Saddle-riding type motor vehicle having two inclined front steered wheels and two non-inclined rear drive wheels

Abstract

A tilting saddle motor vehicle (1) comprising a frame (3), two front steered wheels (11A, 11B) and two rear driven wheels (15A, 15B). The front steered wheels and the frame are adapted to perform a tilting movement during driving, while the rear driven wheels are supported on a carrier (19) which is not subject to tilting movement and is connected to the frame by means of a tilting joint which allows the frame to rotate about a roll axis, for example on a curved road, while the carrier (19) does not participate in the tilting movement, i.e. it does not tilt to the right or to the left.

Description

Technical Field

[0001] This invention relates to the field of tilt-saddle type motor vehicles. Specifically, the embodiments described herein relate to four-wheel tilt-saddle type vehicles, i.e., four-wheel tilt-saddle type vehicles capable of tilting during movement, such as when moving along a curved trajectory. Background Technology

[0002] Typically, saddle-riding vehicles have rear drive wheels and front steering wheels, which are connected by a frame that supports the engine. Two-wheeled saddle-riding vehicles are essentially tilting vehicles, or lobbing vehicles, that is, vehicles that tilt when turning by performing a swinging movement about a central axis located on the ground.

[0003] Tilt (i.e., roll) saddle-riding vehicles with more than two wheels are also becoming increasingly common. Some of these vehicles have two front steering wheels and one rear drive wheel. The front steering wheels are connected to the frame via a linkage system that allows the vehicle to tilt. These front steering wheels lie in planes parallel to each other, which are perpendicular to the ground when the vehicle travels on a straight track, and tilt relative to the ground by tilting movement when the vehicle travels on a curved track. In this case, the vehicle frame performs a similar tilting movement.

[0004] Other tilting saddle-riding vehicles include a front steering wheel and two rear drive wheels, the two rear drive wheels being mounted to perform tilting movement. These drive wheels lie on mutually parallel planes that are orthogonal to the ground when the vehicle travels on a straight track, and tilt relative to the ground when the vehicle travels on a curved track. In this case, the vehicle frame performs similar tilting movement.

[0005] There are also tilting saddle-riding vehicles that include a front steering wheel and two non-tilting rear drive wheels (i.e., rear drive wheels that do not tilt laterally during driving). The frame is connected to the rear drive wheels via a joint that allows the frame, on which the saddle is mounted, to perform tilting movements while the plane of the rear wheels remains orthogonal to the ground on which the vehicle is traveling.

[0006] EP 3455123 discloses a tilting motor vehicle with three or four wheels. This prior art motor vehicle includes a rear drive wheel supported by a fork pivotally connected to a frame. The fork is provided with bouncy movement relative to the frame via a rear suspension inserted between the fork and the frame. A motor is rigidly connected to the frame, transmitting motion to the drive wheel via a chain. The frame consists of two parts connected by a tilt joint. The rear portion of the frame is connected to the front portion of the frame via a tilt joint, allowing the front portion of the frame to tilt relative to the rear portion, the rear portion of the frame rigidly supporting the engine and the suspension fork of the rear drive wheel. The front portion of the frame supports a steering column, which transmits steering movement imparted by the handlebars to a pair of front steering wheels. The front steering wheels are connected to the front portion of the frame via a four-bar linkage to allow tilting movement of the motor vehicle. The motor vehicle disclosed in EP3455123 includes only the rear drive wheel (or a pair of rear drive wheels) as unsprung mass, while the engine is part of the suspended mass integral with the frame.

[0007] Additional tilting motor vehicles are disclosed in JPS60183280 and EP1070658.

[0008] Each of these motor vehicles has its own advantages and disadvantages.

[0009] The object of the present invention is to provide a four-wheel tilting saddle-riding motor vehicle that provides safety and riding comfort and overcomes, in part or in whole, one or more limitations of known motor vehicles. Summary of the Invention

[0010] Generally, according to the present invention, a four-wheeled tilting saddle-riding motor vehicle is provided, comprising a frame and a steering column, the steering column being rotatably housed in a steering tube integral with the frame and integral with the handlebars. The motor vehicle also includes a pair of front steering wheels connected to the frame via at least one tilting four-bar linkage. Each of the two front steering wheels is adapted to perform lateral movement, i.e., tilting movement about an axis parallel to the ground on which the motor vehicle is parked and traveling and passing through the contact point of the wheel. The tilting four-bar linkage comprises a plurality of components pivotally connected to each other about mutually parallel pivot axes. Variations of the tilting four-bar linkage allow the frame, the left front steering wheel, and the right front steering wheel to perform tilting movement, taking a tilted position during travel, for example, when the motor vehicle is cornering. The motor vehicle also includes a pair of rear drive wheels supported by a non-tilting rear bracket, on which the propulsion unit of the motor vehicle is arranged, hereinafter also referred to as the powertrain or power unit, or simply a motor. Because the bracket is not tilted, during travel, the rear drive wheels maintain their own plane orthogonal to the ground on which the motor vehicle is traveling. The plane in which the wheel lies is essentially the center plane of the wheel, orthogonal to the wheel's axis of rotation. To allow the vehicle's frame to perform tilting movements, and for the rear drive wheels to maintain their planes orthogonal to the ground, a tilt joint is provided that connects the non-tilting rear bracket to the frame. The tilt joint defines a roll axis about which the frame rotates relative to the rear bracket when the vehicle tilts, i.e., when performing tilting movements, such as when traveling along a curve.

[0011] The motor vehicle may advantageously include a rear suspension and a suspension hinge, the rear suspension being adapted to allow the frame to flex relative to the rear bracket, the suspension hinge defining a suspension axis extending in a lateral direction in the vehicle's direction of travel, and the frame and rear bracket being adapted to perform flexural movement about the suspension axis.

[0012] In the embodiments disclosed herein, the propulsion unit is rigidly constrained to the rear bracket, thus not participating in bouncy movement. In effect, by arranging the rear suspension to allow bouncy movement of the frame relative to the rear bracket, the propulsion unit and the rear drive wheels form the unsprung mass of the vehicle, i.e., the mass that does not perform the bouncy movement permitted by the vehicle's suspension.

[0013] In some embodiments, the tilt axis may be formed by the rotation axis of the hinge formed by the tilt joint.

[0014] In other embodiments, the tilting joint includes a four-bar linkage mechanism that connects the frame to the rear bracket. The four-bar linkage mechanism may include: a lower transverse connecting rod integral with the frame; an upper transverse connecting rod integral with the rear bracket; a left rocker arm; and a right rocker arm connecting the upper and lower transverse connecting rods.

[0015] In some embodiments, the upper lateral connecting rod is longer than the lower lateral connecting rod, causing the left and right rocker arms to deflect relative to the center plane of the vehicle and converge towards each other from the upper to the lower lateral connecting rod. In this case, the roll axis can be represented by a straight line passing through the intersection of the extensions of the two rocker arms.

[0016] In a suitable embodiment, the tilt axis and pivot axis of at least one tilting four-bar linkage are formed between them at an angle between 0° and 30°, preferably between 0° and 15°.

[0017] In some embodiments, the roll axis defined by the tilt joint connecting the frame to the rear bracket may be tilted at an angle relative to the support surface of the motor vehicle, such that the roll axis intersects the support surface at a point located between the left and right rear drive wheels, and is oriented from bottom to top in the direction of travel of the motor vehicle. For example, the intersection may advantageously be located between the contact area between the left rear drive wheel and the support surface and the contact area between the right rear drive wheel and the support surface.

[0018] The suspension hinge can be positioned between the rear bracket and the swashplate. In this configuration, the rear suspension can be hinged at a first end to an arm integral with the rear bracket and pivotally connected to the swashplate about the suspension axis, and the rear suspension can be pivotally connected at a second end to a point rigidly connected to the swashplate, more precisely, at a position on the swashplate such that the roll axis is located between the frame and the second end of the rear suspension. In this way, the bracket is provided with oscillating, spring-like movement about the suspension axis, resulting in compression and relaxation of the rear suspension, while the swashplate does not participate in this spring-like movement.

[0019] In other embodiments, the suspension hinge may be arranged between the swashplate and the frame. In this case, the rear suspension may be hinged to the swashplate at a first end and to the frame at a second end. In this case, the spring joint participates in bouncy movement, i.e., oscillation about the suspension axis, which results in compression and relaxation of the spring suspension.

[0020] The front suspension associated with (multiple) tilting four-bar linkages and the rear suspension associated with the rear bracket typically include elastic and viscous members, which are preferably coaxial with each other.

[0021] Further advantageous features and embodiments of the motor vehicle of the present invention are defined in the appended claims and are disclosed in more detail below with reference to the accompanying drawings. Attached Figure Description

[0022] The invention will be better understood from the following description and accompanying drawings, which illustrate non-limiting examples of motor vehicle embodiments according to the invention. Various non-essential parts of the motor vehicle are omitted in the drawings. In particular, the fairing is omitted, and in some cases, other parts such as the saddle, wheels, handlebars, etc., are also omitted. More specifically, in the drawings:

[0023] Figure 1 A side view of an embodiment of the motor vehicle of the present invention is shown in a zero tilt angle position;

[0024] Figure 2 It shows Figure 1 Axonometric drawing of the front bracket of a motor vehicle;

[0025] Figure 3 and Figure 4 It shows Figure 1 Motor vehicles are viewed from two different angles as a whole.

[0026] Figure 5 The image shows the same motor vehicle in an inclined position, i.e., with an inclination angle other than zero. Figure 1 The side view of the view;

[0027] Figure 6 A rear view of a tilted motorcycle is shown;

[0028] Figure 7 and Figure 8 Axonometric views of the tilted vehicle at two different angles are shown.

[0029] Figure 9 A side view of a motor vehicle in another embodiment is shown;

[0030] Figure 10 It shows Figure 9 Axonometric view of the rear section of the vehicle;

[0031] Figure 11 A side view of a motor vehicle in another embodiment is shown;

[0032] Figure 12 It shows Figure 11 Axonometric views of the central and rear sections of a motor vehicle;

[0033] Figure 13 A side view of a motor vehicle in another embodiment is shown;

[0034] Figure 14 Another embodiment similar to this is shown. Figure 3 The side view of the view;

[0035] Figure 15A side view of a motor vehicle in another embodiment is shown;

[0036] Figure 16 It shows Figure 15 Partial axonometric drawing of a motor vehicle;

[0037] Figure 17 An axonometric view of the front portion of a motor vehicle is shown in another embodiment; and

[0038] Figure 18 and Figure 19 A front view and an axonometric view of the front portion of a motor vehicle in another embodiment are shown. Detailed Implementation

[0039] The first embodiment of the motor vehicle according to the present invention is in Figures 1 to 8 The diagram is shown in the image.

[0040] In this embodiment, the motor vehicle 1 includes a frame 3, a steering tube 5 integral with the frame 3 or a part of the frame 3, and a steering column 7 integral with the handle 9 rotatably housed in the steering tube 5. The steering movement of a pair of front steering wheels 11 is controlled by means of the handle 9, and more specifically, 11A indicates the left front steering wheel and 11B indicates the right front steering wheel.

[0041] The fairing was attached to the frame, but has been removed for clarity of the figures. Reference numeral 13 schematically indicates the saddle for the driver (not shown), which is omitted in some figures.

[0042] The motor vehicle 1 also includes a pair of drive wheels 15. More specifically, 15A indicates the left rear drive wheel, and 15B indicates the right rear drive wheel. The rear drive wheels 15A and 15B are generally coaxial and are driven to rotate by a powertrain 17. The powertrain may be a reciprocating internal combustion engine or an electric motor. In some embodiments, the powertrain 17 may be a hybrid powertrain, including a combination of a heat-absorbing engine and an electric motor.

[0043] The rear drive wheels 15A and 15B and the powertrain 17 are mounted on a rear bracket, generally indicated by 19. The rear bracket 19 is connected to the frame 3 by means of a tilt joint 21, which allows the frame 3 to tilt about a roll axis AR located in the vertical center plane of the vehicle 1 when the vehicle is upright at zero tilt angle. In this way, for example when the vehicle 1 is traveling around a curve, the frame 3 can tilt to the right or left with the tilt movement, and the driver sitting on the saddle 13 participates in this tilt movement.

[0044] In the embodiments described herein, the tilt joint 21 substantially defines a hinge whose axis coincides with the tilt axis AR. In other embodiments described below, the tilt joint may have a more complex form and include, for example, a four-bar linkage such that the tilt axis does not coincide with the axis of the hinge defining the four-bar linkage.

[0045] exist Figures 1 to 4 In the diagram, the motor vehicle 1 is shown in a vertical position when parked, with zero tilt angle, the tilt angle being defined between a plane perpendicular to the ground and the central plane of the motor vehicle frame 3. Essentially, in Figures 1 to 4 In this context, motor vehicle 1 is in an upright position, as it would be when motor vehicle 1 is stationary or traveling in a straight line. Figures 5 to 8 In the diagram, the same vehicle is shown leaning to the right, i.e., having a non-zero tilt angle and veering to the right. For example, this position is taken when the vehicle is traveling around a curve, and the greater the speed and the smaller the radius of curvature of the curve followed by vehicle 1, the greater the tilt.

[0046] exist Figure 6 In this diagram, TT indicates the plane of the ground where the motor vehicle 1 is parked and driven, PP indicates the plane perpendicular to the ground, and MM indicates the center plane of the motor vehicle. Figure 6 In the given position, vehicle 1 is tilted by an angle αR. When vehicle 1 is stationary or moving in a straight line, the tilt angle αR is zero (zero tilt angle).

[0047] exist Figures 1 to 8 In the embodiment illustrated, the roll axis AR has zero skewness relative to the ground TT where the vehicle 1 is parked. However, this condition is not required, as will become apparent from the description of other embodiments.

[0048] As in Figures 4 to 8 As can be seen, the rear bracket 19 does not participate in the tilting movement of the motor vehicle 1. The two rear drive wheels 15A and 15B maintain their center plane (in Figure 6 The rear bracket 19 (indicated by 15M) is perpendicular to the ground TT. In this sense, the rear bracket 19, rear drive wheels 15A, 15B, and powertrain 17 do not participate in the tilting movement of the vehicle. This allows for the use of a particularly simple transmission between the powertrain 17 and the rear drive wheels 15A, 15B. Furthermore, the powertrain 17 is rigidly connected to the rear bracket 19, and the rotation axes of the rear drive wheels 15A, 15B are fixed relative to the rear bracket 19.

[0049] Conversely, the front steering wheels 11A and 11B participate in the tilting movement of frame 3, such as... Figure 6As specifically shown in the diagram, the front steering wheels 11A and 11B tilt at a certain angle following the tilt of the frame 3, while remaining parallel to each other. For this purpose, the front steering wheels are connected to the frame via an insert linkage system that allows for tilting movement.

[0050] exist Figures 1 to 8 In the embodiment illustrated herein, a tilting four-bar linkage is provided for this purpose, generally indicated by 23, and specifically in Figure 2 As shown in the image.

[0051] In the illustrated embodiment, the tilting four-bar linkage 23 is located at approximately the same height as the front steering wheels 11A and 11B. In fact, the tilting four-bar linkage 23 is positioned between the two front steering wheels 11A and 11B, and more specifically, in this embodiment, the total height of the tilting four-bar linkage 23, i.e., its vertical dimension, is significantly smaller than the diameter of the front steering wheels, thus remaining contained within a cylindrical envelope tangent to the two front steering wheels 11A and 11B. As will be described below, in other embodiments, the tilting four-bar linkage 23 may be positioned differently, for example, entirely above the space occupied by the front steering wheels 11A and 11B.

[0052] The tilting four-bar linkage 23 may include an upper transverse member 25, which is pivotally connected to the frame 3 by means of an upper central hinge or pivot 27, which defines an upper central pivot axis 27A (see in particular). Figure 1 In the illustrated embodiment, as in Figure 1 As can be seen, when the motor vehicle 1 is in an upright position with zero tilt angle, the upper central pivot axis 27A is located in a vertical plane, specifically in the center plane MM of the motor vehicle, and is tilted by an angle β1 relative to the supporting surface TT of the motor vehicle 1.

[0053] The tilting four-bar linkage 23 also includes a lower transverse member 29, which is pivotally connected to the frame 3 by means of a lower central hinge or pivot 31, which defines the lower central pivot axis 31A (see in particular). Figure 1 In the illustrated embodiment, as in Figure 1 As can be seen, when the vehicle 1 is in an upright position with zero tilt angle, the lower central pivot axis 31A is located in a vertical plane, specifically in the central plane MM of the vehicle, and is tilted by an angle β1 relative to the supporting surface TT of the vehicle 1. Therefore, axes 27A and 31A are essentially parallel to each other.

[0054] The left ends of the upper lateral member 25 and the lower lateral member 29 are connected together by a left pillar or rocker arm 33A, and the left front steering wheel 11 is constrained to the left pillar or rocker arm 33A by inserting into the left front suspension 35A. The right ends of the upper lateral member 25 and the lower lateral member 29 are connected together by a right pillar or rocker arm 33B, and the right front steering wheel 11B is constrained to the right pillar or rocker arm 33B by inserting into the right front suspension 35B. Generally, the right front suspension and the left front suspension 35A, 35B include elastic and viscous components, i.e., shock absorbers. The pillars or rocker arms 33A, 33B are pivotally connected to the lateral members 25, 29 by means of hinges, which define axes that are parallel to each other and parallel to axes 27A, 27B. When the vehicle 1 is upright, the axes of the hinges are in a plane orthogonal to the ground TT and form an angle β1 with the plane TT.

[0055] Figure 1 The structure of the front portion of the motor vehicle illustrated is merely an example. Those skilled in the art will know that a tilting saddle-riding vehicle with a tilting four-bar linkage at a low position between the two front steering wheels 11A, 11B can have a different shape than the illustrated shape, which can be used alternatively.

[0056] In terms of characteristics, the difference between angle β1 (formed between the pivot axis of the tilting four-bar linkage 23 and the support surface TT of the motor vehicle 1) and the angle formed between the tilt axis AR of the tilting joint 21 and the support surface TT does not exceed 30°, preferably not more than 15°. Figures 1 to 8 In the example illustrated, the roll axis AR is parallel to the support surface TT of the vehicle 1, i.e., parallel to the ground, and therefore the angle β1 is preferably equal to or less than 30°, more preferably equal to or less than 15°, for example between 0° and 5°, or between 0° and 10°.

[0057] The front steering wheels 11A and 11B are constrained to the tilting four-bar linkage 23 so that they can perform rotational movement about the corresponding steering axis. The handle 9 transmits rotational movement about the steering axis via the steering column 7 and steering rod 37 (see...). Figure 2 ).

[0058] The springback of frame 3 relative to the rear drive wheels 15A and 15B is provided by the rear suspension 41, which includes elastic and viscous elements (shock absorbers). The rear suspension 41 is pivotally connected to the tilt joint 21 at a first end 41X and to frame 3 at a second end 41Y, thereby allowing the tilt joint 21 to springback relative to frame 3. Figure 1As indicated by the double arrow f21 in the diagram. To allow this movement, the tilt joint 21 is pivotally connected to the frame 3 by means of a suspension hinge 43, which defines a lateral axis that is parallel to the ground TT in the vehicle's upright position at zero tilt angle and extends in a left-right direction orthogonal to the center plane MM of the vehicle 1.

[0059] Figure 9 and Figure 10 The rear portion of the motor vehicle 1 in another embodiment is shown. (Refer to reference...) Figures 1 to 8 The same or corresponding parts described are indicated by the same reference numerals. Figures 9 to 10 The embodiments differ from Figures 1 to 8 The embodiments, particularly in terms of the arrangement of the rear suspension 41. Figure 9 and Figure 10 In the middle, the rear suspension 41 is located between the rear bracket 19 and the tilt joint 21, and is pivotally connected to arms 51 and 53 at 41X and 41Y. Arm 53 is integral with one of the two parts forming the tilt hinge defined by the tilt joint 2. Arm 51 is hinged to the tilt joint 21 by means of suspension hinge 43. When the vehicle is in an upright position, i.e., at zero tilt angle, suspension hinge 43 defines a lateral axis orthogonal to the center plane MM of the vehicle 1. Rear bounce movement is again indicated by double arrow f21.

[0060] Figure 1 The front part of the motor vehicle can be like Figures 1 to 8 The structure is illustrated in the figure below, or as shown in the figure below.

[0061] In the same case, the roll axis AR is parallel to the support surface TT (ground) of the vehicle 1, but as will be seen from other embodiments described below, this condition is not mandatory.

[0062] Figure 11 and Figure 12 A simplified side view and partial axonometric view of the rear of a motor vehicle 1 are shown in another embodiment. The same numerical designations indicate parts that are identical or corresponding to those described in the reference example embodiment. The front portion of the motor vehicle 1 in this embodiment is equivalent to that described in the reference example embodiment. Figures 1 to 8 The first part of the description, or those described below.

[0063] In the embodiments described so far, the tilt joint 21 substantially defines a hinge with a tilt axis AR, in Figure 11 and Figure 12 In this embodiment, the tilting joint 21 is formed by a four-bar linkage that connects the frame 3 to the rear bracket 19. The four-bar linkage is again designated 21 because it essentially forms the tilting joint, and its function is similar to that described in the reference above. Figures 1 to 10The tilting joint 21 is described. The four-bar linkage includes a lower transverse connecting rod 21D integral with the frame 3 and an upper transverse connecting rod 21C integral with the rear bracket 19. The two connecting rods 21D and 21C are connected to each other via a left rocker arm 21A and a right rocker arm 21B. Typically, the upper transverse connecting rod 21C is longer than the lower transverse connecting rod 21D. In this way, the left rocker arm 21A and the right rocker arm 21B are symmetrical with respect to the center plane MM of the vehicle 1, are tilted with respect to the center plane MM, and converge towards each other from the upper transverse connecting rod toward the lower transverse connecting rod.

[0064] The tilt axis AR is a straight line parallel to the pivot axis of the four-bar linkage 23 (i.e., parallel to the axis of the hinge that connects the connecting rods 21C and 21B to the rocker arms 21A and 21B) and passing through the intersection of the extensions of the rocker arms 21A and 21B.

[0065] The position of the roll axis AR changes with the tilt angle. Figure 11 The roll axis AR is shown when the vehicle 1 is in a vertical position (zero tilt angle).

[0066] Figure 13 Different embodiments are shown that are similar to Figure 1 The side view of the view in the image. The same numbers indicate the same... Figures 1 to 8 The parts are the same as or correspond to the parts in the picture. Figures 1 to 8 Motor vehicle 1 and Figure 13 The main difference between the motor vehicles 1 and the other motor vehicles 1 is that the tilt joint 21 defines a tilt axis AR that is not parallel to the ground, i.e., not parallel to the support surface TT of the motor vehicle 1, but tilted relative to the plane TT by an angle β2. In the same case, the difference between angle β2 and angle β1 (formed by the pivot axis of the tilt four-bar linkage 23 located in the front part of the motor vehicle 1 and the plane TT) is preferably between 0° and 30°, and more preferably between 0° and 15°.

[0067] In an advantageous embodiment, when the vehicle is in an upright position with zero tilt angle, the skewness of the roll axis AR relative to the support surface TT of the vehicle 1 advantageously suchs that the point of incidence, i.e., the intersection, between the roll axis AR and the plane TT is located between the two rear drive wheels 15A, 15B, and more advantageously along the area between the two contact points of the rear drive wheels 15A, 15B and the ground, such as... Figure 13 Point X in the diagram indicates this.

[0068] Figure 14 It shows the relationship with Figure 19 A side view of a motor vehicle similar to motor vehicle 1. The same numbers indicate the same or corresponding parts as those already described. Figure 14and Figure 9 The main difference between them is that, Figure 14 In this context, the tilt joint 21 is oriented such that when the vehicle 1 is in an upright position, i.e., with a zero tilt angle, it defines a roll axis AR that is tilted at an angle β2 different from zero relative to the support surface TT of the vehicle. As in... Figure 13 In the embodiments, also in Figure 14 In the middle, the incident point X of the roll axis AR on the support surface TT of the motor vehicle is preferably located in the area between the contact point or contact area of ​​the two rear drive wheels 15A and 15B.

[0069] Figure 15 and Figure 16 They respectively showed the same as Figure 11 and Figure 12 The side view and partial axonometric view of a motor vehicle 1, similar to a motor vehicle, are shown. Motor vehicle 1 is constructed such that, Figure 11 and Figure 12 The simple four-bar linkage mechanism is replaced by a more complex linkage system, which has the advantage that the tilt axis defined by the linkage system 21 forming the tilt joint is located on the support surface TT of the motor vehicle, and always remains in the center surface MM even when the motor vehicle is tilted, i.e. when it has a non-zero tilt angle.

[0070] In the embodiments described so far, the tilting four-bar linkage 23 is positioned low, such that it is substantially within the volume between the two front steering wheels 11A, 11B. However, this configuration is not the only possible one. Figure 17 The front portion of the vehicle is shown as an example, in which the tilt four-bar linkage, again indicated by 23, is positioned above the two front steering wheels, again indicated by 11A and 11B. The upper lateral member or connecting rod of the tilt four-bar linkage is again indicated by 25, and the lower lateral member or connecting rod by 29. An upper central hinge or pivot, indicated by 27, is used to pivot the upper lateral member 25 to the frame 3. A lower central hinge or pivot, indicated by 31, is used to pivot the lower lateral member 29 to the frame 3. The hinge axes 27 and 31 form an angle β1 with the support surface of the vehicle 1, which may be zero or not. As in the above embodiment, the difference between angle β1 and angle β2 formed by the roll axis AR (defined by the tilt joint 21) preferably falls between 0° and 30°, preferably between 0° and 15°, for example between 0° and 10°.

[0071] Figure 17The tilt joint 21 of the motor vehicle, and generally the central and rear portions not shown and referencing the preceding figures, are constructed by adapting the frame structure 3 to the arrangement of the tilting four-bar linkage 23 in a higher position.

[0072] Figure 17 Steering rod 39 and connector 38 are also shown, with connector 38 connecting steering rod 39 to steering column 7.

[0073] exist Figure 17 In one embodiment, the two front steering wheels 11A and 11B are connected to the tilting four-bar linkage 23 by means of arms 61A and 61B, which can be supported within columns 33A and 33B to rotate about the steering axis. Suspension members 35A and 35B, each including an elastic member and a viscous member, can be disposed between the front steering wheels 11A and 11B and the arms 61A and 61B.

[0074] Figure 17 The structure of the front portion of the motor vehicle illustrated is merely an example. Those skilled in the art will know that a tilting saddle-riding vehicle with a forward tilting four-bar linkage in the upper position can have a different shape than the illustrated shape, which may be used alternatively.

[0075] In the above embodiment, the motor vehicle 1 includes a single tilting four-bar linkage 23. In other embodiments, the motor vehicle 1 may include different systems for connecting the steering and tilting front wheels to the frame 3, such systems including, for example, two four-bar linkages. This type of construction... Figure 18 and Figure 19 The illustration is shown in the example. Figure 18 and Figure 19 Only a portion of frame 3, the tilting four-bar linkage system, and the hubs of the front steering wheels 11A and 11B are shown. The hubs of the front steering wheels 11A and 11B are indicated by 12A and 12B. The suspension for the two front steering wheels 11A and 11B is again indicated by 35A and 35B. The suspension 35A and 35B are pivoted at the top to the crossbar 36, which is pivoted to frame 3 by means of hinge 36X.

[0076] The tilting four-bar linkage 23A connecting the front steering wheel 11A to the frame 3 includes an upper transverse member 25A hinged to the frame 3 by means of a hinge or pivot 28 and a lower transverse member 29A hinged to the frame 3 by means of a hinge or pivot 32. The tilting four-bar linkage 23B connecting the front steering wheel 11B to the frame 3 includes an upper transverse member 25B hinged to the frame 3 by means of a corresponding hinge or pivot 28 to the hinge and a lower transverse member 29A hinged to the frame 3 by means of a hinge or pivot 32. The two four-bar linkages 23A and 23B share a side 34 formed by the frame 3 and extending between hinges 28 and 32.

[0077] The embodiments of the dual tilt four-bar linkage mechanisms 23A and 23B are merely examples. Other solutions of this type exist, which differ in that the suspension arrangement is not dual, but rather single and central.

[0078] Figure 18 and Figure 19 The dual tilting four-bar linkage system can be combined with any embodiment of the rear portion of the aforementioned motor vehicle 1. Similarly, in this case, when the motor vehicle 1 is in an upright position with zero tilt angle, the hinge axes of the two tilting four-bar linkages 23A and 23B form an angle β1 with the vehicle's support surface TT. This angle β1 can be equal to, or different from, the angle β2 formed by the tilt axis AR and this surface, with a difference equal to or less than 30°, preferably equal to or less than 15°, for example, equal to or less than 10°.

Claims

1. A tilting saddle-mounted motor vehicle (1), comprising: Framework (3); Steering column (7), which is integral with the handle (9) and rotatably housed in a steering tube (5) integral with the frame (3); A left front steering wheel (11A) and a right front steering wheel (11B) are connected to the frame (3) by inserting at least one tilting four-bar linkage (23; 23A, 23B); wherein the left front steering wheel (11A) and the right front steering wheel (11B) are adapted to perform tilting movement; and wherein the at least one tilting four-bar linkage (23; 23A, 23B) comprises a plurality of components pivotally connected to each other about pivot axes parallel to each other, and deformation of the at least one tilting four-bar linkage (23; 23A, 23B) allows the frame (3), the left front steering wheel (11A) and the right front steering wheel (11B) to take a tilted position during driving; The left rear drive wheel (15A) and the right rear drive wheel (15B) are supported by a non-tilted rear bracket (19), and the propulsion unit (17) of the motor vehicle (1) is arranged on the non-tilted rear bracket (19). An inclined joint (21) connects the non-tilted rear bracket (19) to the frame (3); wherein the inclined joint (21) defines a roll axis (AR) about which the frame (3) rotates relative to the non-tilted rear bracket (19). The rear suspension (41) and suspension hinge (43) are adapted to allow the frame (3) to spring-loaded relative to the non-tilted rear bracket (19), the suspension hinge (43) defining a suspension axis extending in a lateral direction relative to the direction of travel of the motor vehicle, the frame (3) and the non-tilted rear bracket (19) being adapted to perform spring-loaded movement about the suspension axis; The propulsion unit is rigidly connected to the non-tilting rear bracket (19).

2. The motor vehicle (1) according to claim 1, wherein, The tilt axis (AR) is formed by the rotation axis of the hinge formed by the tilt joint (21).

3. The motor vehicle (1) according to claim 1, wherein, The tilting joint (21) includes a four-bar linkage mechanism that connects the frame (3) to the non-tilted rear bracket (19); wherein the four-bar linkage mechanism includes: a lower transverse connecting rod (21D) integral with the frame (3); an upper transverse connecting rod (21C) integral with the non-tilted rear bracket (19); a left rocker arm (21A) and a right rocker arm (21B), the left rocker arm (21A) and the right rocker arm (21B) connecting the upper transverse connecting rod (21C) to the lower transverse connecting rod (21D).

4. The motor vehicle (1) according to claim 3, wherein, The upper transverse connecting rod (21C) is longer than the lower transverse connecting rod (21D); and the left rocker arm (21A) and the right rocker arm (21B) are deflected relative to the center plane (MM) of the motor vehicle (1), and converge toward each other from the upper transverse connecting rod (21C) to the lower transverse connecting rod (21D).

5. The motor vehicle (1) according to claim 1, wherein, When the motor vehicle (1) is in an upright position with zero tilt angle, the roll axis (AR) and the pivot axis of the at least one tilting four-bar linkage (23) form an angle between them, the angle being between 0° and 30° or between 0° and 15°.

6. The motor vehicle (1) according to any one of claims 2-5, wherein, When the motor vehicle (1) is in an upright position with zero tilt angle, the roll axis (AR) forms an angle with the pivot axis of the at least one tilting four-bar linkage (23), the angle being between 0° and 30° or between 0° and 15°.

7. The motor vehicle (1) according to any one of claims 1-5, wherein, When the motor vehicle is positioned on the support surface (TT) and the left front steering wheel (11A), the right front steering wheel (11B), the left rear drive wheel (15A), and the right rear drive wheel (15B) are in a vertical position with zero tilt angle, the roll axis (AR) is tilted relative to the support surface (TT) by an angle (β2) such that the roll axis (AR) intersects the support surface (TT) at approximately the intersection between the left rear drive wheel (15A) and the right rear drive wheel (15B), and is oriented from bottom to top in the driving direction of the motor vehicle (1).

8. The motor vehicle (1) according to claim 7, wherein, The intersection point is between the contact area of ​​the left rear drive wheel (15A) and the support surface (TT) and the contact area of ​​the right rear drive wheel (15B) and the support surface (TT).

9. The motor vehicle (1) according to any one of claims 1-5, wherein, When the motor vehicle (1) is placed on the support surface (TT) and the left front steering wheel (11A), the right front steering wheel (11B), the left rear drive wheel (15A) and the right rear drive wheel (15B) are in an upright position with zero tilt angle, the roll axis (AR) is approximately parallel to the support surface (TT).

10. The motor vehicle (1) according to any one of claims 1-5, wherein, The at least one tilting four-bar linkage mechanism (23) includes: The upper transverse member (25) is pivotally connected to the frame (3) via an upper central pivot (27) about an upper central pivot axis (27A); The lower transverse member (29) is pivotally connected to the frame (3) via a lower central pivot (31) about the lower central pivot axis (31A); The left column (33A) is pivotally connected to the left end of the upper transverse member (25) and the left end of the lower transverse member (29) about a pivot axis that is parallel to each other and parallel to the upper central pivot axis (27A) and the lower central pivot axis (31A); The right column (33B) is pivotally connected to the right end of the upper transverse member (25) and the right end of the lower transverse member (29) about a pivot axis that is parallel to each other and parallel to the upper central pivot axis (27A) and the lower central pivot axis (31A).

11. The motor vehicle (1) according to claim 10, wherein the left front steering wheel (11A) is connected to the at least one tilting four-bar linkage (23) by means of the left front suspension (35A), and the right front steering wheel (11B) is connected to the at least one tilting four-bar linkage (23) by means of the right front suspension (35B).

12. The motor vehicle (1) according to any one of claims 1-5, wherein, The at least one tilting four-bar linkage mechanism (23; 23A, 23B) is arranged between the left front steering wheel (11A) and the right front steering wheel (11B).

13. The motor vehicle (1) according to any one of claims 1-5, wherein, The at least one tilting four-bar linkage (23) is arranged at a greater height relative to the left front steering wheel (11A) and the right front steering wheel (11B).

14. The motor vehicle (1) according to any one of claims 1-5, wherein, The at least one tilting four-bar linkage includes a left tilting four-bar linkage (23A) constrained to the left front steering wheel (11A) and a right tilting four-bar linkage (23B) constrained to the right front steering wheel (11B).

15. The motor vehicle (1) according to any one of claims 1-5, wherein, The suspension hinge (43) is arranged between the non-tilted rear bracket (19) and the tilted joint (21).

16. The motor vehicle according to claim 15, wherein, The rear suspension (41) is arranged between the non-tilting rear bracket (19) and the tilting joint (21).

17. The motor vehicle (1) according to any one of claims 1-5, wherein, The suspension hinge (43) is arranged between the inclined joint (21) and the frame (3).

18. The motor vehicle (1) according to claim 17, wherein, The rear suspension (41) is hinged to the tilt joint (21) via a first end (41x) and to the frame (3) via a second end (41Y).

19. The motor vehicle (1) according to any one of claims 1-5, wherein, The pivot axis of the at least one tilting four-bar linkage (23; 23A, 23B) is parallel to the support surface (TT) of the motor vehicle (1).

20. The motor vehicle (1) according to any one of claims 1-5, wherein, The pivot axis of the at least one tilting four-bar linkage (23; 23A, 23B) is tilted relative to the support surface (TT) of the motor vehicle (1).

21. The motor vehicle (1) according to claim 20, wherein, The pivot axis of the at least one tilting four-bar linkage (23; 23A, 23B) is tilted from bottom to top relative to the support surface (TT) of the motor vehicle in the direction of travel of the motor vehicle, such that the intersection of the axis and the support surface is located behind the left front steering wheel (11A) and the right front steering wheel (11B) relative to the direction of travel of the motor vehicle (1).

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