Motor vehicle with rollable front frame and rear frame with two drive wheels

Abstract

A motor vehicle (1) comprising a rollable front chassis (3) and a non-rollable rear chassis (5). The front chassis is connected to the rear chassis by means of a linkage system (23) comprising a four-bar linkage defining a roll axis which remains in a fixed position and on a support surface of the motor vehicle (1) when the motor vehicle performs a roll motion.

Description

TECHNICAL FIELD

[0001] The present invention relates to improvements to a motor vehicle comprising a rollable front chassis and a non-rollable rear chassis, on which the rear driving wheels are mounted. BACKGROUND

[0002] Over the years, different types of vehicles have been developed, in particular for the transport of goods, which comprise a rollable (i.e. tiltable) front chassis and a rear chassis formed by a chassis with a pair of driving wheels, which does not undergo roll movements, i.e. in which the driving wheels remain in a plane orthogonal to the plane of forward motion of the motor vehicle, and a mechanism for connecting between the front chassis and the rear chassis.

[0003] An example of a vehicle of this type is disclosed in US 4666018. In this prior art vehicle, the connection between the rollable front chassis and the non-rollable rear chassis is obtained by means of a joint whose axis of rotation has an inclination in the top-down direction with respect to the direction of forward motion of the vehicle. This prior art vehicle has some drawbacks. In particular, when the front chassis rotates with respect to the rear of the vehicle about the axis of the joint, in addition to the roll movement, a yaw movement also occurs, i.e. a yaw movement of the vehicle about a vertical central axis.

[0004] In some rollable vehicles, the roll axis is not on the ground on which the vehicle stops and moves forward. In this case, even if the roll axis is horizontal, i.e. parallel to the ground (which prevents the occurrence of a yaw movement when the vehicle performs a roll movement), when the front chassis tends to lower, a pitch movement occurs.

[0005] To reduce the problems of this type of vehicle, EP1070658 discloses a vehicle with a rollable front chassis and a non-rollable rear chassis, comprising a linkage system for connecting between the front chassis and the rear chassis. The linkage system is formed by a four-bar linkage mechanism of isosceles trapezoidal shape, with two transverse members of different lengths and two uprights of the same length. The front chassis is pivoted to the lower transverse member of shorter length, while the rear chassis is integral with the upper transverse member of longer length. The roll movement of the front chassis is allowed by the deformation of the four-bar linkage mechanism.

[0006] This known mechanism allows the roll axis of the front frame to be placed at the level of the ground on which the vehicle is moving forward, or even below this level. If the roll axis is horizontal, the yaw movement is avoided. However, the roll axis does not remain in a fixed position. Thus, even when the vehicle is upright (zero roll axis), the roll axis is on the ground, i.e. on the road surface, and when the vehicle is in roll movement (non-zero roll angle), the roll axis forms a curvilinear shape, moving both with respect to the road surface and with respect to the longitudinal vertical median plane of the vehicle. In other words, the roll axis does not remain on the centerline of the vehicle. These displacements do not allow the pitch movement accompanying the roll movement to be eliminated. Furthermore, when the axes of the hinges of the four-bar linkage are inclined with respect to the road surface, the yaw movement of the front frame with respect to the rear frame is added to the unavoidable pitch movement.

[0007] Therefore, there is still a need to improve the structure of a vehicle having a roll front frame and a non-roll rear frame, in order to avoid or reduce the drawbacks of the prior art vehicles. SUMMARY

[0008] According to one aspect, in order to minimize the drawbacks of the prior art, a motor vehicle is provided, comprising a roll front frame, a rear frame having two non-roll rear drive wheels, and a linkage system for connecting between the roll front frame and the rear frame. The linkage system comprises a four-bar linkage, and more precisely, a hinged parallelogram.

[0009] In an embodiment, the linkage system comprises a left upright (also indicated as a left swing arm) pivoted to the rear frame about a left lower pivot axis, a right upright (also indicated as a right swing arm) pivoted to the rear frame about a right lower pivot axis, and an upper cross member pivoted in an upper point of the left upright about a left upper pivot axis and in an upper point of the right upright about a right upper pivot axis.

[0010] The linkage system further comprises an intermediate cross member hingedly connected to the left upright about a left intermediate pivot axis arranged between the left lower pivot axis and the left upper pivot axis, and hingedly connected to the right upright about a right intermediate pivot axis arranged between the right lower pivot axis and the right upper pivot axis.

[0011] The intermediate transverse members are hingedly connected to the front frame about a lower central pivot axis, and the upper transverse members are hingedly connected to the front frame about an upper central pivot axis. The distance between the lower central pivot axis and the upper central pivot axis is substantially the same as the distance between the left intermediate pivot axis and the left upper pivot axis and the distance between the right intermediate pivot axis and the right upper pivot axis. In an upright, non-tilted position of the vehicle on a support surface, the lower central pivot axis is located below the plane in which the left and right intermediate pivot axes lie, and the pivot axes of the linkage system are located in a vertical plane parallel to the vertical median plane of the motor vehicle, the lower central pivot axis and the upper central pivot axis being located on the vertical median plane of the motor vehicle.

[0012] In practice, the uprights or rockers and the two transverse members form a triple four-bar linkage, in addition to the elements to which the rear frame is stationary and to which the two uprights are pivoted, and more precisely a triple hinged parallelogram, in which the tilting front frame is pivoted to the two transverse members, which are movable relative to the rear frame, the linkage connecting between the front frame and the hinged parallelogram being defined by two central pivot axes, which are parallel to each other and to the axes of the four-bar linkage.

[0013] Further advantageous features and embodiments of the motor vehicle are described below and defined in the appended claims, which form an integral part of the present description.

[0014] In the present description, the term "horizontal" generally designates a direction parallel to the support surface of the motor vehicle, for example a road surface. The term "vertical" designates a direction orthogonal to the support surface. BRIEF DESCRIPTION OF DRAWINGS

[0015] In the drawings:

[0016] Figure 1 shows a side view of the vehicle in a first embodiment and in an upright position, i.e. with zero tilting angle;

[0017] Figure 2 and Figure 3 shows an isometric view of the vehicle according to Figure 1 ;

[0018] Figure 4 shows a rear view according to IV-IV of Figure 1 ;

[0019] Figure 5 shows an isometric view of the rear (rear frame) of the vehicle according to Figures 1 to 4 ;

[0020] Figure 6 shows a section according to VI-VI of Figure 1 ;

[0021] Figure 7 A vehicle according to Figures 1 to 6 is shown in an isometric view in a position where the front frame is tilted, i.e. has a non-zero roll angle;

[0022] Figure 8 A rear view similar to Figure 4 is shown, where the vehicle is tilted as in Figure 7 ;

[0023] Figure 9 A section similar to a section of Figure 6 is shown, where the front frame of the vehicle is tilted as in Figure 7 ;

[0024] Figure 10A and Figure 10B show a simplified representation of a section of Figure 6 and Figure 9 ;

[0025] Figure 11 A side view similar to Figure 1 is shown, where the vehicle in another embodiment is in an upright, i.e. non-tilted position;

[0026] Figure 12 and Figure 13 show an isometric view of a vehicle according to Figure 11 ; and

[0027] Figure 14 An isometric view of a vehicle according to Figure 11 is shown in a tilted position, i.e. where the front frame is tilted with a non-zero roll angle. DETAILED DESCRIPTION

[0028] Embodiments will be described below with reference to the accompanying drawings. The person skilled in the art will understand that the described embodiments are non-limiting examples of the invention.

[0029] In the drawings, the arrows U, D indicate the vertical "up-down" direction, the arrows L, R indicate the lateral "left-right" direction, and the arrows F, B indicate the "front-back" direction. In the description and the attached claims, the terms "right" and "left" refer to the right and left sides with respect to a driver in a driving position on the vehicle. The definition "vertical" indicates a position of the vehicle that is orthogonal to the ground or to the support surface in a stationary and upright position, i.e. not tilted about the roll axis. Unless otherwise indicated, the definitions "under", "above", "upper", "lower", "intermediate" with reference to the position of a vehicle component or part refer to the vehicle in an upright and stationary, not tilted position on the support surface or ground surface.

[0030] A first embodiment of a vehicle according to the invention is illustrated in Figures 1 to 1 0.

[0031] The vehicle 1 comprises a front frame 3 and a rear frame 5. The front frame 3 comprises a front steered wheel 7 which is constrained to a steering column 11, for example by means of a telescopic fork 9, the steering column 11 being integral with a handlebar 13 and rotatably housed in a steering tube 15 to rotate about a steering axis A-A (Fig. 1). Figure 1 ).

[0032] The front frame 3 can be integral with a frame which extends towards the rear of the vehicle up to above the rear frame 5. The rear portion of the frame which is integral with the front frame 3 is indicated with 3A. The vehicle's seat (not shown) and a container for loading objects can be fixed on the rear portion 3A. Alternatively, by providing a shorter rear portion 3A of the frame, the container containing the loading objects can be arranged on the rear frame 5. In the first case, there is the advantage of the loading objects leaning with the front frame of the vehicle, making driving more stable.

[0033] The rear frame 5 comprises a left rear drive wheel 17A and a right rear drive wheel 17B. The rear drive wheels 17A, 17B receive their power from a motor 21, for example an internal combustion engine. However, the vehicle 1 can also be provided with one electric motor or two electric motors associated with the two rear drive wheels 17A, 17B.

[0034] The front frame 3 is connected to the rear frame 5 by means of a linkage system 23, which is particularly visible in Figure 5 and Figure 6 and simplified in Figure 10A , Figure 10B In the illustrated embodiment, the linkage system 23 comprises a left upright or left swing arm 25A and a right upright or right swing arm 25B. The left upright 25A is pivoted to the frame 5 about a hinge which defines a left lower pivot axis 27A, while the right upright 25B is pivoted to the frame 5 about a hinge which defines a right lower pivot axis 27B. In the illustrated embodiment, the hinges which define the right lower pivot axis 27A and the left lower pivot axis 27B are integral with a lower transverse member 29 of the linkage system 23.

[0035] The left upright or left swing arm 25A is also pivoted to an upper transverse member 33 by means of a hinge which defines a left upper pivot axis 31A. Likewise, the right upright or right swing arm 25B is pivoted to the upper transverse member 33 by means of a hinge which defines a right upper pivot axis 31B. The left pivot axes 27A, 31A and the right pivot axes 27B, 31B are parallel to each other and each lie in a vertical plane. The left upright 25A and the right upright 25B are parallel to each other, that is to say, the plane in which the pivot axes 27A, 31A lie is parallel to the plane in which the pivot axes 27B, 31B lie.

[0036] In the example illustrated, the right and left pivot axes 27A, 27B, 31A, 31B are parallel to the front-rear direction identified by the arrows F, B, i.e. parallel to the direction of travel of the motor vehicle 1 when it travels along a straight line.

[0037] The left pivot axes 27A, 31A are coplanar with each other in a plane which is vertical, i.e. orthogonal to the support surface S of the vehicle 1, when the vehicle is stationary and not inclined, i.e. has a zero roll angle. Figure 4 Figure 6 This plane is indicated with PA in Figure 6 and Figure 10A . The left upper pivot axis 31A and the right upper pivot axis 31B are coplanar and lie on a plane parallel to the ground, i.e. parallel to the support surface S of the vehicle 1. Likewise, the right pivot axes 27B, 31B are coplanar with each other on a plane parallel to the plane PA in which the left pivot axes 27A, 31A lie (indicated with PB in Figure 6 and Figure 10A ). The pivot axes 27A, 27B are coplanar and lie on a plane parallel to the plane in which the pivot axes 31A, 31B lie. The support surface S, which can correspond to the ground or road surface on which the motor vehicle 1 is stopped, is in fact a geometric plane tangent to the wheels of the motor vehicle 1.

[0038] In the present context, the reference numerals 27A, 27B, 31A, 31B and the other reference numerals used hereinafter to indicate pivot axes are also used to indicate the respective hinges which define these axes. For example, the reference numeral 27A indicates both the left pivot axis between the lower cross-member 29 and the left upright 25A, and the hinge which connects the lower cross-member 29 and the left upright 25A to each other.

[0039] The right upright 25B and the left upright 25A, the lower cross-member 29 and the upper cross-member 33, and the respective hinges define a four-bar linkage. In the embodiment illustrated, the four-bar linkage 25A, 25B, 29, 33 is rectangular in shape (vehicle upright and zero roll angle, Figure 6 ).

[0040] The upper cross-member 33 has an isosceles triangle shape, with its base extending from the left upper pivot axis 31A to the right upper pivot axis 31B, and its apex pointing downwards.

[0041] ​In the illustrated embodiment, the upper cross-member 33 is formed by three linear elements, and more precisely by the following elements: a bottom edge element 37C extending in the left-right direction (L-R) between the upper pivot hinges 31A, 31B; a left side edge element 37A; and a right side edge element 37B. The side edge elements 37A, 37B converge in the apex of an isosceles triangle defined by the upper cross-member 33. The apex defines an upper central hinge axis 39 by means of which the front frame 3 is connected to the rear frame 5. The upper central hinge 39 defines an upper central pivot axis, which is also indicated with the same reference 39, in accordance with the nomenclature and numbering defined above for the hinges already described.

[0042] In other embodiments, the bottom edge element 37C can be omitted. However, it provides greater rigidity to the upper cross-member 33.

[0043] As Figure 5 and Figure 6 particularly shown again, the linkage system 23 also comprises an intermediate cross-member 41 also in the shape of an isosceles triangle, having a left side edge element 43A and a right side edge element 43B. The left side edge element 43A is pivoted to the left upright 25A at an intermediate position between the lower left hinge 27A and the upper left hinge 31A by means of a left intermediate hinge 45A. Likewise, the right side edge element 43B is pivoted to the right upright 25B at an intermediate position between the lower right hinge 27B and the upper right hinge 31B by means of a right intermediate hinge 45B. The base of the isosceles triangle defining the intermediate cross-member 41 thus has a base extending from the left intermediate hinge 45A to the right intermediate hinge 45B. The two side edge elements 43A, 43B converge towards the apex of the isosceles triangle, at which the central lower hinge 47 is formed, which defines a lower central pivot axis connecting the rear frame 5 to the front frame 3. The upper central pivot axis 39 and the lower central pivot axis 47 are parallel to the pivot axes connecting the uprights 25A, 25B, the lower cross-member 29 and the upper cross-member 33 to each other. In the position of the vehicle at rest, upright and with zero roll angle (Fig. 1), the central upper pivot axis 39 and the central lower pivot axis 47 lie on the vertical median plane of the vehicle 1, indicated with PC in Figs. Figure 5 , Figure 6 Figure 6 and Figure 10A .

[0044] ​In the illustrated example, when the vehicle 1 is in the upright position, with zero roll angle (the vehicle is not rolled), the left intermediate pivot axis 45A lies on a vertical plane containing the left upper pivot axis 31 A and the left lower pivot axis 27A, while the intermediate pivot axis 45B lies on a vertical plane containing the right upper pivot axis 31 B and the right lower pivot axis 27B. The lower central pivot axis 47 and the upper central pivot axis 39 lie on the vertical midplane of the motor vehicle 1.

[0045] In the illustrated embodiment, the intermediate cross-member 41 comprises, in addition to the left side element 43A and the right side element 43B, a bottom element 43C parallel to the bottom element 37C and to the lower cross-member 29, which provides greater rigidity to the intermediate cross-member 41.

[0046] As can be seen from Figure 6 , the lower central hinge 47 and the pivot axis defined thereby are placed at a lower height with respect to the upper central pivot hinge 39 and the respective upper central pivot axis defined thereby. Moreover, the lower central pivot axis 47 lies below the plane in which the left pivot axis 45A and the right pivot axis 45B lie, through which the intermediate cross-member 41 is respectively pivoted to the left upright 25A and to the right upright 25B. In the illustrated example, also the upper central pivot axis 39 lies below the plane in which the left pivot axis 45A and the right pivot axis 45B lie.

[0047] The shape of the upper cross-member 33 and of the intermediate cross-member 41 is identical, that is to say, the mutual distance of the triangular apexes defined by the pivot axes 31 A, 31 B, 39 for the upper cross-member 33 and by the pivot axes 45A, 45B, 47 for the lower cross-member 29 is identical. The distance X in vertical direction between the upper central pivot axis 39 and the lower central pivot axis 47 Figure 6 is the same as the distance in vertical direction between the pivot axes 31 A and 45A, or 31 B and 45B.

[0048] Moreover, the linkage system 23 is configured so that the distance Y of the lower central pivot axis 47, that is to say, the distance from the support surface S of the vehicle 1, is equal to the distance Y between the pivot axes 45B and 27B or to the distance Y between the pivot axes 45A and 27A.

[0049] As can be seen in particular in Figure 10A and Figure 10BAs can be seen, the linkage system 23 thus configured substantially defines a triple four-bar linkage and, more particularly, a triple hinged parallelogram, comprising two uprights 25A, 25B and three cross members, namely: an intermediate cross member 41, an upper cross member 33 and a lower cross member 29. The front frame is pivoted to the upper cross member and to the intermediate cross member and can perform a roll movement with respect to the frame 5. The lower cross member 29 is fixed with respect to the rear frame 5. The apex indicated with A, which is always kept on the vertical median plane of the vehicle 1, is the portion of the lower cross member 29 which is stationary with respect to the rear frame 5, at which the straight lines R1 and R2 passing through the left lower pivot axis 27A and through the right lower pivot axis 27B, respectively, and parallel to the side elements 43A, 43B (i.e. parallel to the sides converging towards the lower central pivot axis 47 of the isosceles triangle whose base extends between the intermediate pivot axes 45A, 45B) converge. The apex A is the locus of the roll axis of the front frame 3 of the vehicle 1.

[0050] Preferably, in the illustrated embodiment, the point A lies on the support surface S of the motor vehicle 1. The roll axis, which is parallel to the axes of the hinges of the linkage system 23, is preferably parallel to the support surface S.

[0051] As can be seen, with the above-described linkage system 23, for any angle of inclination of the front frame, and therefore for any roll angle of the front frame (in Figure 10A equal to 0° and in Figure 10B equal to a), the roll axis is always kept in substantially the same position and on the ground (surface S). Therefore, with respect to the linkage systems of the prior art, all the drawbacks caused by the shift of the roll axis when the roll angle of the vehicle changes are eliminated, and in the particular configuration described, the advantage of placing the roll axis on the ground level is also achieved.

[0052] Figures 1 to 9 The vehicle 1 of the type described in the introductory part of the description, in addition to the above-described components, also comprises a suspension 51, as can be seen in particular in Figure 1 , Figure 6 and Figure 9 .

[0053] In this embodiment, the suspension 51, which can comprise springs and shock absorbers, is arranged between the linkage system 23 and the assembly comprising the engine 21 and the rear drive wheels 17A, 17B. Therefore, in this case, the linkage system 23 forms part of the unsprung mass of the vehicle, while the rear frame 5, with the engine 21 and the rear drive wheels 17A, 17B, forms part of the sprung mass.

[0054] Figures 11 to 14 Another embodiment of the motor vehicle 1 is shown, in which elements identical or equivalent to those already described are indicated with the same reference numerals and will not be described in detail again. Figures 11 to 14embodiments of the application and Figures 1 to 1 The main difference between the embodiments of the application and

[0055] In the schematic view of the figures, the rotation axes of the hinges connecting the various components of the linkage system 23, in particular axes 27A, 27B, 31A, 31B, 45A, 45B, 39 and 47, are parallel to the support surface, i.e. to the road surface S on which the vehicle 1 is located. This condition is preferred because in this way the roll axis is also on the plane S and remains on this plane and on the centre line of the motor vehicle 1 independently of the roll angle with which the front frame 3 rotates about this axis.

[0056] This eliminates the pitch and yaw movements which, in other roll vehicles of this type, are generated when the motor vehicle performs a roll movement.

[0057] However, it is also possible to arrange the pivot axes of the linkage system and the central pivot axes 39 and 47 inclined with respect to the support surface S, rather than parallel to it.

[0058] In this case, the roll axis will also be inclined with respect to the support surface S. Preferably, the inclination will be such that the roll axis passes through the straight line of intersection between the support surface S and a transverse plane orthogonal to the support surface S and containing the rotation axes of the rear drive wheels 17A, 17B. This transverse plane is indicated by T in Figure 1 and Figure 11 in figures 1 and 2.

[0059] In this configuration, the motor vehicle 1 will not be subjected to a pitch movement simultaneous to the roll movement, but only to a yaw movement which will be reduced in proportion to the reduction in the inclination of the pivot axes 27A, 27B, 45A, 45B, 31A, 31B and axes 39 and 47 with respect to the support surface S of the motor vehicle.

[0060] Typically, if the rotation axes of the linkage system are inclined with respect to the road surface S, the rotation axes can be configured so that the rotation axis of the roll movement intersects the road surface S at a transverse plane which is orthogonal to the surface S and passes through the centre of the rear drive wheels 17A, 17B.

[0061] In addition to the advantages mentioned above of reducing or eliminating the roll motion simultaneous to the yaw motion and the pitch motion, the vehicle configuration described herein, with the roll axis arranged on the support surface (road surface) of the vehicle, also allows further advantages with respect to vehicles of the prior art in which the roll axis is arranged above the support surface (road surface) of the vehicle. In particular, these advantages are obtained when the load of the vehicle is integral with the roll frame. In fact, in this case, as in the exemplary embodiments described above, with the roll axis placed at ground level, the arc followed by the load in the roll motion has a greater radius than it would have with the roll axis raised from the ground. This allows the load plane to be lowered, bringing it closer to the rear wheels, without the risk of the load plane interfering with the rear wheels in the event of a roll of the vehicle. In this way, the load capacity of the vehicle is increased without raising its center of gravity.

Claims

1. A motor vehicle (1), comprising: The front frame (3) tilts about the roll axis; The rear frame (5) has two non-tilting rear drive wheels; Linkage system (23), the linkage system (23) is used to connect the tilted front frame (3) and the rear frame (5); The linkage system (23) includes: -Left pillar (25A), the left pillar (25A) is pivotally connected to the rear frame (5) about the lower left pivot axis (27A); - Right column (25B), which is pivotally connected to the rear frame (5) about the lower right pivot axis (27B); - Upper transverse member (33), which is pivotally connected to the upper part of the left column (25A) about the upper left pivot axis (31A); and pivotally connected to the upper part of the right column (25B) about the upper right pivot axis (31B); - A middle transverse member (41) is pivotally connected to the left column (25A) about a left middle pivot axis (45A) arranged between the lower left pivot axis (27A) and the upper left pivot axis (31A); and is pivotally connected to the right column (25B) about a right middle pivot axis (45B) arranged between the lower right pivot axis (27B) and the upper right pivot axis (31B). The intermediate transverse member (41) is hinged to the front frame (3) about the lower central pivot axis (47), and the upper transverse member (33) is hinged to the front frame (3) about the upper central pivot axis (39). The distance (X) between the lower central pivot axis (47) and the upper central pivot axis (39) is equal to the distance (X) between the left middle pivot axis (45A) and the left upper pivot axis (31A) and is equal to the distance (X) between the right middle pivot axis (45B) and the right upper pivot axis (31B). In the upright, non-tilting position of the vehicle (1) on the support surface (S), the lower central pivot axis (47) is located below the plane containing the left intermediate pivot axis (45A) and the right intermediate pivot axis (45B), and the pivot axes (27A, 27A, 31A, 31B, 45B, 45B) of the linkage system (23) are located on a vertical plane parallel to the vertical mid-plane of the motor vehicle, and the lower central pivot axis (47) and the upper central pivot axis (39) are located on the vertical mid-plane of the motor vehicle.

2. The motor vehicle (1) according to claim 1, wherein, The left column (25A) and the right column (25B) are parallel to each other, and the upper transverse member (33) is parallel to the middle transverse member (41).

3. The motor vehicle (1) according to claim 1, wherein, In the non-tilting upright position of the vehicle on the support surface (S), the distance (Y) of the lower central pivot axis (47) from the support surface (S) is equal to the distance (Y) between the lower left pivot axis (27A) and the left middle pivot axis (45A) and equal to the distance (Y) between the lower right pivot axis (27B) and the right middle pivot axis (45B).

4. The motor vehicle (1) according to claim 2, wherein, In the non-tilting upright position of the vehicle on the support surface (S), the distance (Y) of the lower central pivot axis (47) from the support surface (S) is equal to the distance (Y) between the lower left pivot axis (27A) and the left middle pivot axis (45A) and equal to the distance (Y) between the lower right pivot axis (27B) and the right middle pivot axis (45B).

5. The motor vehicle (1) according to claim 1, wherein, In the non-tilting upright position of the vehicle on the support surface (S), the upper central pivot axis (39) is positioned below the plane containing the right intermediate pivot axis (45B) and the left intermediate pivot axis (45A).

6. The motor vehicle (1) according to any one of claims 2-4, wherein, In the non-tilting upright position of the vehicle on the support surface (S), the upper central pivot axis (39) is positioned below the plane containing the right intermediate pivot axis (45B) and the left intermediate pivot axis (45A).

7. The motor vehicle (1) according to claim 1, wherein, The left column (25A) and the right column (25B) are pivotally connected to the rear frame (5) at the left and right ends of the lower transverse member (29).

8. The motor vehicle (1) according to any one of claims 2-5, wherein, The left column (25A) and the right column (25B) are pivotally connected to the rear frame (5) at the left and right ends of the lower transverse member (29).

9. The motor vehicle (1) according to any one of claims 1-5 and 7, wherein, The left intermediate pivot axis (45A), the right intermediate pivot axis (45B), and the lower central pivot axis (47) are arranged at the vertices of the first isosceles triangle, the base of which extends from the left intermediate pivot axis (45A) to the right intermediate pivot axis (45B); and wherein the upper left pivot axis (31A), the upper right pivot axis (31B), and the upper central pivot axis (39) are arranged at the vertices of the second isosceles triangle, the second isosceles triangle being equal to the first isosceles triangle, the base of which extends from the upper left pivot axis (31A) to the upper right pivot axis (31B).

10. The motor vehicle (1) according to claim 9, wherein, The intersection point (A) between the lower left pivot axis (27A), the lower right pivot axis (27B), and the first straight line passing through and orthogonal to the lower left pivot axis (27A) and the second straight line passing through and orthogonal to the lower right pivot axis (27B) is located at the vertex of the third isosceles triangle, which is equal to the first and second isosceles triangles. The first and second straight lines are parallel to the first side of the first isosceles triangle and the first side of the second isosceles triangle, respectively. The roll axis of the motor vehicle is parallel to the lower central pivot axis (47) and the upper central pivot axis (39) and passes through the intersection point (A).

11. The motor vehicle (1) according to claim 10, wherein, The intersection point (A) is located on the vertical midplane of the motor vehicle (1) and is independent of the roll angle of the motor vehicle.

12. The motor vehicle according to claim 10, wherein, The intersection (A) is located on the support surface of the motor vehicle.

13. The motor vehicle according to any one of claims 1-5 and 7, wherein, The lower left pivot axis (27A), the lower right pivot axis (27B), the upper left pivot axis (31A), the upper right pivot axis (31B), the left middle pivot axis (45A), the right middle pivot axis (45B), the lower central pivot axis (47), and the upper central pivot axis (39) are substantially parallel to each other.

14. The motor vehicle (1) according to claim 13, wherein, The lower left pivot axis (27A), the lower right pivot axis (27B), the upper left pivot axis (31A), the upper right pivot axis (31B), the left middle pivot axis (45A), the right middle pivot axis (45B), the lower central pivot axis (47), and the upper central pivot axis (39) are substantially parallel to the support surface (S) of the motor vehicle.

15. The motor vehicle (1) according to claim 13, wherein, The lower left pivot axis (27A), the lower right pivot axis (27B), the upper left pivot axis (31A), the upper right pivot axis (31B), the left middle pivot axis (45A), the right middle pivot axis (45B), the lower central pivot axis (47), and the upper central pivot axis (39) are inclined relative to the support surface (S) of the motor vehicle, such that the tilt axis intersects the support surface (S) of the motor vehicle at the intersection between the support surface (S) and a transverse plane, the transverse plane being orthogonal to the support surface and including the rotation axis of the rear drive wheels (17A, 17B).

16. The motor vehicle (1) according to claim 14, wherein, The roll axis is located on the support surface (S) of the motor vehicle (1).

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