VEHICLE SUSPENSION MECHANISM

Abstract: A vehicle suspension mechanism (1) including a strut assembly (2) connected with a vehicle body (13) at an upper end portion and with a wheel (7) at a lower end portion, a damper axis (m) along which shaft means (3) of the strut assembly is displaced for a damping effect being extended oblique to a kingpin axis (l) about which the wheel is steered so that the shaft means damper shaft is inclined when the wheel is steered to produce a pivotal movement of the kingpin axis around the damper axis. The improvement comprises conversion member (12) provided at the upper end portion of the strut assembly for converting the inclination of the shaft means produced during the steering action of the wheel to a displacement in a transverse direction of the vehicle at the upper end of the strut assembly so that a negative camber angle change is produced in the wheel located outer side of the steering action.

Description: The present invention relates to a vehicle suspension mechanism according the first part of the main claim. There has been proposed a vehicle suspension mechanism constituted so as to produce a certain change in the camber angle or the vehicle wheel during a cornering operation of the vehicle. EP-A-0 174 007 discloses a vehicle suspension mechanism according to the preamble of claim 1 in which an upper end of a piston rod of a strut assembly is connected with a vehicle body through an assist link and a lower end of the strut assembly is connected with a vehicle wheel through a ball joint, a knuckle and the like. With this structure, in the case where an outer side wheel of the vehicle displaces upwardly relative to the vehicle body when the vehicle is running on a curved path, or the vehicle is in a cornering operation, the strut assembly is urged upwardly so that the upper end of the piston rod of the strut assembly is displaced upwardly and inwardly by means of the assist link. In other words, the upper end of the strut assembly is displaced in a direction oblique to the longitudinal axis of the piston rod so that the strut assembly pivots slightly to the inside about the lower end. This causes pivotal inclination of the vertical axis of the wheel slightly inwardly to produce a negative change in the camber angle of the wheel. This negative camber angle change during the cornering operation of the vehicle is effected to provide the vehicle with a running stability. It should be however noted that in the strut suspension disclosed in EP-A-0 174 007 the piston rod of the strut assembly produces a upward displacement in the direction of the longitudinal axis of the piston rod even where one of the wheels climbs a projection on a road during running a straight path as well. This causes the assist link to displace the upper end of the strut assembly in a direction oblique to the longitudinal axis of the piston rod resulting in a negative camber angle change. This means that the strut suspension structure disclosed in the above document may produce a negative change in the camber angle of the wheel during a straight driving condition of the vehicle so that the driving stability of the vehicle is deteriorated when the vehicle runs in a straight path. It is therefore an object of the invention to provide a vehicle suspension mechanism which can produce a desirable negative change in the camber angle of wheel when the vehicle runs in a curved path and suppress the camber angle change when the vehicle runs in a straight path. It is another object or the invention to provide a vehicle suspension mechanism which can provide a driving stability during a straight path driving condition of the vehicle as well as a curved path driving condition. It is further object of the invention to provide a strut suspension mechanism wherein an upper end of a strut assembly is swung slightly inwardly about a lower end thereof only when the vehicle runs a curved path. According to the invention these problems are solved going out from the known vehicle suspension mechanism by the features of the characterizing part of the main claim. The conversion means can be constituted by resilient means provided between the vehicle body and the shaft means of the strut assembly wherein the resilient means are disposed around the shaft means with different levels and support the upper end of the shaft means of the strut assembly independently. For example, one set of resilient means may be disposed opposite sides of the shaft in a longitudinal direction of the vehicle with substantially same levels with regard to the damper axis of the strut assembly. The other set of the resilient means may be disposed opposite sides of the shaft in a transverse direction of the vehicle with substantially same levels which are different from the levels of the one set of the resilient means. Alternatively, the conversion means can be constituted by a pair of link means connected with the vehicle body at one end and with the upper end of the shaft means of the strut assembly at the other end. The connecting points of each of the link means are located opposite to those of the other one. The connecting point of the link means to the vehicle body panel is spaced from that to the shaft means with regard to the damper axis. In other words, the link means are extended to cross each other in a direction oblique to the damper axis. According to features of the present invention, when the vehicle is running in a curved path or the wheel is being steered for a cornering, a steering force causes steering wheels of the vehicle to produce a pivotal movement around the kingpin axis. It should be noted that the damper axis of the strut assembly by which the wheels are resiliently carried is different from the kingpin axis so that the steering action for the wheels causes the shaft means of the strut assembly to rotate around the damper axis and to exert a moment around the upper end portion of the strut assembly. With this operation, the shaft means is rotated about the damper axis relative to the strut assembly so as to absorb or eliminate the rotating force around the shaft means. However, the moment acted on the strut assembly causes a front portion of the shaft means to be dragged downwardly while a rear portion thereof urged upwardly with regard to a traverse section of the shaft means perpendicular to the damper axis in an outer side wheel of steering. This means that there produces a different movement between the front portion and the rear portion of the traverse section of the shaft means in the outer side wheel under the vehicle cornering operation. The present invention is constituted so as to take advantage of this phenomenon. In a preferred embodiment of the present invention, one set of resilient means are provided between the vehicle body and the shaft means so as to carry the upper end portion of the shaft means in an arrangement that the resilient means are located on opposite sides of the shaft means to each other in the longitudinal direction of the vehicle at substantially same positions in level. Similarly the other set of resilient means are arranged opposite sides of the shaft means to each other in the transverse direction of the vehicle at substantially same positions in level. It should be however noted that the one set of the resilient means are located at level positions higher than a moment acting point about which the moment acts on the shaft means during the cornering operation and that the other set of the resilient means are located at level positions lower than the moment acting point. With this structure, upper front resilient means of the one set of the resilient means and lower outer resilient means of the other set of the resilient means are subjected to a shearing force and a compression force in a steering direction to which the wheel is steered. On the other hand, upper rear resilient means of the one set of the resilient means and lower inner resilient means of the other resilient means are subjected to a shearing force and a tension force in the steering direction. As a result, the upper end position of the shaft means is displaced inwardly relative to the vehicle body with regard to the traverse direction of the vehicle. This movement of the upper end portion of the shaft means causes a slightly inwardly swingable movement of the strut assembly around the lower end of thereof so that a negative change in the camber angle of the outer wheel is produced during the cornering operation. This negative camber angle change in the outer wheel is effected to improve the driving stability during the cornering operation. On the other hand, in the case where the vehicle climbs on an obstacle such as a stone projected from the road surface when the vehicle is running in a straight path, the wheel is urged upwardly relative to the vehicle body so that the strut assembly is compressed along the damper axis. This compression force is transmitted to the shaft means to urge upwardly in the direction of the damper axis. Accordingly, in this operation, no moment acts on the shaft means of the strut assembly and only an axial force acts on the shaft means upwardly so that there is no difference between the front portion of the shaft means and the rear portion thereof in the movement with regard to the traverse section of the shaft means. As a result, although all the resilient means produce upward deformations uniformly because of the axial force, there produces no relative movement of the shaft means to the vehicle body unlike the cornering operation. This means that no camber angle change is produced during the straight path operation of the vehicle. Meanwhile, the vehicle is bumped in the outer wheel of a steering during the cornering operation so that the shaft means is subjected to the axial force as well as the moment. It should be however noted that the axial force does not affect the camber angle of the wheel. The resilient means may have any arrangement within the scope of the claims in which the upper end of the shaft means is displaced inwardly relative to the vehicle body during the cornering operation of the vehicle. In another aspect of the invention, a pair of link means are pivotally connected with the vehicle body at one end and with the upper end of the shaft means at the other end. In this case the connecting points of the link means to the shaft means are located opposite sides of the shaft means in the longitudinal direction of the vehicle. The connecting points of the link means to the shaft means are positioned higher than those to the vehicle body so that the link means are extended to cross each other in the direction oblique to the damper axis. The moment acting point located on the damper axis between the connecting points to the vehicle body and the connecting points to the shaft means. As described above, the front portion of the shaft means is displaced downwardly and the rear portion is displaced upwardly during the cornering operation. As a result, front link means of which connecting point to the shaft means is located at the front side of the shaft means is displaced in a manner of reducing the inclination. On the other hand, rear side link means of which connecting point to the shaft means is located at the rear side of the shaft means is displaced in a manner of increasing the inclination so that the upper end portion of the shaft means is displaced inwardly relative to the vehicle body. This causes a negative camber change in the outer wheel of steering during cornering operation as well. On the other hand, in the case where one of the wheels climbs up a road obstacle such as a stone projecting from the road surface when the vehicle is running in a straight path, the shaft means is subjected to an upward force along the damper axis. It should be however noted that the upward force causes the shaft means to rotate about the damper axis but does not produce a moment against the shaft means. Therefore, any camber angle change is not produced in the wheel during the straight path operation. The arrangement of the link means can be changed so that the upper end of the shaft means is displaced inwardly relative to the vehicle body during the cornering operation of the vehicle. The above and other objects and features of the present invention will be apparent from the following description by taking reference with accompanying drawings employed for a preferred embodiment of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic view of a vehicle suspension mechanism in accordance with the present invention; Figure 2 is a plan view showing an upper end portion of the suspension mechanism where the suspension is mounted on the vehicle body; Figure 3 is a sectional view showing the upper end portion of the suspension mechanism taken along a line A-A in Figure 2; Figure 4 is a a sectional view showing the upper end portion of the suspension mechanism taken along a line B-B in Figure 2; Figure 5 is a view of the upper end portion of the suspension mechanism seen from the lower side thereof; Figure 6 is a simulation view of the upper end portion of the suspension mechanism showing a deformation of resilient structures disposed around a strut; Figure 7 is a view illustrating a deformation of a resilient structure employed for the suspension mechanism of the present invention; Figure 8 is a diagram showing directions of counterforces acting on the strut from the resilient structure of Figure 7; Figure 9 is a plan view of an upper end portion similar to Figure 2 but showing a suspension mechanism in accordance with another embodiment; Figure 10 is a sectional view taken along a line C-C of Figure 9; Figure 11 is a view showing a displacement of link members in the embodiment of the present invention shown in Figure 9; Figure 12 is a plan view of an upper end portion of a suspension mechanism in accordance with still another embodiment of the present invention; Figure 13 is a sectional view of the upper end portion of the suspension mechanism taken along a line D-D of Figure 9; Figure 14 is a view illustrating a development of an outer surface of a structure taken along a circular line k in Figure 12. DESCRIPTION OF PREFERRED EMBODIMENTS Referring to the drawings, specifically to Figure 1, there is shown a schematic view of a strut suspension mechanism of an automotive vehicle in accordance with the present invention. The suspension mechanism 1 comprises a strut assembly 2 having a coil spring 2a and a shock absorber 3. The shock absorber 3 is provided with a cylinder 3a and a piston rod 3b connected with a piston (not shown ) which is slidably inserted in the cylinder 3a. On a lower end of the cylinder 3a is mounted a bracket 4 which is connected with an upper arm 6a of a knuckle 6 of through bolts 5. The knuckle 6 carries a wheel 7 through a wheel hub (not shown). A lower arm 6b of the knuckle 6 is connected with an outer end of a control link 9 through a lower ball joint 8. The other end of the control link 9 is connected with a vehicle body member 11 through a resilient member 10. The upper end of the piston rod 3b is connected with a body member 13 of the vehicle through a resilient assembly 12. Hereinafter, there is described a mounting structure of an upper end portion of the suspension mechanism 1 to the body member 13 taking reference with Figure 2 through 5. The body member 13 is provided with a tubular portion 13a . The upper portion of the piston rod 3b is located at the center of the tubular portion 13a. The piston rod 3b formed with a threaded portion 31b at the top end portion. A bracket 14 is fixed to a shoulder portion of the piston rod 3b formed on an upper end portion thereof through the threaded portion 31b by means of a nut 3c. The bracket 14 is formed with a tubular portion 14a extending upwardly, and a skirt portion 14b extending downwardly and a web 14c extending inwardly in the vicinity of a meeting point of the tubular portion 14a and the skirt portion 14b. The resilient assembly 12 is interposed between the outer surface of the tubular portion 14a and skirt portion 14b of the bracket 14, and the body member 13. The resilient assembly 12 comprises tubular shaped resilient elements 12a, 12b, and 12c, and conical shaped metallic elements 12d and 12e which are expanded downwardly. The resilient element 12a, 12b and 12c and the metallic elements 12d and 12e are coaxially assembled in an overlapped relationship to constitute the resilient assembly 12. The outermost resilient element 12c has a uniform section circumferentially. It should be however noted that the intermediate and innermost resilient elements 12b and 12a are not circumferentially uniform in section. Specifically, as clearly shown in Figure 4, the intermediate and innermost resilient 12b and 12a are provided respectively with a pair of upper extensions 12ba, 12aa extending upwardly and located opposite sides of the bracket 14 in the substantially longitudinal direction of the vehicle and a pair of lower extensions 12bb, 12ab extending downwardly and located opposite sides of the bracket 14 in the substantially transverse direction of the vehicle. A spring seat 16 is provided in the vicinity of the lower end of the skirt portion 4b of the bracket 4 for supporting the coil spring 2a of the strut assembly 2. The spring seat 16 is carried by the web 4c of the bracket 4 through bearings 17 and 18 to support the coil spring 2a. In operation, when the vehicle is in a cornering operation or the wheel 7 is steered, the wheel 7 pivots about the kingpin axis 1 oriented a certain angle away from the damper axis m or axis of the piston rod 3b of the strut assembly 2. As a result, a moment acts on the piston rod 3b of the strut assembly 2 at the upper end portion connected to the body member 13 through the resilient assembly 12 as well as a rotative force about the damper axis 1. Although the rotative force is absorbed in the assembly to be eliminated, the moment remains to displace the piston rod 3b. The moment causes the piston rod 3b to be displaced downwardly at a front portion thereof and upwardly at a rear portion thereof with regard to the transverse section of the piston rod 3b. As described hereinafter, the upper extensions 12aa, 12ba and the lower extensions 12ab, 12bb of the resilient elements 12a, 12b substantially affect a camber angle change of the wheel 7 of outer side during steering. Figure 6 shows a view in which a deformation of the resilient assembly 12 during a cornering operation of the vehicle is simulated. As far as Figure 6 is concerned, front upper extensions 12aa, 12ba are referred as a front upper resilient structure 12A. Rear upper extensions 12aa, 12ba are referred as a rear upper resilient structure 12B. Further, inner and outer lower extensions 12ab, 12bb are referred as an inner lower resilient structure 12C and an outer lower resilient structure 12D respectively. As shown in Figure 6, The structures 12A, 12B, 12C and 12D are disposed in a circular space formed by the inner surface of the tubular portion 13a of the body member 13 and the outer surface of the tubular portion 14a of the bracket 14 fixed to the piston rod 3b and located spaced from one another in the circumferential direction of the space. The upper resilient structure 12A and 12B are disposed at opposite sides of the tubular portion 14a of the bracket 14 in the substantially longitudinal direction of the vehicle. The lower resilient structures 12C and 12D are disposed at opposite sides of the tubular portion 14a in the substantially transverse direction. The upper and lower structures 12A, 12B and 12C, 12D are spaced from each other in the up and down direction or axial direction of the piston rod 3b. In this structure, the moment produced by a steering operation of the wheel 7 acts on the piston rod 3b at a point C which is located on the damper axis m and the middle position between the upper and lower resilient structures 12A, 12B and 12C, 12D in the up and down direction. This moment causes the piston rod 3b to incline about a line perpendicular to a line n shown in Figure 6 passing through the point C. As a result, the piston rod 3b is forced to be displaced forwardly at the upper portion higher than the point C and rearwardly at the lower portion lower than the point C along the line n. Therefore, the front upper resilient structure 12A is subjected to a force as shown by an arrow D in Figure 6. Similarly, the other resilient structures 12B, 12C and 12D are subjected to forces as shown by arrows E, F and G in Figure 6 respectively. Since the side of the piston rod higher than point C 3b is displaced in the opposite direction to the side lower than the point C as aforementioned, the front upper resilient structure 12A and outer lower resilient structure 12D are subjected to compression and shearing forces respectively and the rear upper and inner lower resilient structures 12B and 12C are subjected to tension and shearing forces. With regard to the front upper resilient structure 12A, there is described a deformation mechanism thereof taking reference with Figure 7. In Figure 7, x axis denotes a direction of the compression force and y axis denotes a direction of the shearing force. A sign l shows the amount of displacement of the piston rod 3b in the direction of inclination or the direction along the line n in Figure 6. An angle ϑ show an angle of the x axis to the direction of the inclination of the piston rod 3b. K x , and K y denote the longitudinal and transverse moduli of elasticity respectively. Accordingly, a deformation of the structure 12A can be expressed by l*cos ϑ for the direction of the x axis and by l*sin ϑ for the direction of the y axis as shown in Figure 7 because of the compression force and shearing force transmitted from the piston rod 3b. On the other hand, a counterforce f x =l*cos ϑ is transmitted from the resilient structure 12A to the piston rod 3b in the direction of the x axis. Concurrently, a counterforce f y =l*sin ϑ is transmitted to the piston rod 3b in the direction of the y axis. The sum of respective component forces of the counterforces in the direction of the inclination can be expressed by f x *cos ϑ + f y *sin ϑ. On the other hand, component forces of the counterforces f x and f y in a direction perpendicular to the direction of the inclination are K x *l*sin ϑ*cos ϑ and K y *l*cos ϑ*sin ϑ. these component forces act in the opposite direction each other so that the sum of the component forces in the direction perpendicular to the direction of the inclination can be expressed by F = l*sin ϑ*cos ϑ*(K x - K y ). It should be noted that where the resilient structure 12A is constituted by a rubber, the relationship between K x and K y is K x > K y so that the sum of the component forces K x and K y acts inwardly on the piston rod 3b in the direction perpendicular to the direction of the inclination of the piston rod 3b. In conclusion, with regard to the direction of the inclination of the piston rod 3b, the counterforce of the resilient structure 12A shown by f x *cos ϑ + f y *sin ϑ acts on the piston rod 3b substantially rearwardly. With regard to the direction perpendicular to the direction of the inclination, the counterforce of the resilient structure 12A shown by l*sin ϑ*cos ϑ*(K x - K y ) acts on the piston rod 3b substantially inwardly. As for the rear upper resilient structure 12B, a counterforce acts on the piston rod 3b from the structure 12B as well as the structure 12A in the direction of the inclination. Although the counterforce of the structure 12B has a same magnitude as that of the structure 12A in the direction of the inclination, the sense of the force is opposite to each other so that the counterforces of the structures 12A and 12B negate with each other to be eliminated. However, the counter force of the structure 12B has a same sense and magnitude as that of the structure 12A in the direction perpendicular to the direction of the inclination so that the piston rod 3b is caused to be displaced inwardly by the sum of the counterforces of the structures 12A and 12B in this direction. Similarly, the inner and outer lower resilient structures produce a counterforce acting on the piston rod 3b inwardly. As a whole, the piston rod 3b is caused to be displaced inwardly with regard to the transverse direction of the vehicle as shown in Figure 6 by an arrow H along the line perpendicular to the line n due to the counter force of the resilient structures 12A, 12B, 12C and 12D. This means that the upper end portion of the piston rod 3b is displaced inwardly at the point C relative to the body member 13 in the direction of the arrow H from the center position of the tubular portion 13a of the body member 13 during the steering operation of the wheel 7. This inward displacement of the upper end portion of the piston rod 3b in the suspension mechanism 1 of the out side wheel 7 of the curve causes a negative camber angle change in the wheel 7 so that the out side wheel 7 can engage with the road surface with a sufficient frictional force to thereby improve a driving stability during the cornering operation of the vehicle. When the vehicle is in a straight path driving and the wheel 7 is caused to be displaced upwardly relative to the vehicle body, for example when the wheel 7 climbs on a stone projecting from the road surface, the piston rod 3b is displaced as described below. In this case, the wheel 7 is forced to be displaced upwardly along the damper axis m which coincides with the longitudinal axis of the piston rod 3b of the strut assembly 2. As a result, the resilient structures 12A, 12B, 12C and 12D are uniformly forced to be displaced upwardly so that there occurs no relative displacement between the upper end portion the piston rod 3b and the tubular portion 13a of the body member 13 in a plane perpendicular to the damper axis m. In other words, the upper end of the piston rod 3b is maintaining at the center of the tubular portion 13a while it is displaced upwardly. Therefore, this displacement of the upper end portion of the piston rod 3b does not produce a substantial camber angle change in the wheel 7. In the illustrated embodiment, the resilient elements 12a and 12b are formed with intermediate resilient portions other than the upper and lower extensions respectively. However the intermediate portions are provided symmetrically with regard to the moment acting point C so that the intermediate portions do not affect the camber angle change but function as only usual insulations. Further, although the illustrated resilient structures are associated with one another to cause the piston rod 3b to be displaced inwardly, it is not necessary to provide a plurality of resilient structure for obtaining such desirable inward displacement of the piston rod but only one or two resilient structures can be constituted so as to produce a counterforce to displace the piston rod 3b inwardly. Where only the resilient structure 12A produces a counterforce which can displace the piston rod 3b inwardly, the other resilient structures may affect the camber angle change in the wheel 7. In addition, The number, shape and arrangement of the resilient element are changeable. The circumferential position of the resilient structures and distance therebetween in the up and down direction and distance to the moment acting point C therefrom can be controlled so as to change the steering angle in which the maximum camber angle change occurs. If the resilient structures 12A, 12B and 12C, 12D are reversely mounted with regard to the moment acting point C, a positive camber angle change can be obtained during the cornering operation. The thickness of the resilient structures 12A, 12B, 12C and 12D can be changed so as to control the magnitude of the camber angle change in the wheel 7 produced during the cornering operation of the vehicle. Now referring to Figure 9, 10 and 11, there is shown another embodiment of the present invention. In this embodiment, the same components as those in the former embodiment are referred to the same numerals as the former embodiment. As shown in Figure 9 and 10, in this embodiment, a cup shaped bracket 30 of a substantially rectangle in section and a conical bracket 33 expanded downwardly are fixed to the shoulder portion of the piston rod 3b through the threaded portion formed at the upper portion of the piston rod 3b by means of the nut 15. The bracket 33 is engaged with the resilient member 34 at an upper surface thereof so that the bracket 33 is associated with an inner surface of the tubular portion 13a of the body member 13 to carry the resilient member 34. A pair of ball joints 21, 22 are mounted on the outer surface of the bracket 30 through nuts 23, 24 respectively. One of the ball joint 21 is located inward of the bracket 30 in the transverse direction of the vehicle. The other of the ball joint 22 is located outward of the bracket 30. Link members 31, 32 are connected with the ball joints 21, 22 at one ends thereof. The other end of the link members 31, 32 are respectively connected a pair of ball joints 27, 28 which are fixed to the inner surface of the tubular portion 13a of the body member 13 at the opposite sides through nuts 25, 26 respectively. As a result, the link member 31, 32 are extended in parallel with each other substantially along the transverse direction of the vehicle. In this arrangement, the connecting point of the link member 31 to the body member 13, that is, the ball joint 27 substantially faces to the connecting point of the link member 32 to the bracket 30, that is the ball joint 22. The ball joint 21 on the bracket 30 for the link member 31 substantially faces to the ball joint 28 on the body member 13 for the link member 32. In other words, the link member 31, 32 are placed symmetrically to each other with regard to the center of piston rod 3b in Figure 9. As shown in Figure 10, the ball joints 21, 22 on the bracket 30 are located higher than the ball joints 27, 28 on the body member 13 with regard to the up and down direction of the piston rod 3b. Therefore, the link members 31, 32 are inclined upwardly toward the connections to the piston rod side. In this arrangement, when the vehicle is in a cornering operation, the moment produced by the pivotal movement of the wheel 7 about the kingpin axis 1 causes the upper end portion of the piston rod 3b to be displaced downwardly at the front portion and upwardly at the rear portion with regard to the transverse section of the piston. This means that the ball joint 21 of the link member 31 is forced to be displaced downwardly and the ball joint of the link member 22 is forced to be displaced upwardly. As a result, the inner link member 31 pivots about the ball joint 27 on the body member 13 in a direction of reducing the inclination thereof as shown by a phantom line A′ of Figure 11. The outer link member 32 pivots about the ball joint 28 on the body member 13 in a direction of increasing the inclination thereof as shown by a phantom line B′ of Figure 11. This causes the upper end of the piston rod 3b to be displaced inwardly as shown by a phantom line C′ of Figure 11. It will be therefore understood that the upper portion of the piston rod 3b is displaced inwardly along substantially an arrow B in Figure 9 from the center position of the tubular portion 13a of the body member 13 relative thereto. This inward displacement of the upper portion of the piston rod 3b causes the outerside wheel 7 to produce a negative camber angle change during the cornering operation. When the vehicle is in a straight path driving and the wheel 7 is forced to be displaced upwardly, the piston rod 3b is also displaced upwardly along the damper axis m so that the ball joint 21, 22 are displaced upwardly as shown by lines A″, B″ in Figure 11. Although this causes a slight upward and rotative displacement of the upper end of the piston rod 3b as shown in Figure 11 by a line C″, there is produced no transverse displacement of the piston rod 3b relative to the body member 13. This means that there occurs no camber angle change in the wheel 7 during the straight path driving of the vehicle. There is shown a still another embodiment of the present invention in Figure 12, 13, 14. In this embodiment, the same members as the former embodiment are referred as the same numerals as those of the former embodiment and a detailed explanation is omitted. As shown in Figure 13, the suspension mechanism in this embodiment is provided a bracket 48 fixed to the upper portion of the piston rod 3b by means of the nut 15. There are interposed a resilient member 60 usually constituted by a rubber busing and intermediate support member 62 and a resilient member usually constituted by a rubber bushing between the bracket 48 and body member 13. The resilient member 60, the support member 62 and the resilient member 64 are arranged coaxially with an overlapped relationship in this order. Therefore, the upper end portion of the piston rod 3b is resiliently supported by the body member 13 through the bracket 48, resilient member 60, support member 62 and resilient member 64. The resilient member 60 has not a uniform thickness circumferentially. As shown in Figure 12 and 14, the resilient member 60 is formed with a pair of thin portions 60a, 60b at the opposite sides of the piston rod 3b in a direction along the line n in Figure 12 and a pair of thick portions 60c and 60d at the opposite sides of the piston rod 3b in a direction perpendicular to the line n. This means that the the resilient member has an ununiform resilient characteristic with regard to the circumferential direction. The bracket 48 is formed with a pair of projections 72, 74 located corresponding to the thin portions 60a and 60b of the resilient member 60. The projections 72 and 74 are formed by gentle slopes 72a, 74a and abrupt slopes 72b and 74b respectively. The gentle slope 72a is located at a substantially rear side of the damper axis m with regard to the transverse direction of the vehicle and extended substantially inwardly upwardly in the transverse direction. The gentle slope 74a is located at a substantially front side of the damper axis m and extended substantially outwardly upwardly. The support member 62 is formed with a pair of recesses 76 and 78 located between the thin portions 60a, 60b and thick portions 60c, 60d respectively. The recesses 76 and 78 are formed by gentle slopes 76a, 78b extending substantially in parallel with the gentle slopes 72a, 74a of the projections 72, 74 and abrupt slopes 76b, 78b providing the thick portions 60c, 60d. In operation, when the vehicle is in the cornering operation, the upper end of the piston rod 3b is displaced downwardly at the front portion and upwardly at the rear portion. With this operation, there is described hereinafter a displacement of the upper end portion of the piston rod 3b in connection with displacements of points P and Q on the bracket 48 which is displaced together with the upper end portion of the piston rod 3b. The points P and Q are located on the gentle slopes 72a and 74a of the bracket 48 and on the line n at the opposite sides of the piston rod 3b. In the point P, the bracket 48 is forced to be displaced upwardly to compress the resilient member 60 at the thin portion 60a so that the bracket 48 is subjected to a force downwardly from the resilient member 60 as a counterforce as shown by an arrow P₁. In this case, the counterforce P₁ produces a horizontal component force as shown by an arrow P₂ because of the slope 72a so that the sum of the counterforces P₁ and P₂ acts on the point P in a direction shown by an arrow P₃ which is directed inwardly with regard to the transverse direction of the vehicle. On the other hand, in the point Q, the bracket 48 is forced be displaced downwardly to stretch the resilient member 60 at the thin portion 60b so that the bracket 48 is subjected to a force upwardly from the resilient member 60 as a counterforce as shown by an arrow Q₁. In this case, the counterforce Q₁ produces a horizontal component force as shown by an arrow Q₂ because of the slope 72a so that the sum of the counterforces Q₁ and Q₂ acts on the point P in a direction shown by an arrow Q₃ which is also directed inwardly with regard to the transverse direction of the vehicle. These counterforces P₃, Q₃ cause the upper end portion of the piston rod 3b to be displaced inwardly. And in the thick portions 60c and 60d of the resilient member 60, there is produced no substantially horizontal force which causes the piston rod 3b to be displaced. As a whole, the upper end portion of the piston rod 3b is displaced inwardly during the cornering operation of the vehicle. When the vehicle is in a straight path driving and the wheel 7 is forced to be displaced upwardly, the piston rod 3b is also displaced upwardly along the damper axis m so that the resilient member 60 is deformed upwardly and uniformly. Although this causes a slight upward and rotative displacement of the upper end of the piston rod 3b, there is produced no transverse displacement of the piston rod 3b relative to the body member 13. This means that there occurs no camber angle change in the wheel 7 during the straight path driving of the vehicle. It will be apparent from the above description that many modifications and variations may be made by those skilled in the art without apart from the scope of the claims as attached.

Claims: A vehicle suspension mechanism (1) including a strut assembly (2) connected with the vehicle body (13) at an upper end portion and with a wheel (7) at a lower end portion, further including a damper axis (m) along which a shaft means (3b) of the strut assembly is displacable for a damping effect, said axis being extended oblique to a kingpin axis (1) about which the wheel (7) is steered so that the shaft means (3b) is inclined when the wheel (7) is steered to produce a pivotal movement about the kingpin axis (1), further including conversion means (12) provided at the upper end portion of the strut assembly (2) that displaces the upper end of the strut assembly (2) in a transverse direction of the vehicle, characterized in, that the conversion means (12) displaces the upper end of the strut assembly (2) in a transverse direction of the vehicle under the action of the moment acting on the strut assembly (2) caused by the inclination of the shaft means (3b) produced during the steering action of the wheel (7). A vehicle suspension mechanism (1) in accordance with claim 1 wherein the suspension mechanism (1) further comprises support means provided on the vehicle body (13) and having an opening in which the shaft means (3b) is coaxially located, resilient guide means (12a, 12b, 12c) interposed between the shaft means (3b) and the support means, the resilient guide means (12a,12b,12c) being adapted to convert the inclination of the shaft means (3b) produced during the steering action of the wheel (7) to a displacement in a transverse direction of the vehicle at the upper end of the strut assembly (2). A vehicle suspension mechanism (1) in accordance with claim 2 wherein the resilient guide means comprises first resilient means (12ba, 12aa) located on opposite sides of the shaft means (3b) in a longitudinal direction of the vehicle body (13) and second resilient means (12bb, 12ab) located on opposite sides of the shaft means (3b) in a transverse direction of the vehicle body (13); the first resilient means (12ba, 12aa) being located higher than the second resilient means (12bb, 12ab). A vehicle suspension mechanism in accordance with claim 2 wherein the resilient guide means is provided with main resilient means and first resilient means extended upwardly from the main resilient means, the first resilient means being located on opposite sides of the shaft means in a longitudinal direction of the vehicle body. A vehicle suspension mechanism in accordance with claim 2 wherein the resilient guide means is provided with main resilient means and second resilient means extended downwardly from the main resilient means, the second resilient means being located on opposite sides of the shaft means in a transverse direction of the vehicle body. A vehicle suspension mechanism in accordance with claim 4 wherein the resilient guide means is provided with main resilient means and second resilient means extended downwardly from the main resilient means, the second resilient means being located on opposite sides of the shaft means in a transverse direction of the vehicle body. A vehicle suspension mechanism in accordance with claim 4 wherein the opening of the support means and externals of the shaft means (3b) are of circular configurations respectively, the main resilient means interposed between the support means and the shaft means (3b) having a circular plate configuration. A vehicle suspension mechanism in accordance with claim 1 wherein the suspension mechanism further comprises support means (13a) provided on the vehicle body (13) and having an opening in which the shaft means (3b) is coaxially located, a pair of link means (31, 32) connected with the support means (13a) at one end and with the upper end of the shaft means (3b) of the strut assembly (2) at the other end, connecting points (21, 22 ; 27, 28) of the link means to the support means (13a) and the shaft means (3b) being arranged in a manner that the shaft means (3b) is swung in a transverse direction of the vehicle body (13) when the wheel (7) is steered and the shaft means (3b) produces a rotative movement when the wheel (7) is displaced along the damper axis (m). A vehicle suspension mechanism in accordance with claim 8 wherein the connecting points at the other ends (21, 22) of the link means are positioned higher than those at the one ends (27, 28) of the link means (31, 32) so that the link means (31, 32) are extended to cross each other in a direction oblique to the damper axis (m). A vehicle suspension mechanism in accordance with claim 9 wherein the link means (31, 32) are pivotally connected with the support means (13a) at one end in a longitudinal direction of the vehicle body (13) and with the shaft means (3b) of the strut assembly (2) at the other ends in a transverse direction of the vehicle body (13). A vehicle suspension mechanism in accordance with claim 10 wherein first link means (31) is pivotally connected with the support means (13a) at one end at a forward position of the shaft means (3b) and with the shaft means (3b) at the other end at an inward position of the shaft means (3b), and second link means (32) is pivotally connected with the support means (13a) at one end at a rearward position of the shaft means (3b) and with the shaft means (3b) at the other end at an outward position of the shaft means (3b). A vehicle suspension mechanism in accordance with claim 11, resilient means (34) being interposed between the shaft means (3b) and the support means (13a). A vehicle suspension mechanism in accordance with claim 1 wherein the suspension mechanism is provided with support means (13a) connected with the vehicle body (13), shaft means (3b) disposed downward of the support means (13a) and connected with the support means (13a) through resilient means (60, 64), the shaft means (3b) being formed at an upper surface with a slope which is located at a substantially front side of the damper axis and extended substantially outwardly upwardly with regard to the transverse direction of the vehicle, the support means being formed at a lower surface with a slope extending substantially in parallel with the slope of the shaft means, the resilient means (60) being interposed between the slopes of the shaft means and support means. A vehicle suspension mechanism in accordance with claim 1 wherein the suspension mechanism is provided with support means (13a) connected with the vehicle body (13), shaft means (3b) disposed downward of the support means (13a) and connected with the support means (13a) through resilient means (60, 64), the shaft means (3b) being formed at an upper surface with a slope which is located at a substantially rear side of the damper axis and extended substantially inwardly upwardly with regard to the transverse direction of the vehicle, the support means being formed at a lower surface with a slope extending substantially in parallel with the slope of the shaft means, the resilient means (60) being interposed between the slopes of the shaft means (3b) and support means (13a). A vehicle suspension mechanism in accordance with claim 13 wherein the suspension mechanism is provided with support means (13a) connected with the vehicle body (13), shaft means (3b) disposed downward of the support means (13a) and connected with the support means (13a) through resilient means, the shaft means (3b) being formed at an upper surface with a slope which is located at a substantially rear side of the damper axis and extended substantially inwardly upwardly with regard to the transverse direction of the vehicle, the support means (13a) being formed at a lower surface with a slope extending substantially in parallel with the slope of the shaft means, the resilient means (60) being interposed between the slopes of the shaft means (3b) and support means (13a).

Inventors: KONDO, TOSHIRO
Applicants: MAZDA MOTOR CORPORATION
Application year: 1988
Main classification: B60G15
IPC codes: F16F1, B60G15, B60G3