in the intermediate zone 52, and the fins 20 in the intermediate zone 52 have a maximum angle of incidence α that is smaller than the minimum height of the fins 20 in the outlet zone 53.

[0077] The progressive development of the angle of incidence α of the fins 20 between the inlet 31 and the outlet 32 can be stepwise, as is the case in Figure 2 . In this example, in the case where all the fins 20 in a single zone have the same angle of incidence α, the respective average angles of incidence α m1 , αm2 and α m3 will be equal to the angle of incidence α of any fin 20 in the same zone.

[0078] In a variant, as can be seen in Figure 3 , the progressive development of the angle of incidence α of the fins 20 between the inlet 31 and the outlet 32 can be linear. Specifically, along the main direction of the fluid between the inlet 31 and the outlet 32, each fin 20 in a single longitudinal row has an angle of incidence α that is less than the angle of incidence α of the subsequent fin 20. Here, the respective average angles of incidence α m1 and α m2 and α m3 of each zone 51, 52, 53 will thus be equal to the sum of the angles of incidence α of the fins 20 in each zone 51, 52, 53 divided by the number of fins 20 in each zone.

[0079] Each fin 20 extends over a height h between the base and the tip provided on the exchange surface 5, and the fin 20 projects from this exchange surface. Thus, the height h is generally understood here as the distance separating the base and the tip along an axis perpendicular to the exchange surface 5.

[0080] As can be seen in Figures 6 to 10 , the average height of the fins 20 in a zone is not the same from one zone to another. In this case, the average height of the fins in each zone is considered. Thus, in the inlet zone 51, the fins 20 extend over an average inlet height h m51 , in the intermediate zone 52, they extend over an average intermediate height h m52 , and in the outlet zone 53, they extend over an average outlet height h m53 .

[0081] The average height of the fins 20 in a zone is calculated by taking the sum of all the fins 20 in that zone and then dividing it by the number of fins 20 in the same zone.

[0082] In the example considered, the average inlet height h m51 of the fins 20 is less than the average intermediate height h m52 , which is less than the average outlet height h m53 . In other words, h m51 < h m52 < h m53 .

[0083] Here, the fins 20 are arranged in seven longitudinal rows and fifteen transverse rows.

[0084] The fins 20 in the inlet zone 51 have a maximum height that is less than the minimum height of the fins 20 in the intermediate zone 52, and the fins 20 in the intermediate zone 52 have a maximum height that is less than the minimum height of the fins 20 in the outlet zone 53.

[0085] In Figure 6 , some of the fins 20 in a single zone have different heights (the fins 20 in the longitudinal rows), while other fins have the same height (the fins 20 in the transverse rows). The gradual development of the height of the fins between the inlet 31 and the outlet 32 can be linear, as in Figure 6 and Figure 7 . Specifically, along the direction of the fluid between the inlet 31 and the outlet 32, each fin 20 in a single longitudinal row has a height that is less than the height of the subsequent fin 20.

[0086] In a variant, as can be seen in Figure 8 or Figure 9 , the gradual development of the height of the fins between the inlet 31 and the outlet 32 can be stepped. In this example, all of the fins 20 in a single zone 51, 52, 53 extend at the same height.

[0087] In Figures 6 to 8 's example, each zone 51, 52, 53 includes 5 transverse rows of fins 20. It is likely that the exchange surface 5 includes an inlet zone 51, an outlet zone 53, and n intermediate zones 52 (where n is an integer between 1 and 13 in this case) provided between the inlet zone 51 and the outlet zone 53. The average height will always comply with the following rule: h m51 <h m52n <h m52(n+1) <h m3 .

[0088] An example where the exchange surface 5 is divided into an inlet zone 51, a first intermediate zone 52 1 , a second intermediate zone 52 2 , a third intermediate zone 52 3 , and an outlet zone 53 is presented in Figure 9 . In this case, there is clearly the following relationship between the average heights in each zone: h m51 <h m52.1 <h m52.2 <h m52.3 <h m3 .

[0089] In all the examples so far, the inlet zone 51, the intermediate zone 52, and the outlet zone 53 have the same number of fins 20. In other words, the density (i.e., the number) of the fins 20 in each zone is the same between different zones. The number of fins 20 in each zone is the same as the number of fins 20 in another zone. In this case, each of the zones 51, 52, 53 includes thirty-five fins.

[0090] In a variant, and as Figure 10 shown, the number of fins 20 in the inlet zone 51 can be less than the number of fins 20 in the intermediate zone 52, and the number of fins in this intermediate zone can be less than the number of fins 20 in the outlet zone 53. In this case, the number of fins 20 in the inlet zone 51 is fourteen, the number of fins in the intermediate zone 52 is twenty-eight, and the number of fins in the outlet zone 53 is thirty-five.

[0091] In all the examples so far, all the fins 20 protruding from the exchange surface 5 of the radiator 1 have the same shape, which is a parallelepiped shape in this case. Preferably, all the fins 20 in a single zone 51, 52, 53 have the same shape.

[0092] In a variant, the shape of the fins 20 varies from one zone 51, 52, 53 to another. According to another variant, the shape of the fins 20 can vary within a zone.

[0093] Advantageously, the radiator further includes an additional exchange surface 50, which is arranged next to the exchange surface 5 in this case. This additional surface 50 extends between the inlet 31 and the outlet 32 and is intended to exchange heat with the heat transfer fluid. Advantageously, the additional surface repeats the characteristics of the exchange surface 5, namely:

[0094] An inlet zone, which is in communication with the fluid inlet,

[0095] An outlet zone, which is in communication with the fluid outlet, and

[0096] At least one intermediate zone, which is arranged between the inlet zone and the outlet zone,

[0097] All the zones of the additional exchange surface have the same area, and

[0098] A plurality of additional fins protrude from the said additional exchange surface 50.

[0099] Furthermore:

[0100] In each zone of the zones, the additional fins extend at an average inlet height, an average intermediate height, and an average outlet height in an inlet zone, an intermediate zone, and an outlet zone, respectively, the average inlet height of the additional fins being less than the average intermediate height, which is less than the average outlet height, and / or

[0101] the number of additional fins in the inlet zone is less than the number of additional fins in the intermediate zone, which is less than the number of additional fins in the outlet zone, and / or

[0102] Each additional fin has a leading edge, a trailing edge, and an angle of incidence measured between the minimum distance segment connecting the leading edge to the trailing edge and the main direction of the heat transfer fluid between the inlet and the outlet. The additional fins in the inlet zone, the intermediate zone, and the outlet zone have an average inlet angle of incidence, an average intermediate angle of incidence, and an average outlet angle of incidence, respectively, the average inlet angle of incidence being less than the average intermediate angle of incidence, which is less than the average outlet angle of incidence.

[0103] The exchange surface 5 and the additional exchange surface 50 are thus arranged to at least partially form a cooling chamber in which the heat transfer fluid flows. This chamber is delimited by the surface 5 as the inner surface and the additional surface 50 as the outer surface.

[0104] In all the examples considered so far, heat sinks designed to cool power electronic devices have been presented. In this case, the exchange surface 5 has a planar surface, which preferably has a rectangular shape. The additional surface 50 also has a planar surface, which preferably has a rectangular shape.

[0105] Preferably, the distance between the exchange surface 5 and the additional surface 50 is constant. In other words, the height of the cooling chamber is constant.

[0106] In a variant not shown, the exchange surface may have a circular shape in order to cool, for example, a rotating electrical machine.

[0107] The rotating electrical machine includes a polyphase stator having a stator body surrounding a rotor mounted on a shaft and having an axis X. The stator of the machine surrounds the rotor, and an air gap exists between the inner periphery of the stator and the outer periphery of the rotor. The stator and the rotor form the active part of the electrical machine and will be surrounded by the heat sink.

[0108] The power of the machine can be between 4 kW and 50 kW. Alternatively, the electric motor can be mounted on an axle of a motor vehicle, in particular the rear axle. In the example considered, the electric motor advantageously has an operating voltage of less than 60 volts and preferably 48 volts. Typically, the torque supplied by the electric motor is between 30 N.m and 150 N.m. Alternatively, the electric motor can have an operating voltage greater than 60 V or even greater than 80 V or greater than 100 V, in particular 300 V or more. In this case, the power of the machine can be between 60 kW and 300 kW.

[0109] Of course, the above description is given by way of example only and does not limit the scope of the present invention, and the scope of the present invention will not be departed from by replacing the various elements with any other equivalents.

[0110] Furthermore, the different features, variants and / or embodiments of the present invention can be combined with each other in various combinations, as long as they are compatible with each other or not mutually exclusive.

Claims

1. A radiator (1), in particular a radiator for an electrical equipment, comprising: an inlet (31) and an outlet (32) for a heat transfer fluid, An exchange surface (5), which extends between the inlet (31) and the outlet (32) and is intended to exchange heat with the heat transfer fluid. The surface (5) includes an inlet zone (51) in communication with the fluid inlet, an outlet zone (53) in communication with the fluid outlet, and at least one intermediate zone (52) provided between the inlet zone (51) and the outlet zone (53). All zones of the exchange surface (5) have the same area (a 1 , a 2 , a 3 ). a plurality of fins (20), which project from the exchange surface (5) in each of the zones (51, 52, 53), each fin (20) having a leading edge (25), a trailing edge (26), and an incident angle (α) measured between the minimum distance segment (27) connecting the leading edge to the trailing edge and the main direction of the heat transfer fluid between the inlet (31) and the outlet (32), Characterized in that the fins (20) in the inlet region (51), the intermediate region (52) and the outlet region (53) respectively have an average inlet incident angle (α m1 ), an average intermediate incident angle (α m2 ), and an average outlet incident angle (α m3 ), and the average inlet incident angle (α m1 ) is less than the average intermediate incident angle (α m2 ), and the average intermediate incident angle is less than the average outlet incident angle (α m3 ).

2. The radiator (1) according to claim 1, characterized in that all the fins (20) in a single zone have the same incident angle (α).

3. The radiator (1) according to any one of the preceding claims, characterized in that the fins (20) have a parallelepiped shape, an elliptical shape or a substantially elliptical shape.

4. The radiator (1) according to any one of the preceding claims, characterized in that the fins (20) in the inlet zone (51) have a maximum incident angle (α) smaller than the minimum incident angle of the fins in the intermediate zone (52), and the fins in the intermediate zone have a maximum incident angle smaller than the minimum incident angle of the fins in the outlet zone (53).

5. The radiator (1) according to any one of the preceding claims, characterized in that The fin (20) extends at an average inlet height (h m51 ) in the inlet region (51), at an average intermediate height (h m52 ) in the intermediate region (52), and at an average outlet height (h m53 ) in the outlet region (53), And wherein, the average inlet height (h m51 ) of the fin (20) is less than the average middle height (h m52 ), and the average middle height is less than the average outlet height (h m53 ).

6. The radiator (1) according to any one of the preceding claims, characterized in that all the fins (20) in a single zone (51, 52, 53) extend at the same height.

7. The radiator (1) according to any one of the preceding claims, characterized in that the fins (20) in the inlet zone (51) have a maximum height smaller than the minimum height of the fins in the intermediate zone (52), and the fins in the intermediate zone have a maximum height smaller than the minimum height of the fins in the outlet zone (53).

8. The radiator (1) according to any one of the preceding claims, characterized in that the number of fins (20) in the inlet zone (51) is less than the number of fins in the intermediate zone (52), and the number of fins in the intermediate zone is less than the number of fins in the outlet zone (53).

9. The radiator (1) according to any one of the preceding claims, characterized in that all the fins (20) in a single zone (51, 52, 53) have the same shape.

10. The radiator (1) according to any one of the preceding claims, characterized in that the exchange surface (5) has a flat surface, which preferably has a rectangular shape.

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