ENGINE SUPPORT FOR A HEATING, VENTILATION AND / OR AIR CONDITIONING UNIT FOR MOTOR VEHICLES

Description

technical field

[0001] The present invention relates to the field of heating, ventilation and / or air conditioning devices for motor vehicles. More particularly, the invention concerns an electric motor support for such a device. Previous technique

[0002] Motor vehicles are commonly equipped with a heating, ventilation, and / or air conditioning (HVAC) system, which generates airflow. This system also manages the temperature and distribution of the generated airflow within the vehicle's passenger compartment. Such a HVAC system includes, among other things, a fan with a fan wheel driven by an electric motor. The electric motor is typically electronically commutated and controlled by a power supply module.

[0003] An electronically commutated electric motor, or brushless DC motor (also known by the English name "brushless"), comprises a rotor and stator assembly, each of these components carrying electromagnetic elements whose interaction generates the movement of the rotor relative to the stator, and further the movement of the fan wheel.

[0004] The electric motor is assembled into the heating, ventilation and / or vibration device by means of a motor support which includes an inner ring configured to accommodate the stator of the electric motor and an outer ring suitable for being fixed, directly or indirectly, to a structural element of the vehicle.

[0005] A decoupling element is interposed between the inner and outer rings. This decoupling element aims to limit, and preferably prevent, the transmission of vibrations and / or stresses generated by the rotation of the electric motor, from the inner ring to the outer ring. This reduces the transmission of vibrations to the heating, ventilation, and / or air conditioning system, which could be felt by the vehicle's occupants.

[0006] The decoupling element allows significant relative movement of the inner ring with respect to the outer ring, particularly in the event of vibration. In this case, repeated movement can lead, in the long term, to breakage of the decoupling element. A challenge, therefore, is to obtain a decoupling element with good mechanical endurance and also low vibration transmission. Documents EP 2 081 280 A1, FR 2 933 246 A1, and FR 2 957 987 A1 disclose a motor mount for a vehicle ventilation system.

[0007] The aim of the present invention is to provide an engine mount, in particular for a heating, ventilation and / or air conditioning system of a motor vehicle, which is simple to make and does not have at least some of the disadvantages of the mounts of the prior art. Summary

[0008] To this end, the invention relates to a motor support, in particular for a motor-fan unit of a vehicle ventilation system, according to claim 1 and comprising: two coaxial rings, of which an inner ring suitable for receiving one or more motor elements and an outer ring suitable for being fixed on a housing forming a structural element, a decoupling means between the two coaxial rings comprising a plurality of pads made of elastomeric material, interposed between the inner ring and the outer ring, each pad having a thickness measured in the direction of the common axis of the two rings, each pad having a shape substantially in the shape of an "H", the two arms of the "H" being separated by a distance B, oriented along the radial direction of the rings, each arm having a width D measured in the radial direction, the web of the "H" having a width A, measured along the tangential direction, in which the ratio A / B is greater than or equal to 1.4 and the ratio A / D is greater than or equal to 2.

[0009] Thus, surprisingly, the studs thus defined make it possible to reinforce the decoupling element to prevent it from deteriorating prematurely, while maintaining a relatively low natural frequency, making it possible to limit the noise in the passenger compartment of the vehicle in which the engine mount is integrated.

[0010] Preferably, the engine mount has one or more of the following characteristics, taken alone or in combination: the thickness C being greater than or equal to 10 mm, preferably greater than or equal to 14 mm, and / or less than 20 mm, preferably less than or equal to 16 mm; and / or distance B is greater than or equal to 3 mm and / or less than or equal to 6 mm; width A is greater than or equal to 4 mm and / or less than or equal to 20 mm; width D of the arms of the "H" is greater than or equal to 2 mm and / or less than or equal to 5 mm; the web of the "H" has a blind hole, preferably substantially at the center of the web and extending along the direction of the common axis of the two rings; each pad is flush with at least one of the two rings, in the direction of the common axis of the two rings; the decoupling means comprises an elastomer ring extending between the two rings, the elastomer ring preferably being formed from the material with the pads; the elastomer ring defines a ring arranged radially between one of the inner and outer rings, on the one hand, and the pads, on the other hand; the elastomeric material has a hardness between 25 and 60 Shore, in particular approximately equal to 40 Shore;the motor support includes at least one tilting limiting element of the inner ring relative to the outer ring, the tilting limiting element comprising a finger extending outward from one of the two rings and housed in a recess formed in the second of the two rings, two axial stops being formed in the recess to limit the displacement of the finger in the recess relative to the direction of the common axis of the two rings; the motor support includes two pads arranged angularly, symmetrically on either side of each finger; a means for limiting the relative displacement of one of the two rings relative to the other, in a plane normal to the common axis of the two rings, comprising at least one radial stop fixed to one of the two rings, with a radial clearance between the stop and the other of the two rings;at least one radial stop extends between the inner and outer rings, preferably having an inner curvature complementary to the curvature of the inner ring and / or an outer curvature complementary to the curvature of the outer ring; the inner and / or outer ring is covered with elastomeric material, at least opposite at least one radial stop; the motor support includes at least two radial stops opposed with respect to the center of the rings, preferably at least three radial stops regularly distributed angularly around the common axis of the two rings; the radial clearance is approximately 1 mm; the motor support further includes a means for limiting, preferably preventing, the relative rotation of the rings about the common axis of the two rings; at least one of the axial stops is projecting into the housing;elastomeric material is disposed between the finger and each of the two axial stops and in contact with the finger and one of the two axial stops, the elastomeric material being preferably compressed between the finger and each of the two axial stops, the elastomeric material preferably having a further compression ratio greater than or equal to 5% and / or less than or equal to 25%, preferably still approximately equal to 15%; the motor support comprises the same thickness of elastomeric material between the finger and each of the two stops; at least one axial stop extends in a direction substantially perpendicular to the direction of elongation of the finger; the motor support comprises two axial stops projecting in the housing, disposed on either side of the finger, the two projecting axial stops being opposite each other; the elastomeric material is overmolded on two opposite faces of the finger;The elastomeric material on the faces of the finger has a hardness between 20 and 45 Shore, in particular approximately equal to 25 Shore; the elastomeric material in contact between the finger and each of the two stops is bonded to the elastomeric ring; the finger has an "H" shaped cross-section; and the two opposite faces of the finger facing the axial stops are flat.

[0011] According to another aspect, a fan is described, particularly for vehicle ventilation installation, comprising an electric motor, in particular a brushless electric motor, a fan wheel, driven in rotation by the electric motor, and a motor support as described above, in all its combinations, the motor, in particular the stator of the motor, being fixed on the inner ring of the motor support.

[0012] According to yet another aspect, a heating, ventilation and / or air conditioning device for a motor vehicle is described, comprising a fan as described above in all its combinations. Brief description of the drawings

[0013] Other features, details and advantages will become clearer upon reading the description given below for guidance purposes in relation to the following figures. There figure 1 This is a schematic side view of a sample fan unit for a heating, ventilation, and / or air conditioning system in a motor vehicle. figure 2 is a schematic perspective view of an assembly formed by the motor mount and a housing for the fan device of the figure 1 . There figure 3 is a schematic perspective view of a subset of the motor support of the figure 2 . There figure 4is a schematic side view of a detail of the subset of the figure 3 . There figure 5 is a schematic perspective view of a pawl implemented in the motor support of the figures 2 And 3 . There figure 6 represents a detail of the subset of the figure 3 . There figure 7 schematically represents the detail of the figure 6 . There figure 8 represents a detail of a first variant of the subset of the figure 3 . There figure 9 schematically represents the detail of the figure 8 . There Figure 10 represents a detail of a second variant of the subset of the figure 3 . There figure 11 schematically represents the detail of the Figure 10 . There figure 12 represents a detail of a third variant of the subset of the figure 3 . There figure 13 schematically represents the detail of the figure 12 . Detailed description

[0014] There figure 1This schematically illustrates a side view of a fan device 10 for a heating, ventilation, and / or air conditioning system for a motor vehicle. Typically, such a heating, ventilation, and / or air conditioning system for a motor vehicle comprises a ventilation circuit, a fan device 10 for moving the air in the ventilation circuit, and means for heating and / or cooling the airflow moved by the fan device 10.

[0015] As illustrated in the figure 1The fan assembly 10 essentially comprises a fan wheel 12 and an electric motor, concealed here by a motor cover 14, to drive the fan wheel 12 in rotation around its axis A1. The electric motor is, for example, a brushless motor. The fan assembly 10 also includes a motor bracket 16 for mounting the electric motor onto a support. In this case, the electric motor is connected to a deflector 18 of the motor bracket 16, the deflector 18 forming part of the ventilation circuit of the heating, ventilation, and / or air conditioning system.

[0016] The following section describes the engine mount 16 in more detail.

[0017] As shown in the figures, the motor mount 16 essentially comprises an inner ring 20, an outer ring 22, and a decoupling element 24 interposed between the inner ring 20 and the outer ring 22. The decoupling element 24 is designed to limit the transmission of vibrations from one of the two rings 20, 22 to the other. The decoupling element 24 is formed here by a ring made of an elastomeric material. For example, the elastomeric material is SEBS (polystyrene-β-poly(ethylene-butylene)-β-polystyrene). The decoupling ring 24 is, for example, overmolded onto the inner ring 20 and outer ring 22. The decoupling ring 24 thus secures the inner ring 20 and outer ring 22. The inner ring 20, outer ring 22 and decoupling ring 24 are coaxial, with a common axis of rotation A of the fan wheel 12.

[0018] The assembly formed by the inner ring 20, outer ring 22, and decoupling ring 24 is received in a cavity of the deflector 18. The inner ring 20 is secured to the stator (not visible here) of the motor. The outer ring 22 is attached to the deflector 18. A layer of elastomeric material may be interposed between the outer ring 22 and the deflector 18.

[0019] According to the example shown in the figures, the inner ring 20 has a plurality of fingers 26. The fingers 26 extend radially outwards from the outer surface of the inner ring 20. In this case, each finger 26 has an H-shaped cross-section, comprising two substantially flat surfaces 261, 262 connected to each other by a core 263. The flat surfaces 261, 262 are normal to the direction of the axis A1 common to the rings 20, 22, 24. Each flat surface 261, 262 is covered with a layer 271, 272 of elastomeric material.

[0020] In the illustrated example, the inner ring 20 has three fingers 26. The fingers 26 are preferably regularly distributed angularly around the axis A1 of the inner ring 20.

[0021] The outer ring 22 comprises a plurality of housings 28. Each housing 28 is adapted to receive a respective finger 26. The housings 28 thus open at least onto the radially inner surface of the outer ring 22. In this case, the housings 28 are through-holes, opening onto both the radially inner surface of the outer ring 22 and the radially outer surface of the outer ring 22. The housings 28 are preferably regularly distributed angularly around the axis A1 of the outer ring 22.

[0022] The reception of the fingers 26 in the housings 28 allows to limit the possible relative tilting of the inner ring 20 with respect to the outer ring 22. By tilting, we mean here any movement of one of the rings 20, 22 with respect to the other 20, 22, outside the common median plane of the rings 20, 22, normal to the direction of the axis A1 common to the two rings 20, 22.

[0023] In the illustrated example, the housings 28 have dimensions such that a gap exists between the walls of each housing 28 and the finger 26 that is received there. In particular, a gap exists in the orthoradial direction. The walls of each housing 28 are coated with elastomeric material. Preferably, the elastomeric layer 30 that coats the walls of each housing 28 is formed along with the decoupling ring 24.

[0024] As is particularly evident on the figure 4In each housing 28, the finger 26 cooperates with two axial stops 32, 34 to further limit the axial displacement of the finger 26 in the housing 28. Here, the two axial stops 32, 34 protrude from the walls of the housing 28. By axial stop, we mean here a stop limiting the displacement along the direction of the common axis A1 of the rings 20, 22, 24.

[0025] In the illustrated example, the elastomeric material of one of the layers 271, 272 is in contact between one of the axial stops 32, 34 and one of the flat surfaces 261, 262 of the finger 26. This limits the possible movement of the finger 26 in the housing 28, along the axial direction A1. To further limit this axial movement, the elastomeric material of the layers 271, 272 located between the axial stops 32, 34 and the flat surfaces 261, 262 is compressed here. For example, the elastomeric material of layers 271, 272 located between the axial stops 32, 34 and the flat surfaces 261, 262 has an axial compression ratio greater than or equal to 5% and / or less than or equal to 25%, preferably approximately 15%. The axial compression ratio ε1, ε2 is defined as the ratio between: the difference between the thickness e10<, e20< of the elastomer layer on the flat surfaces 261, 262 of the fingers 26 before the placement of the fingers 26 between the axial stops 32, 34, on the one hand, and the thickness e1, e2 of the elastomer layer 271, 272 on the flat surfaces 261, 262 of the fingers 26 after the placement of the fingers 26 between the axial stops 32, 34, on the other hand; and the thickness e10<, e20< of the elastomer layer on the flat surfaces 261, 262 of the fingers 26 before the placement of the fingers 26 between the axial stops 32, 34: ε 1 = e 1 0 − e 1 e 1 0 , ε 2 = e 2 0 − e 2 e 2 0

[0026] Thus, the possible deformation of the elastomer material makes it possible to limit the transmission of vibrations from one of the two rings 20, 22 to the other of the two rings 20, 22. Concomitantly, the compression of the elastomer material of the layers 27 1 , 27 2 limits, however, the movement of the fingers 26 and, by the same token, the possible relative movements of the two rings 20, 22.

[0027] To achieve this, the elastomeric material forming layers 271 and 272 can also be chosen based on its hardness. This elastomeric material can, in particular, have a hardness greater than or equal to 25 Shore A and / or less than or equal to 60 Shore A.

[0028] The thicknesses e1, e2, on the one hand, and / or e10<, e20<, on the other hand, are advantageously approximately equal. This allows for centering of the fingers 26 between the two axial stops 32, 34.

[0029] The elastomer material of the layers 271, 272 can advantageously be overmolded onto the surfaces 261, 262 of the fingers 26, in particular concurrently with the overmolding of the decoupling ring 24. The elastomer material is thus held in position relative to the fingers 26. The mounting of the inner ring 20 relative to the outer ring 22 is also facilitated.

[0030] The first axial stop is formed here by a lug 32 of a pin 36. The pin 36 also has a substantially flat base 38, from which the lug 32 extends along an axis A2 intended to be parallel to the common axis A1 of the rings 20, 22, and 24 when the pin 36 is fixed to the outer ring 22. To ensure this fixing, the base 38 has two openings 40 intended to be press-fitted onto two complementary cylindrical reliefs formed on the outer ring 22. In addition, two notches 42 are provided at the longitudinal ends of the base 38. One of the two notches 42 receives a complementary rib formed by the outer ring 22 to guide the mounting of the pin 36 onto the outer ring 22. The lug 32 is press-fitted into a hole in the outer ring 22 so as to protrude into a recess 28 and thus form the first axial stop 32.More precisely, the lug 32 extends along the direction of the common axis A1 of the rings 20, 22, 24, from one of the walls of the housing 28, towards the finger 26 which is received there.

[0031] The second axial stop 34 is here formed by the deflector 18 which has protruding cylindrical reliefs, passing through an opening in the outer ring 22, so as to protrude into the housings 28, from a wall opposite to the first axial stop 32. The protruding cylinders also extend in a direction parallel to the direction of the axis A1 common to the rings 20, 22, 24.

[0032] Furthermore, as is particularly evident on the figures 2 And 3The decoupling ring 24 defines an annular groove 44 between the inner ring 20 and the outer ring 22. Within this groove 44, the decoupling ring 24 forms studs 46. The studs 46 are thus formed from the material along with the decoupling ring 24. In this case, the decoupling ring 24 forms six studs 46. These six studs 46 form three pairs of studs 46 which are substantially regularly distributed angularly around the axis A1. Each pair of studs 46 comprises, for example, one stud 46 on either side of a finger 26.

[0033] The studs 46 are primarily intended to reinforce the decoupling ring 24, particularly along the direction of the common axis A1 of the rings 20 and 22, to reduce the risk of cracking in the decoupling ring 24. However, the addition of corresponding material, which increases the rigidity of the decoupling ring 24, tends to simultaneously increase the resonance frequency of the engine mount 16, particularly of the decoupling ring 24. This increase in resonance frequency results in a potential increase in noise inside the passenger compartment of the vehicle equipped with the engine mount 16.

[0034] Therefore, the shape of the studs 46 is chosen to significantly increase the rigidity of the decoupling ring 24, along the direction of the common axis A1 of the rings 22 and 24, while limiting the increase in the resonance frequency of the motor mount 16. To achieve this, the studs 46 are essentially H-shaped. Strictly speaking, as illustrated in the figure 6 For example, the two arms 46int, 46ext are slightly curved, the Lint length of the inner arm 46int being slightly smaller than the Lext length of the outer arm 46ext. In practice, however, one can consider, as illustrated in the figure 7 , the plot 46 as having the shape of an "H" with two straight arms 46 1 , 46 2, of length L equal to the average of the lengths Lint, Lext of the inner arm 46int and outer arm 46ext.

[0035] The two arms 46int, 46ext, respectively 461, 462, of the "H" are separated by a distance B, oriented along the radial direction of the rings 20, 22, 24. Each arm 46int, 46ext, respectively 461, 462, of the "H" has a width D measured in the radial direction. The web 46a of the "H" has a width A, measured along the tangential direction. The width A of the web 46a and the distance B between the two arms 46int, 46ext, respectively 461, 462, of the "H" are such that the ratio A / B is greater than or equal to 1.4. In addition, the A / D ratio is greater than or equal to 2. Indeed, the inventors found that, surprisingly, by respecting these inequalities, it was possible to strengthen the decoupling ring 24, while maintaining a relatively low resonance frequency, in particular less than 75 Hz, preferably less than 50 Hz.

[0036] The width A of the core of the "H" 46 can be greater than or equal to 4 mm and / or less than or equal to 20 mm.

[0037] The distance B between the arms 46int, 46ext, respectively 461, 462, of the "H" 46, can be greater than or equal to 3 mm and / or less than or equal to 6 mm.

[0038] The width D of the arms 46int, 46ext, respectively 461, 462 of the "H" 46 can be greater than or equal to 2 mm and / or less than or equal to 5 mm.

[0039] To further improve the mechanical strength of the assembly, the studs 46 are advantageously flush with the inner ring 20 and / or the outer ring 22, depending on the direction of the common axis A1 of the two rings. To achieve this, the thickness C of the studs, measured along the direction of the common axis A1 of the rings 20, 22, 24, is preferably greater than or equal to 10 mm, preferably greater than or equal to 14 mm, and / or less than or equal to 20 mm, preferably less than or equal to 16 mm.

[0040] The pads 46 can also be made of polymer material, for example SEBS. The polymer material from which the pads 46 are formed can have a hardness between 25 and 60 Shore A, in particular approximately 40 Shore A. The use of a significantly softer material further reduces the resonant frequency of the motor mount 16.

[0041] The decoupling ring 24 also forms a ring 48, arranged here radially between the inner ring 20 and the studs 46. The ring 48 covers, for example, substantially the entire radially external surface of the inner ring 20.

[0042] The following section describes in more detail variations in the shape of plots 46, in relation to the figures 6 has 13 .

[0043] In the example of figures 6 and 7 : the thickness C of the block 46 is for example between 10 and 20 mm, in particular approximately equal to 14 mm; the width A of the web is for example between 3 and 6 mm, in particular approximately equal to 4.4 mm; the distance B between the arms 46int, 46ext, respectively 46 1 , 46 2 , of the “H”, is for example between 3 mm and 6 mm, in particular approximately equal to 3 mm.

[0044] With such pads, it was possible to make a decoupling ring 24 whose natural frequency was approximately equal to 32 Hz.

[0045] In the example of figures 8 and 9 : the thickness C of the block 46 is for example between 10 and 20 mm, in particular approximately equal to 16 mm; the width A of the web is for example between 6 and 10 mm, in particular approximately equal to 8.8 mm; the distance B between the arms 46int, 46ext, respectively 46 1 , 46 2 , of the “H”, is for example between 3 mm and 6 mm, in particular approximately equal to 6 mm.

[0046] With this geometry of studs 46, it was possible to produce a decoupling ring 24 whose natural frequency was approximately 32 Hz when a material with a hardness of approximately 25 Shore A was used. With the same geometry and a material with a hardness of approximately 40 Shore A, the natural frequency is approximately 47 Hz.

[0047] In the example of Figures 10 and 11 : the thickness C of the block 46 is for example between 10 and 20 mm, in particular approximately equal to 16 mm; the width A of the web is for example between 6 and 10 mm, in particular approximately equal to 8.8 mm; the distance B between the arms 46int, 46ext, respectively 46 1 , 46 2 , of the “H”, is for example between 3 mm and 6 mm, in particular approximately equal to 3 mm.

[0048] With this geometry of studs 46, it was possible to produce a decoupling ring 24 whose natural frequency was approximately 45 Hz when a material with a hardness of approximately 25 Shore A was used. With the same geometry and a material with a hardness of approximately 40 Shore A, the natural frequency is approximately 67 Hz.

[0049] Finally, in the example of Figures 12 and 13 : the thickness C of the block 46 is for example between 10 and 20 mm, in particular approximately equal to 16 mm; the width A of the web is for example between 10 and 20 mm, in particular approximately equal to 12 mm; the distance B between the arms 46int, 46ext, respectively 46 1 , 46 2 , of the “H”, is for example between 3 mm and 6 mm, in particular approximately equal to 6 mm.

[0050] It should be noted that the width A of the web 46a corresponds here to the sum of the two lengths A₁ and A₂ measured tangentially along a median arc of the web 46a, on either side of a hole 50. Here, the two lengths A₁ and A₂ are substantially equal, so that the hole 50 is substantially in the middle of the median arc of the web 46a. The hole 50 is advantageously blind, so as not to compromise the sealing of the motor mount 16. The hole 50 also facilitates the molding of the decoupling ring 24 and, in particular, of relatively large studs 46. It should be noted here that the web 46a may have more than one hole 50, preferably blind. The length A of the web 46a then corresponds to the sum of the lengths measured on either side of the different holes 50, along a median arc of the web 46a.

[0051] With this geometry of studs 46, it was possible to produce a decoupling ring 24 whose natural frequency was approximately 35 Hz when a material with a hardness of approximately 25 Shore A was used. With the same geometry and a material with a hardness of approximately 40 Shore A, the natural frequency is approximately 53 Hz.

[0052] This disclosure is not limited to the example described above, but encompasses all the variants and combinations that a person skilled in the art may consider in the context of the protection sought.

[0053] According to a first variant embodiment, only one axial stop is projecting in the housings 28. In this case, the finger received in the housing can be squeezed between the projecting axial stop, on the one hand, and the wall of the housing opposite the projecting axial stop, on the other hand.

[0054] Furthermore, axial stops can be achieved by means other than those described in the example above. For example, one or both axial stops can be achieved by a boss on the wall of the housing, extending towards the finger received in the housing.

[0055] Also, in the illustrated example, elastomeric material is present on the finger faces opposite the axial stops. Alternatively, or in addition, elastomeric material can be provided on the axial stops themselves, whether they are protruding or not. Preferably, however, contact between two layers of elastomeric material is avoided. Thus, only one of the two contacting surfaces is preferably covered with elastomeric material.

[0056] Furthermore, in the illustrated example, the inner ring forms fingers that fit into recesses formed in the outer ring. The reverse configuration is also possible, in which the outer ring has fingers oriented radially towards the inner ring and fitted into recesses formed in that inner ring.

[0057] It should also be noted that the decoupling element can take a form other than that of a decoupling ring.

[0058] The pads can be separate from the decoupling ring, the decoupling ring and the pads then forming a decoupling means.

Claims

1. Motor mount (16), particularly for a motor-fan unit of a vehicle ventilation system, comprising: • two coaxial rings (20; 22), including an inner ring (20) capable of receiving one or more motor elements and an outer ring (22) capable of being fixed to a housing forming a structural element, • a decoupling means (24) between the two coaxial rings (20; 22) comprising a plurality of studs (46) made of elastomeric material, interposed between the inner ring (20) and the outer ring (22), • each stud (46) having a thickness C measured in the direction of the common axis (A1) of the two rings (20; 22), each stud (46) having a substantially "H" shape, the two arms (46int, 46ext; 461, 462) of the "H" being separated by a distance B oriented along the radial direction of the rings (20, 22), each arm (46int, 46ext; 461, 462) having a width D measured in the radial direction of the rings (20, 22), the web (46a) of the "H" having a width A, measured along the tangential direction, • characterized in that the ratio A / B is greater than or equal to 1.4 and the ratio A / D is greater than or equal to 2.

2. Motor mount according to claim 1, wherein: • the thickness C being greater than or equal to 10 mm, preferably greater than or equal to 14 mm, and / or less than 20 mm, preferably less than or equal to 16 mm; and / or • the distance B is greater than or equal to 3 mm and / or less than or equal to 6 mm.

3. Motor mount according to claim 1 or 2, wherein the width A is greater than or equal to 4 mm and / or less than or equal to 20 mm.

4. Motor mount according to any one of claims 1 to 3, wherein the width D of the arms (46int, 46ext; 461, 462) of the "H" is greater than or equal to 2 mm and / or less than or equal to 5 mm.

5. Motor mount according to any one of the preceding claims, wherein the web (46a) of the "H" has a blind hole (50), preferably substantially in the center of the web (46a) and extending along the direction of the common axis (A1) of the two rings (20; 22).

6. Motor mount according to any one of the preceding claims, wherein each stud (46) is flush with at least one of the two rings (20; 22), in the direction of the common axis (A1) of the two rings (20; 22).

7. Motor mount according to any one of the preceding claims, wherein the decoupling means comprises an elastomeric ring (24) extending between the two rings (20; 22), the elastomeric ring (24) being preferably made of the same material as the studs (46).

8. Motor mount according to claim 7, wherein the elastomeric ring (24) defines a crown (48) arranged radially between one of the inner ring (20) and the outer ring (22) on one hand, and the studs (46) on the other hand.

9. Motor mount according to any one of the preceding claims, wherein the elastomeric material has a hardness between 25 and 60 Shore, in particular substantially equal to 40 Shore.

10. Fan (10), in particular for a vehicle ventilation system, comprising an electric motor, in particular a brushless electric motor, a fan wheel (12) driven in rotation by the electric motor, and a motor mount (16) according to any one of the preceding claims, the motor, in particular the stator of the motor, being fixed on the inner ring (20) of the motor mount (16).