Anti-vibration mount and vehicle comprising such an anti-vibration mount

Abstract

Anti-vibration mount (1) comprising a first frame (2), a second frame (3), an elastic body (4) connecting the first frame and the second frame, the elastic body allowing a relative displacement of the second frame with respect to the first frame in a first direction of vibration (Z) and in a second direction of vibration (X) perpendicular to the first direction of vibration, the elastic body being further adapted to mount a weight in the first direction of vibration (Z). An inertial body (15) is connected to the first frame by an elastic suspension (19) placed between the inertial body and the first frame along the second direction of vibration. An elastic lateral abutment body (20) is placed between the first frame and the inertial body to limit the relative displacement of the second frame with respect to the first frame in the second direction of vibration. The natural frequency of the inertial body is lower than 800 Hz.

Description

Technical Field

[0001] This specification relates to vibration damping frames and vehicles that include such vibration damping frames. Background Technology

[0002] Document WO2008152284A1 describes an example of such a shock-absorbing device. Summary of the Invention

[0003] The purpose of this specification is, in particular, to provide an anti-vibration frame capable of filtering high vibration frequencies, especially for mounting vehicle engines or hybrid powertrains, including internal combustion engines and motors.

[0004] Therefore, this specification proposes a vibration damping frame suitable for filtering and damping vibrations between a first element and a second element, the vibration damping frame comprising:

[0005] -A first frame suitable for fixing to the first element

[0006] - A second frame suitable for fixing to a second element.

[0007] - An elastic body connecting the first frame and the second frame, the elastic body allowing relative displacement of the second frame relative to the first frame at least along a first vibration direction and along a second vibration direction perpendicular to the first vibration direction, the elastic body also being able to support the weight of the second element in the first vibration direction, the first element being the vehicle body or chassis, and the second element being the vehicle's power unit.

[0008] - At least one inertial body, which is connected to the first frame by an elastic suspension inserted between the inertial body and the first frame in a second vibration direction.

[0009] - At least one elastic lateral abutment capable of limiting the relative displacement of the second frame with respect to the first frame in the second vibration direction.

[0010] Among them, the inertial body has a natural frequency of less than 800 Hz for vibration in the second vibration direction.

[0011] These arrangements ensure the filtering of high-frequency vibrations (more precisely, the filtering of vibrations at frequencies higher than the natural frequency), particularly in the second vibration direction.

[0012] The achievement of this effect does not result in the anti-vibration frame becoming larger or its durability being reduced (the elastic suspension of the inertial body is substantially compressed between the inertial body and the first frame by vibrations oriented in the second vibration direction).

[0013] In various embodiments of the vibration damping joint, one or more of the following arrangements (alone or any combination) may also be used:

[0014] - The elastic body has a tapered external shape, with a top molded on a second frame and an enlarged base molded on a rigid base, which is rigidly fixed to the first frame or inertial body;

[0015] -The inertial body has a natural frequency between 200 and 700 Hz in the second vibration direction;

[0016] - The inertial body is made of metal;

[0017] -The lateral abutment is integrally fixed to the second frame;

[0018] -The lateral abutment is at least integrally fixed to the inertial body;

[0019] - The lateral abutment is integrally fixed to the first frame and the inertial body, and the second frame can abut the lateral abutment by biasing the inertial body in the second vibration direction;

[0020] -The elastic body and the rigid base are integrally formed, and the rigid base is rigidly fixed to the first frame;

[0021] - The elastic body and the rigid base are integrally formed, and the rigid base is rigidly fixed to the inertial body (in this case, the rigid base is connected to the first frame through the inertial body and the elastic suspension);

[0022] - The elastic suspension includes an elastic lateral pad fixed to the inertial body and the first frame, the elastic lateral pad being arranged to be sheared under vibration in a first vibration direction and compressed under vibration in a second vibration direction.

[0023] - The inertial body includes two flanges perpendicular to the second vibration direction and connected to each other by a web. The first frame includes two sidewalls facing the two flanges of the inertial body. The elastic suspension includes two elastic lateral gaskets, each placed between one of the flanges of the inertial body and the sidewall of the first frame. Each elastic lateral gasket is configured to be sheared under vibration in the first vibration direction and compressed under vibration in the second vibration direction. The vibration damper includes two elastic lateral abutments that can limit the displacement of the second frame in two opposite directions by abutting against the flanges of the inertial body along the second vibration direction.

[0024] - The web of the inertial body extends substantially perpendicular to the first vibration direction and covers the elastic body and the second frame. The first frame further includes a cover wall covering the web, and the vibration-damping frame further includes an elastic upper gasket that connects the web of the inertial body and the cover wall of the first frame and is configured to withstand shear under vibration in the second vibration direction and compressive vibration under vibration in the first vibration direction. The elastic upper abutment is placed between the second frame and the web of the inertial body, and the two elastic lateral abutments are respectively placed between one of the flanges of the second frame and the inertial body.

[0025] -The upper abutment is integrally fixed to the second frame;

[0026] -The upper abutment body is integrally fixed to the inertial body;

[0027] - The vibration damping frame includes two inertial bodies perpendicular to the second vibration direction. The first frame includes two sidewalls facing the two inertial bodies respectively. The elastic suspension includes two elastic lateral pads, each elastic lateral pad being placed between one of the inertial bodies and the sidewall of the first frame. Each elastic lateral pad is arranged to be sheared under vibration in the first vibration direction and compressed under vibration in the second vibration direction. The vibration damping frame also includes two elastic lateral abutments, respectively placed between the first frame and one of the inertial bodies.

[0028] - The first frame includes two side walls that are interconnected by a cover wall, and the inertial body is disposed between the side walls of the first frame, located below the cover wall;

[0029] - The first frame includes two sidewalls interconnected by a cover wall, and the inertial body includes two flanges perpendicular to the second vibration direction and interconnected by a web. The flanges of the inertial body form the first frame in the second vibration direction, and the web of the inertial body covers the cover wall of the first frame.

[0030] - The vibration-damping frame also includes an elastic upper pad that connects the web of the inertial body to the cover wall of the first frame and is arranged to withstand shear under vibration in the second vibration direction and compression under vibration in the first vibration direction.

[0031] - The vibration-damping frame further includes an elastic upper abutment disposed between the second frame and the cover wall of the first frame;

[0032] - The two elastic lateral abutments are integrally formed with the elastic lateral pads of the elastic suspension and are molded onto the second frame by passing through grooves formed in the sidewalls of the second frame, and the two elastic lateral abutments are shaped and arranged to bias the flange of the inertial body when the second frame abuts the two elastic lateral abutments in the second vibration direction.

[0033] Furthermore, the present invention also relates to a vehicle comprising a body, a power unit, and at least one anti-vibration frame as defined above for connecting the body to the power unit, the elastic body supporting the weight of the power unit along a first vibration direction, i.e., the vertical direction.

[0034] The power unit may include at least one engine. Attached Figure Description

[0035] Referring to the accompanying drawings, other features and advantages of the vibration-damping frame will become apparent in the following description of five embodiments given as non-limiting examples.

[0036] In the attached diagram:

[0037] Figure 1 This is a schematic diagram of a vehicle whose power unit can be supported by one or more vibration-damping frames, particularly according to this specification.

[0038] Figure 2 This is a perspective view of the vibration-damping frame according to the first embodiment.

[0039] Figure 3 yes Figure 2 The longitudinal sectional view of the vibration damping frame shows no support for connecting to the power unit.

[0040] Figure 4 In the second embodiment, it is similar to Figure 2 The view.

[0041] Figure 5 yes Figure 4 The longitudinal sectional view of the vibration damping frame shows no support for connecting to the power unit.

[0042] Figure 6 In the third embodiment, it is similar to Figure 2 The view.

[0043] Figure 7 yes Figure 6 A partially exploded view of the vibration damping frame, without the brackets for connecting to the power unit.

[0044] Figure 8 yes Figure 7 The partial exploded view of the vibration-damping frame shows only the first frame and the inertial body.

[0045] Figure 9 yes Figure 8 The longitudinal sectional view of the vibration damping frame shows no support for connecting to the power unit.

[0046] Figure 10 It is similar to the fourth in terms of strength. Figure 2 The view.

[0047] Figure 11 yes Figure 10 The longitudinal sectional view of the vibration damping frame shows no support for connecting to the power unit.

[0048] Figure 12 In the fifth embodiment, it is similar to Figure 2 The view.

[0049] Figure 13 It is similar to the rear three-quarter view. Figure 12 The view.

[0050] Figure 14 yes Figure 12 The longitudinal sectional view of the vibration damping frame shows no support for connecting to the power unit.

[0051] Figure 15 This is a graph showing the dynamic stiffness curves of the X-axis in the fifth embodiment with and without an inertial body. Detailed Implementation

[0052] In the various figures, the same reference numerals denote the same or similar elements.

[0053] Figure 1 A vehicle V, particularly a motor vehicle, is represented very schematically, comprising a main body CV (or chassis) and a power unit M connected to the main body CV via one or more anti-vibration frames 1, at least one of which corresponds to this description.

[0054] The power unit can be, in particular, a hybrid powertrain, which includes an internal combustion engine and a motor for driving the vehicle. Alternatively, the power unit may consist of only the motor. In both cases, the operation of the motor generates relatively high-frequency vibrations, typically above 600 Hz.

[0055] The vibration-damping frame 1 will now be described in five embodiments. The first embodiment will be described in detail, and the other embodiments will be described more briefly, while emphasizing the differences between them. All features and advantages explained for one embodiment are also valid for the other embodiments, provided that such features and advantages do not contradict the features and advantages of another embodiment.

[0056] First Embodiment

[0057] In the first embodiment, referring to Figure 2 and Figure 3 The vibration damping frame 1 includes a first rigid frame 2 adapted to be fixed to a first element, particularly selected from the main body CV and the power unit M. For example, the first frame 2 can be fixed to the main body CV of the vehicle. The first frame 2 can be made of metal, such as a light alloy.

[0058] The first frame 2 may, for example, form a hoop 6, specifically including a substantially horizontal cover wall (extending along the X and Y axes) and two substantially vertical side walls 8 and 9 (extending along the Y and Z axes). Each of the side walls 8 and 9 may include a base 5 adapted for fixing to the main body CV of the vehicle, specifically by means of screws.

[0059] The vibration damping frame 1 also includes a second frame 3 adapted to be fixed to a second element, particularly selected from the main body CV and the power unit M. For example, the first frame 2 can be fixed to the vehicle's power unit M, particularly via bracket 11. The second frame 3 can be made of metal, such as steel plate.

[0060] The vibration-damping frame 1 also includes an elastic body 4 that connects the first frame 2 and the second frame 3.

[0061] The elastic body 4 allows the second frame 3 to be relatively displaced relative to the first frame 2 at least along a first vibration direction corresponding to the vertical axis Z and along a second vibration direction perpendicular to the first direction, the second vibration direction corresponding to the horizontal axis X.

[0062] The elastic body 4 is also suitable for supporting the weight of the power unit M along the Z-axis.

[0063] The elastic body 4 may have, for example, a conical external shape, having a top molded onto the second frame 3 and an enlarged base molded onto the rigid base 10.

[0064] The top of the elastic body 4 and the second frame 3 may define, for example, a channel 4a, which may or may not be a through channel opening along the Y-axis, in which the arm 11a of the support 11 is located and engaged.

[0065] As explained in the aforementioned document WO2008152284A1, the rigid base 10 can be fixed to the first frame 2, for example, by interlocking and clamping along the Y-axis.

[0066] The vibration damper 1 can be hydraulic. Specifically, in a known manner, the elastic body 4 can be hollow and, together with the rigid base 10, defines a chamber A, which communicates with a compensation chamber B via a narrow channel C. Chambers A, B, and the narrow channel C are filled with liquid. The rigid base 10 can form a partition 11 separating chambers A and B and defining the contraction channel C. The compensation chamber B can be defined between the rigid base 10 and a flexible bellows 13 molded in the lower part of the rigid base 10. For example, the narrow channel can have a resonant frequency between 5 and 20 Hz. These arrangements enable the suppression of low-frequency (e.g., less than 20 Hz) and relatively large-amplitude vibrations of the power unit M along the Z-axis, particularly those caused by the rolling motion of the vehicle.

[0067] The baffle 11 may include decoupling blades 14, which are also known in themselves, to filter out the vibrational motion of the power unit M along the Z-axis at higher frequencies (e.g., above 20 Hz) and relatively low amplitudes, especially due to the operation of the internal combustion engine of the power unit M.

[0068] The vibration-damping frame 1 also includes an inertial body 15, or may include several inertial bodies 15. The inertial body 15 may be made of metal, particularly of a light alloy.

[0069] The inertial body 15 is connected to the first frame 2 via an elastic suspension 19 along the X-axis between the inertial body 15 and the first frame 2.

[0070] The inertial body 15 may have an inverted U-shaped general shape, with two flanges 17 extending along the Y and Z axes and a web 16 connecting the two flanges 17 and extending along the X and Y axes. The flanges 17 may be arranged between one of the side walls 8 and 9 of the second frame 3 and the first frame 2, respectively, while the web 16 may be located below the cover wall 7 of the first frame 2.

[0071] The elastic suspension 19 may include two elastic lateral gaskets, each of which is inserted between a flange 17 of the inertial body and the sidewalls 8, 9 of the first frame 2. Each of these elastic lateral gaskets may, for example, be molded and adhered to the outer surface of the respective flange 17 and the inner surface of the respective sidewalls 8, 9.

[0072] Each elastic lateral gasket can be arranged to be subjected to shear under the influence of vibration of the power unit M along the Z-axis and to be subjected to compression under the influence of vibration along the X-axis.

[0073] The inertial body 15 and the elastic suspension 19 are sized such that the inertial body has a natural frequency of less than 800 Hz (e.g., between 200 and 700 Hz, particularly about 400 Hz) for vibrations along the X-axis, and preferably also for vibrations along the Z-axis.

[0074] The vibration damping frame may also include an elastic upper pad 18, which connects the web 17 of the inertial body and the cover wall 7 of the first frame 2. The elastic upper pad 18 may, for example, be molded and adhered to the lower surface of the cover wall 7 and the upper surface of the web 17.

[0075] The elastic upper gasket 18 is arranged to be sheared under the action of the vibration of the power unit M along the X-axis and compressed under the action of the vibration along the Z-axis.

[0076] The vibration damping frame 1 also includes at least one elastic lateral abutment 20, which is located between the second frame 3 and the inertial body 15 to limit the relative displacement of the second frame 3 relative to the first frame 2 along the X-axis.

[0077] Specifically, the vibration-damping frame 1 may include two elastic lateral abutments 20, which are respectively inserted between one of the side walls 8 and 9 of the first frame and one of the flanges 17 of the inertial body.

[0078] These lateral abutments 20 can be integrally formed with the second frame 3; in particular, they can be molded integrally with the elastic body 4.

[0079] The vibration-damping frame 1 may also include at least one elastic upper abutment 4b (two in the example shown) disposed between the second frame 3 and the web 16 of the inertial body to limit the displacement of the second frame 3 along the Z-axis.

[0080] The elastic upper abutment 4b can be integrally formed with the second frame. The elastic upper abutment 4b can be molded integrally with the elastic body 4.

[0081] Through the inertial body 15, these arrangements ensure the filtering of high-frequency vibrations originating from the power unit M, particularly vibrations with frequencies greater than 600 Hz. Such vibrations are especially likely to originate from the operation of the engine, which is part of the power unit M. This filtering is particularly effective for vibrations oriented along the X-axis, and is especially significant when the second frame 3 is supported on one of the flanges 17 of the inertial body via one of the elastic lateral adjacent bodies 20, for example, when the power unit M applies high torque (especially when the anti-vibration frame 1 is part of the swing suspension of the power unit M).

[0082] This effect is achieved without increasing the space occupied by the anti-vibration frame or reducing its durability (the elastic suspension 19 and the elastic upper pad 18 are subjected to either compression or shear, but the amplitude is limited by the general arrangement of the components of the anti-vibration frame 1).

[0083] Second Embodiment

[0084] Second embodiment, such as Figure 4 and Figure 5 As shown, the only difference from the first embodiment is that:

[0085] - The elastic lateral abutment 20a is integral with the inertial body 15, but not with the second frame 3.

[0086] - The elastic upper contact body 18 is integrated with the inertial body 15, but not with the second frame 3.

[0087] For example, the elastic transverse abutment 20a and the elastic upper abutment 22 can be integrally formed onto the inner surface of the web 16 and the flange 17 of the inertial body 15.

[0088] Third Embodiment

[0089] The third embodiment is in Figures 6 to 9As can be seen, the difference from the second embodiment is that the inertial body 15 is located on the outside of the first frame 2 instead of the inside.

[0090] Specifically, the flange 17 of the inertial body forms the first frame 2 along the X-axis, and the web 16 of the inertial body covers the cover wall 7 of the first frame.

[0091] The elastic upper gasket 18 can be, for example, molded and adhered to the upper surface of the cover wall 7 and the lower surface of the web 17.

[0092] The transverse abutment 20b is integral with the side walls 8 and 9 of the first frame 2 and the flange 17 of the inertial body. The tops of the second frame 3 and the elastic body 4 can abut against the abutment 20b to limit the displacement of the second frame 3 along the X-axis.

[0093] The lateral pads of the elastic suspension 19 can be molded integrally with the lateral abutment 20b. The elastic body of the lateral pads and the elastic body of the lateral abutment 20b are located on the same side of the vibration-damping frame, for example, traversing the grooves 8a and 9a, which are formed in the corresponding sidewalls 8 and 9 of the first frame.

[0094] Two elastic lateral abutments 20b are shaped and arranged such that when the second frame 3 abuts against the elastic lateral abutments 20b along the second vibration direction X, the flange 17 of the inertial body is biased (through recesses 8a, 9a).

[0095] The elastic upper abutment 18 can be integrally formed with the cover wall 7 of the second frame. In particular, the elastic upper abutment 18 can be molded and adhered to the lower surface of the cover wall 7.

[0096] Fourth embodiment

[0097] Fourth embodiment, such as Figure 10 and 11 As shown, the difference from the second embodiment is that the vibration-damping frame 1 includes two independent inertial bodies 15a, which roughly correspond to Figure 2 The two flanges 17 of the inertial body 15 are not connected to each other through the web.

[0098] The elastic lateral pads of the suspension 19 are respectively molded and adhered to the outer surface of the corresponding inertial body 15a and the inner surface of the side walls 8 and 9 of the corresponding second frame.

[0099] The elastic lateral abutments 20c are respectively molded and adhered to the inner surface of the inertial body 15a.

[0100] One or more elastic upper abutments 4b are similar to those in the first embodiment and are capable of abutting the lower surface of the cover wall 7 of the first frame 2.

[0101] Fifth Embodiment

[0102] Fifth embodiment, such as Figures 12 to 14 As shown, the difference from the second embodiment is that the rigid base 10 is not rigidly fixed to the first frame.

[0103] In this embodiment, the rigid base 10 is connected to the first frame via the inertial body 15, and the base 10 is rigidly fixed to the inertial body 15.

[0104] The rigid base 10 can be secured to the inertial body 15 in any known manner. For example, the rigid base 10 can be secured to the inertial body 15 along the Y-axis by interlocking and clamping, similar to the securing of the rigid base 10 to the first frame 2 in the previous four embodiments, i.e., as described in or similar to the previous document WO2008152284A1. For this purpose, the rigid base 10 can be fitted along the Y-axis into two inner grooves 23 formed at the lower end of the inner surface of the flange 17 facing the inertial body 15 until it abuts against the rear wall portion 24, which connects to the flange 17.

[0105] The elastic lower pad 21 can be inserted between the lower end of the inertial body 15 and the horizontal lower wall 27 of the first frame to vertically support the weight of the power unit M.

[0106] Effects of the present invention

[0107] Figure 15 The dynamic stiffness curve 25 of the vibration-damping frame of the fifth embodiment along the X-axis is compared with the dynamic stiffness curve 26 of a similar vibration-damping frame without the inertial body 15 (meaning a vibration-damping frame similar to the second embodiment, wherein the adjacent body 20 is integral with the side walls 8 and 9 of the first frame 2).

[0108] The figure shows that the dynamic stiffness of the bracket according to the invention decreases significantly from 600 Hz, which allows for the filtering of high-frequency vibrations along the X-axis, an effect not permitted by comparable prior art devices, as explained above. The vibration-damping bracket according to this specification also allows for the filtering of high-frequency vibrations along the Z-axis in a manner at least as effective as in the prior art.

Claims

1. A vibration damping frame (1) adapted to filter and dampen vibrations between a first element and a second element, said vibration damping frame (1) comprising: - A first frame (2), adapted to be fixed to the first element, - A second frame (3), adapted to be fixed to the second element, - An elastic body (4) connecting the first frame (2) and the second frame (3), the elastic body (4) allowing the second frame (3) to have relative displacement with respect to the first frame (2) at least along a first vibration direction (Z) and along a second vibration direction (X) perpendicular to the first vibration direction, the elastic body (4) also being able to support the weight of the second element in the first vibration direction (Z), the first element being a vehicle body or chassis, and the second element being a vehicle power unit (M). - At least one inertial body (15; 15a) is connected to the first frame (2) by an elastic suspension (19) inserted between the inertial body (15; 15a) and the first frame (2) in the second vibration direction (X). - At least one elastic lateral abutment (20; 20a; 20b; 20c; 20d) capable of limiting the relative displacement of the second frame (3) with respect to the first frame (2) in the second vibration direction (X), The inertial body (15; 15a) has a natural frequency of less than 800 Hz for vibration in the second vibration direction (X). The elastic body (4) has a conical shape that extends along the first vibration direction (Z) from the top of the second frame (3) to an enlarged base molded on a rigid base (10), which is rigidly fixed to the first frame (2) or the inertial body (15; 15a).

2. The vibration-damping frame (1) according to claim 1, characterized in that, The inertial body (15; 15a) has a natural frequency between 200 and 700 Hz in the second vibration direction (X).

3. The vibration-damping frame (1) according to claim 1, characterized in that, The inertial body (15; 15a) is made of metal.

4. The vibration-damping frame (1) according to claim 1, characterized in that, The elastic lateral abutments (20; 20a; 20b; 20c; 20d) are integrally fixed to the second frame (3) or at least fixed to the inertial body (15; 15a).

5. The vibration-damping frame (1) according to claim 1, characterized in that, The elastic suspension (19) includes elastic lateral pads fixed to the inertial body (15; 15a) and the first frame (2), the elastic lateral pads being arranged to withstand shear under vibration in the first vibration direction (Z) and compression under vibration in the second vibration direction (X).

6. The vibration-damping frame (1) according to claim 1, characterized in that, The inertial body (15) includes two flanges (17) perpendicular to the second vibration direction (X) and interconnected by a web (16). The first frame (2) includes two sidewalls (8, 9) facing the two flanges (17) of the inertial body. The elastic suspension (19) includes two elastic lateral gaskets, each placed between one of the flanges (17) of the inertial body and the sidewalls (8, 9) of the first frame. Each elastic lateral gasket is arranged to be sheared under vibration in the first vibration direction (Z) and compressed under vibration in the second vibration direction (X). The vibration-damping frame, including two elastic lateral abutments (20; 20a; 20b; 20d), can limit the displacement of the second frame (3) in two opposite directions by abutting the flanges of the inertial body along the second vibration direction (X).

7. The vibration-damping frame (1) according to claim 6, characterized in that, The web (16) of the inertial body extends substantially perpendicular to the first vibration direction (Z) while covering the elastic body (4) and the second frame (3). The first frame (2) further includes a cover wall (7) covering the web (16). The vibration-damping frame further includes an elastic upper gasket (18) connecting most of the webs (16) of the inertial body and the cover wall (7) of the first frame. The upper gasket (18) is arranged to withstand shear under vibration in the second vibration direction (X) and compression under vibration in the first vibration direction (Z). An elastic upper abutment (4b, 22) is provided between the second frame (3) and the web (16) of the inertial body. The two elastic lateral abutments (20; 20a; 20d) are respectively provided between the second frame (3) and one of the flanges (17) of the inertial body.

8. The vibration-damping frame (1) according to claim 1, comprising two inertial bodies (15a) perpendicular to the second vibration direction (X), the first frame (2) comprising two sidewalls (8, 9) facing the two inertial bodies (15a) respectively, the elastic suspension (19) comprising two elastic lateral pads, each elastic lateral pad being between one of the inertial bodies (15a) and the sidewalls (8, 9) of the first frame, each elastic lateral pad being configured to be sheared under vibration in the first vibration direction (Z) and compressed under vibration in the second vibration direction (X), and the vibration-damping frame comprising two elastic lateral abutments (20c), the two elastic lateral abutments (20c) being respectively disposed between the second frame (3) and one of the inertial bodies (15a).

9. The vibration-damping frame (1) according to claim 1, characterized in that, The first frame (2) includes two side walls (8, 9) connected to each other by a cover wall (7), and the inertial body (15) includes two flanges (17) perpendicular to the second vibration direction (X) and connected to each other by a web (16). The flanges (17) of the inertial body form the first frame (2) in the second vibration direction (X), and the web (16) of the inertial body covers the cover wall (7) of the first frame (2).

10. The vibration-damping frame (1) according to claim 9, characterized in that, The two elastic lateral abutments (20b) are integrally formed with the elastic lateral pads of the elastic suspension (19) and are molded onto the second frame by passing through grooves (8a, 9a) respectively, the grooves (8a, 9a) being formed on the sidewalls (8, 9) of the second frame, and the two elastic lateral abutments (20b) are shaped and arranged to bias the flange (17) of the inertial body when the second frame (3) abuts the two elastic lateral abutments (20b) in the second vibration direction (X).

11. A vehicle comprising a body (CV), a power unit (M), and at least one vibration damping frame (1) according to claim 1, the vibration damping frame (1) connecting the body (CV) to the power unit (M), the elastic body (4) supporting the weight of the power unit (M) along a first vibration direction (Z) perpendicular to it.

12. The vehicle according to claim 11, characterized in that, The power unit (M) includes at least one engine.

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