Steerable axle support linkage

Abstract: A tractor having a steerable axle (15) that pivotally moves laterally in response to a corresponding steering action of the steerable wheels (17) mounted on the steerable axle (15) is disclosed wherein the front of the axle (15) is pivotally supported by a four-bar linkage (30) to control vertical movement of the chassis (11) relative to the steerable axle (15) during lateral relative movement between the chassis (11) and the axle (15). The mechanism is composed of a spherical ball joint (13) connecting the steerable axle (15) to the chassis (11), a front carrier member (31) pivotally connected to the chassis (11), and a pair of link members (35) pivotally interconnecting the carrier member (31) and the steerable axle (15). All pivot axes associated with the carrier member (31) and the link members (35) coincide at the spherical ball joint (13).

Description: This invention relates generally to a steering mechanism for an agricultural tractor in which the front axle is laterally shiftable in response to a steering movement of the steerable wheels and, more particularly, to a linkage mechanism pivotally connecting a laterally shiftable steering axle to a vehicle chassis, such as defined in the preamble of claim 1 or 10 and known for example WO-A-8907545. Tractors, whether used in an agricultural setting or in an industrial setting, typically include a fixed axle through which primary driving power is transferred through fixed wheels rotatably mounted on opposing ends of the fixed axle, and a steering axle having pivotally mounted steerable ground engaging wheels rotatably mounted on the opposing ends thereof to support the chassis of the tractor above the ground. Supplemental driving power is often provided through the steerable ground engaging wheels, while a steering mechanism remotely controllable by the operator from the operator's compartment selectively controls the pivotal movement of the steerable wheels relative to the steering axle. One such steering mechanism incorporates a transversely disposed, horizontally extending hydraulic cylinder supported by the steering axle and connected to the opposing steerable wheels. This hydraulic cylinder affects pivotal movement of the steerable wheels about their respective pivotal connections to the steering axle by manipulating the pressures in the hydraulic cylinder to effect a transverse displacement of the cylinder rod, causing a turning of the wheels. Due to physical limitations relating to the range of movement of the steering mechanism and to the eventual interference between the steerable wheels and the steering axle or chassis frame, the amount of pivotal movement of the steerable wheels relative to the steering axle is limited by tire size and track setting to a given restricted turning angle. This maximum turning angle defines the minimum turning radius of the tractor for a given chassis clearance width, axle oscillation angle, wheel base length and king pin spacing. The selection of the length of the wheel base, i.e. the distance between the fixed axle and the steering axle, is a compromise between the need to minimize the turning radius and, therefore, minimize the wheel base length, and to maximize ride considerations which require longer wheel base lengths. These conflicting wheel base requirements can be better resolved by a steering mechanism incorporating a laterally shifting front axle that is movable in response to a corresponding steering movement of the steerable wheels, which will decrease the turning radius of the tractor for any given wheel base length. The mechanism mounting the steerable axle to the vehicle chassis must accommodate the relative lateral movement between the steering axle and the chassis. However, in known prior art arrangements, such as shown in WO-A-8907545, a substantially constant chassis elevation is not maintained as the axle and chassis move relative to one another in a generally horizontal plane. Moreover, in WO-A-8907545, due to the structural design, the steerable wheels are not maintained in their imposed position when the front axle oscillates vertically. EP-A-0.581.380 is a document comprised in the state of the art according to Article 54(3) EPC and schematically shows a linkage mechanism forming the basis of the present invention, without however providing any details on the relative positions of the pivots and the orientation of the pivot axes. It therefore is the objective of the present invention to overcome the aforementioned disadvantage of the prior art by providing a linkage mechanism interconnecting the transverse steerable axle and the vehicle chassis which maintains a generally substantially constant chassis elevation during relative lateral movement between the axle and the chassis and by which the position of the steerable wheels is not influenced when the axle oscillates vertically. According to a first aspect of the present invention, a steerable axle assembly is provided connectable to a vehicle chassis at a spherical, first pivot joint carried by said vehicle chassis; said first pivot joint defining a generally vertically extending first pivot axis and said axle assembly, when connected to said vehicle chassis, being laterally moveable relative thereto about said first pivot axis; said axle assembly comprising : a transverse axle having a pair of steerable wheels pivotally connected to the opposing transverse ends of said axle; a carrier mechanism pivotally attached thereto and pivotally connectable to said vehicle chassis by pivot axes aligned with the center of said first pivot joint and by a second pivot joint; and at least one tying link extendable between steering means associated with a steerable wheel and said chassis. The steerable axle assembly is characterized in that : when said carrier mechanism is connected to said chassis, said second pivot joint extends generally horizontally and is aligned with said first pivot joint thereby defining a second pivot axis for allowing oscillatory movements of said axle assembly relative to said chassis when connected thereto; and the line extending longitudinally through said at least one tying link when connected to said chassis intersects with said second pivot axis. The carrier mechanism preferably takes the form of a four-bar linkage apparatus including a carrier member and a pair of link members interconnecting the carrier member and the steerable axle. With such an arrangement, any limited relative vertical movement of the tractor chassis relative to the transverse axle occurs in a generally parallel orientation. All of the pivot axes of the linkage mechanism interconnecting the transverse steering axle and the vehicle chassis intersect at the rearward pivot joint connecting the center housing of the steering axle to the vehicle chassis. Said rearward pivot joint is a spherical ball joint and therefore allows a universal movement of the transverse axle, including the lateral movement in a generally horizontal plane needed to improve vehicle steering characteristics. The carrier member and link members are positioned forwardly of the transverse steerable axle to position the axle between the carrier member and the spherical ball joint pivotally connecting the axle to the vehicle chassis. According to a second aspect of the present invention, a vehicle is provided having a chassis, a steerable axle assembly connected to said chassis at a spherical, first pivot joint carried by said chassis; said first pivot joint defining a generally vertically extending first pivot axis and said axle assembly being laterally moveable relative to said chassis about said first pivot axis; said axle assembly comprising : a transverse axle having a pair of steerable wheels pivotally connected to the opposing transverse ends of said axle; a steering mechanism operably connected to said steerable wheels to control the pivotal movement thereof relative to said axle for controlling the direction of travel of said vehicle, said steering mechanism including means for effecting relative pivotal movement between said axle and said chassis in response to the pivotal movement of said steerable wheels, a carrier mechanism pivotally attached to said axle assembly and pivotally connected to said vehicle chassis by a second pivot joint; and at least one tying link extended between steering means associated with a steerable wheel and said chassis. The vehicle is characterized in that : said second pivot joint extends generally horizontally and is aligned with said first pivot joint thereby defining a second pivot axis for allowing oscillatory movements of said axle assembly relative to said chassis; the line extending longitudinally through said at least one tying link intersects with said second pivot axis; and said axle assembly further comprises pivot connection means interconnecting said transverse axle and said carrier member to define at least a third pivot axis extending generally horizontally and being aligned with said first pivot joint, said pivot connection means allowing a generally lateral pivotal movement of said transverse axle about said first pivot axis in a parallel orientation relative to said chassis. A linkage mechanism for connecting a steerable axle to a vehicle chassis in accordance with the present invention will now be described in greater detail, by way of example, with reference to the accompanying drawings, in which : Figure 1 is a top plan view of a front axle assembly for an agricultural tractor incorporating the principles of the instant invention, the front portion of the tractor chassis overlying the front axle assembly being shown in phantom; Figure 2 is a cross-sectional view of the front axle assembly taken along lines 2-2 of Figure 1, the front portion of the tractor chassis being shown in phantom relative to the front axle assembly; Figure 3 is a cross-sectional view of the tractor front axle assembly taken along lines 3-3 of Figure 1 to depict generally a front elevational view of the tractor assembly immediately rearwardly of the weights; Figure 4 is a cross-sectional view of the front axle assembly similar to Figure 2, but with the front ballast assembly removed to better depict the linkage pivotally interconnecting the steerable axle and the vehicle chassis; Figure 5 is a top plan view of the front axle assembly similar to the view of Figure 1, but with the front ballast assembly removed for purposes of clarity; Figure 6 is a top plan view of the front axle assembly similar to the view of Figure 5 but with the steerable axle and steerable wheels moved to effect a right turn of the vehicle; Figure 7 is a front elevational view of the tractor front axle assembly similar to the view of Figure 3, but with the front ballast assembly removed for purposes of clarity; and Figure 8 is a front elevational view of the front axle assembly similar to the view of Figure 7, but with the steerable axle and steerable wheels moved to effect a right hand turn of the vehicle as depicted in Figure 6. Referring now to Figures 1-3, a laterally shifting front axle assembly for an agricultural tractor or other vehicle, pivotally connected to the vehicle chassis to provide a decreased turning radius for an given wheel base, can best be seen. The front axle assembly 10 is pivotally connected to the tractor chassis 11 for pivotal movement about a generally vertical axis 12, thereby allowing the front axle assembly 10 to rotate about the pivot axis 12 and shift the front axle assembly 10 laterally relative to tractor chassis 11. The pivot axis 12 includes a spherical ball joint 13 to permit some oscillatory movement of the front axle 15 relative to the chassis 11. The details of a laterally shiftable front axle assembly to provide better turning capabilities is described in detail in US-A-5.046.577. The front axle assembly 10 includes a transversely extending axle member 15 having pivotally mounted on the respective laterally opposing ends thereof a pair of steerable wheels 17 pivotable about respective nearly vertical king pin axes 18 to effect a steering of the wheels 17 relative to the axle member 15. A pair of hydraulic cylinders 19 interconnect the axle member 15 and the steerable wheels 17 via a steering arm 27 to control the pivotable movement of the wheels 17 relative to the axle member, and thereby, effect steering. The front axle member 15 carries a rearwardly extending subframe member 21 which carries the vertical pivot 12 and ball joint 13 connected to the tractor chassis 11 rearwardly of the front axle member 15 yet generally positioned laterally between the front steerable wheels 17. A front yoke assembly 30 suspends the laterally shiftable front axle member 15 from the forward end of the tractor chassis 11 to permit a pivotal movement of the front axle assembly 10 relative to tractor chassis 11 about the vertical axis 12. To facilitate relative movement between the front axle assembly 10 and the tractor chassis 11 when the axle is fully oscillated, the front axle member 15 is also provided with an arcuate track 24 having a center of curvature coincident with the pivot axis 12. The chassis 11 carries a pair of laterally spaced rollers 26 that are engageable with the arcuate track 24 when the front axle member 15 oscillates about a generally horizontal axis in response to changing ground contours and undulations so that the rollers 26 provide a limit to the vertical movement of the front axle member 15 relative to the tractor chassis 11 due to an engagement thereof with the arcuate track 24. A pair of tie rods 28 interconnecting the chassis 11 and the steerable wheels 17 transmit coordinated steerable movement of the wheels 17 relative to each other and to the front axle member 15 and to a lateral shifting movement of the chassis 11 relative to the front axle 15. Although the front axle 15 is pivotally connected to the chassis 11, the front axle 15 is engaged with the ground through the wheels 17 and the actual pivotal movement results in a lateral shifting of the chassis 11. Looking at the front axle 15 from the reference frame of the chassis 11, the appearance is that the axle 15 shifts relative thereto and any reference hereinafter describing the pivotal movement of the front axle member 15 relative to the chassis is so described. Because of the fixed length of the tie rods 28 interconnecting the chassis 11 and the wheels 17 at a connection point 29 spaced inwardly toward the center of the chassis 11 and rearwardly from the respective pivot axis or king pin 18 for the corresponding steerable wheel 17 by a rearwardly and inwardly extending steering arm 27, a pivotable movement of the wheel 17 about the corresponding pivot axis 18 will result in a corresponding shifting of the front axle 15 relative to the center (not shown) of a tractor chassis 11, along which the vertical pivot axis 12 is positioned. The front yoke assembly 30 has a contoured front carrier member 31 pivotally connected at a second pivot joint 32 to the chassis 11. The front carrier member 31 also carries a pair of transversely spaced third and fourth lower pivots 33, 34, respectively, for pivotally supporting a corresponding pair of dog bone-shaped links 35 which, in turn, are pivotally connected to the front axle member 15 by respective transversely spaced fifth and sixth pivots 36, 37. As depicted in Figure 4, each of the pivots 32, 33, 34, 36 and 37 associated with the front yoke assembly 30 have a corresponding pivot axis aligned with the ball joint 13, which is located on the pivot axis 12. Accordingly, the pivot axis for each of the five pivots 32, 33, 34, 36 and 37 have a nonparallel relationship intersecting a common point at the center of the ball joint 13. As a result, the pivotal movement of the front axle assembly 10 relative to the tractor chassis 11, resulting in a lateral shifting of the front axle member 15, is accomplished through a four-bar linkage which has very little vertical component associated with the movement thereof, yet the chassis 11 maintains a substantially uniform elevation relative to the front axle 15 throughout the range of relative movement between the front steerable axle and the vehicle chassis. The main pivot axis for lateral shifting and vertical oscillatory movement of the front axle 15 is the axis defined by the second pivot joint 32 extending through the ball joint 13, as both the pivot 32 and the ball joint 13 are fixed relative to the chassis 11. The generally transverse lines defined by the tie rods 28 extend through this main pivot axis extending through pivot 32 and ball joint 13 so that movements of the axle 15, especially oscillatory movements, causes a minimum additional steering effect to the axle 15. As depicted in Figures 1-3, the front axle assembly 10 may be powered in a conventional manner from the transmission (not shown) carried by the tractor chassis 11 through the front wheel drive shaft 38 connected to a conventional front wheel drive mechanism 39 to operatively power the rotation of the steerable wheels 15 to facilitate movement of the tractor chassis 11 over the ground. One skilled in the art will readily realize that the provision of a front wheel drive mechanism 39 is optional and independent of the operation of the compound steering mechanism permitting a lateral shifting of the tractor chassis 11 relative to the front axle member 15. The continuous driving of the front wheels 17 during steering operation involving a lateral shifting of the tractor chassis 11 relative to the front axle member 15 can be accommodated by the universal joint 39a interconnecting the front wheel drive mechanism 39 and the drive shaft 38. The tractor ballast assembly 40 is carried by the front axle assembly 10 intermediate of the steerable wheels 17 at a position centrally therebetween. A carrier 42 is detachably connected by fasteners 43 to the front axle member 15 to extend forwardly thereof and forwardly of the tractor chassis 11, as well. The carrier 42 is provided with an arcuate mounting ring 44 upon which individual suitcase weights 45 are supported. Since the carrier 42 moves with the front axle member 15 relative to the chassis 11, the position of the ballast assembly 40 relative to the laterally spaced front wheels 17 remains relatively fixed, thereby maintaining a substantially constant weight distribution relative to the front wheels 17. Furthermore, since the ballast assembly 40 moves with the axle member 15, the steering clearance between the pivotally movable wheels 17 and the ballast assembly 40 does not change as the front axle 15 shifts laterally and/or oscillates vertically. As a result, the operator may mount additional weight units 45 to increase the amount of ballast on the front axle 15 without decreasing the tire clearance below that which is acceptable for traditional tractors. Greater detail in the construction and assemblage of the individual weights 45 to form the ballast assembly 40 can be found in US-A-5219180 (corresponding to EP-A-0581380 and published on 15.06.93). The configuration of the components of the front yoke assembly 30, chassis 11 and front steerable axle 15, as the tractor steering mechanism 19 effects a turn of the tractor chassis 11, is best seen in Figures 5 - 8. The dog-bone link members 35 diverge upwardly so that the fifth and sixth pivot joints are transversely spaced further apart than the third and fourth lower pivot joints to provide a nearly parallel planar motion of the chassis 11 relative to the axle 15 and an increased measure of stability to the assembly 30. A turning of the steerable wheels 17, as exemplified by the right turn depicted in Figures 6 and 8, causes a corresponding relative shifting between the steerable axle 15 and the chassis 11, which in the frame of reference of the chassis 11 causes a shifting of the axle 15 in the direction of the intended turn. As described above, this relative shifting of the axle 15 shortens the turning radius and allows the tractor to make a tighter turn. During such a turn, the tie rods 28 force the chassis 11 in the opposite direction from which the turn is being made, which in the frame of reference of the chassis 11 causes a relative movement of the axle 15 about the first pivot axis 12 into the direction of the turn being made. When the axle 15 moves relative to the chassis 11, the carrier member 31 pivots about its pivotal connection 32 with the chassis 11, as shown in Figures 6 and 8, swinging the third and fourth lower pivots 33, 34 and the connected dog-bone link members 35 toward the direction the turn is being made. Because of the configuration of the four pivots 33, 34, 36 and 37 associated with the two link members 35, the fifth and sixth upper pivots 36, 37 swing toward the direction of the turn in a parallel orientation to which they were centrally positioned. As a result, the vertical movement of the axle 15 relative to the chassis 11 is minimized during turns. The disclosed assembly 30 has been found to result in a lowered elevational change of the chassis 11 of approximately a quarter of an inch during turns, and during this minimal vertical movement, the chassis 11 remains in a parallel orientation with respect to its position prior to the turn. The spherical ball joint 13 at the first pivot 12 accommodates any limited vertical movement of the axle 15 relative to the chassis 11 and allows oscillatory or lateral pitching movement of the axle 15 relative to the chassis 11 about the pivot 32. This oscillatory movement of the axle 15 can cause greater pivotal movement of the carrier member 31 about the pivot 32 than is shown in Figures 6 and 8. This particular configuration of components pivotally mounting the axle 15 to the chassis 11 for relative lateral movement results in a minimum of elevational changes for the chassis, irrespective of the movement of the axle 15, which in turn provides the ability to utilize front mounted attachments for the chassis 11 without affecting their operation during turns. Furthermore, the respective tie rods 28 are oriented such that the inwardly extending line of each of the tie rods 28 from the connection point 29 will intersect with the pivot axis extending between the pivot joint 32 and the center of the ball joint 13. This orientation of the tie rods 28 minimizes any steering effect to the wheels 17 whenever the axle 15 oscillates relative to the chassis 11. The centering of all the pivot axes associated with the pivot joints 32, 33, 34, 36 and 37 at the center of the ball joint 13 allows the unrestricted pivotal movement of the carrier member 31 and the dog-bone link members 35 during the turning movements and for oscillatory or pitching movements as well, without requiring additional motion components to be accommodated during the relative movement of the axle 15 and the chassis 11. It will be understood by one skilled in the art that the specific orientation of these respective pivots 32, 33, 34, 36 and 37 requires the formation of a specially formed carrier member 31 and dog-bone members 35 to orient properly the respective pivots. Furthermore, the carrier member 31 has a somewhat arcuate shape to bow out around the dog-bone members 35 for their unrestricted movement between the carrier member 31 and the axle 15. It will be understood that changes in the details, materials, steps and arrangements of parts which have been described and illustrated to explain the nature of the invention will occur to and may be made by those skilled in the art upon a reading of this disclosure within the principles and scope of the invention. The foregoing description illustrates the preferred embodiment of the invention; however, concepts, as based upon the description, may be employed in other embodiments without departing from the scope of the invention, such as defined in the claims.

Claims: A steerable axle assembly (10) connectable to a vehicle chassis (11) at a spherical, first pivot joint (13) carried by said vehicle chassis (11); said first pivot joint (13) defining a generally vertically extending first pivot axis (12) and said axle assembly (10), when connected to said vehicle chassis (11), being laterally moveable relative thereto about said first pivot axis (12); said axle assembly (10) comprising : a transverse axle (15) having a pair of steerable wheels (17) pivotally connected to the opposing transverse ends of said axle (15); a carrier mechanism (30) pivotally attached thereto and pivotally connectable to said vehicle chassis (11) by pivot axes aligned with the center of said first pivot joint (13) and by a second pivot joint (32); and at least one tying link (28) extendable between steering means (27) associated with a steerable wheel (17) and said chassis (11); and characterized in that : when said carrier mechanism (30) is connected to said chassis (11), said second pivot joint (32) extends generally horizontally and is aligned with said first pivot joint (13) thereby defining a second pivot axis for allowing oscillatory movements of said axle assembly (10) relative to said chassis (11) when connected thereto; and the line extending longitudinally through said at least one tying link (28) when connected to said chassis (11) intersects with said second pivot axis. An axle assembly (10) according to claim 1 characterized in that said axle assembly (10) comprises a pair of tie links (28) in the form of rods extendable substantially transversely to the vehicle drive direction and interconnectable between said chassis (11) and said steerable wheels (17) to effect a lateral shifting of said transverse axle (15) in response to the pivotal movement of said wheels (17) relative to said axle (15). An axle assembly (10) according to claim 1 or 2 characterized in that said carrier mechanism (30) comprises: a carrier member (31) pivotally supportable by said vehicle chassis (11) by said second pivot joint (32) carried by said vehicle chassis (11) and defining said second pivot axis extending generally horizontally and being aligned with said first pivot joint (13); and pivot connection means (33-37) interconnecting said steerable axle (15) and said carrier member (31) to define at least a third pivot axis extending generally horizontally and being aligned with said first pivot joint (13). An axle assembly (10) according to claim 3 characterized in that said pivot connection means (33-37) includes: first and second link members (35) interconnecting said carrier member (31) and said axle (15); a third pivot joint (33) interconnecting said carrier member (31) and said first link member (35) to define said third pivot axis; a fourth pivot joint (34) transversely spaced from said third pivot joint (33) to interconnect said carrier member (31) and said second link member (35) and define a fourth pivot axis extending generally horizontally and being aligned with said first pivot joint (13); a fifth pivot joint (36) interconnecting said first link member (35) and said axle (15) to define a fifth pivot axis extending generally horizontally and being aligned with said first pivot joint (13); and a sixth pivot joint (37) transversely spaced from said fifth pivot joint (36) and interconnecting said second link member (35) and said axle (15) to define a sixth pivot axis extending generally horizontally and being aligned with said first pivot joint (13). An axle assembly (10) according to claim 4 characterized in that said first link member (35) is connected at one end to said third pivot joint (33) and at a remote second end to said fifth pivot joint (36); and said second link member (35) is connected at one end to said fourth pivot joint (34) and at a remote second end to said sixth pivot joint (37). An axle assembly (10) according to claim 4 or 5 characterized in that the transverse distance between said fifth and sixth pivot joints (36, 37) is greater than the transverse distance between said third and fourth pivot joints (33, 34). An axle assembly (10) according to any of the preceding claims characterized in that said axle (15) defines a transverse major axis and rotatably mounts said opposing transversely spaced steerable wheels (17) at the opposite ends of said transverse major axis, said first pivot joint (13) being located rearwardly of said transverse major axis. An axle assembly (10) according to claim 7 when appended either directly or indirectly to claim 4 characterized in that the carrier member (31) and the link members (35) are positioned forwardly of said axle (15) with said transverse major axis of said axle (15) being positioned between said carrier member (31) and said first pivot joint (13). An axle assembly (10) according to any of the preceding claims characterized in that said first pivot joint (13) permits movement of said steerable axle (15) in a universal manner, including pivotal movement in a generally horizontal manner about said first pivot axis (12). A vehicle having a chassis (11), a steerable axle assembly (10) connected to said chassis (11) at a spherical, first pivot joint (13) carried by said chassis (11); said first pivot joint (13) defining a generally vertically extending first pivot axis (12) and said axle assembly (10) being laterally moveable relative to said chassis (11) about said first pivot axis (12); said axle assembly (10) comprising : a transverse axle (15) having a pair of steerable wheels (17) pivotally connected to the opposing transverse ends of said axle (15); a steering mechanism operably connected to said steerable wheels (15) to control the pivotal movement thereof relative to said axle (15) for controlling the direction of travel of said vehicle, said steering mechanism including means for effecting relative pivotal movement between said axle (15) and said chassis (11) in response to the pivotal movement of said steerable wheels (15), a carrier mechanism (30) pivotally attached to said axle assembly and pivotally connected to said vehicle chassis (11) by a second pivot joint (32); and at least one tying link (28) extended between steering means (27) associated with a steerable wheel (17) and said chassis (11); and characterized in that : said second pivot joint (32) extends generally horizontally and is aligned with said first pivot joint (13) thereby defining a second pivot axis for allowing oscillatory movements of said axle assembly (10) relative to said chassis (11); the line extending longitudinally through said at least one tying link (28) intersects with said second pivot axis; and said axle assembly (10) further comprises pivot connection means (33-37) interconnecting said transverse axle (15) and said carrier member (31) to define at least a third pivot axis extending generally horizontally and being aligned with said first pivot joint (13), said pivot connection means (33-37) allowing a generally lateral pivotal movement of said transverse axle (15) about said first pivot axis (12) in a parallel orientation relative to said chassis (11). A vehicle according to claim 10 characterized in that said pivot connection means (33-37) includes: first and second link members (35) interconnecting said carrier member (31) and said transverse axle (15); a third pivot joint (33) interconnecting said carrier member (31) and said first link member (35) to define said third pivot axis; a fourth pivot joint (34) transversely spaced from said third pivot joint (33) to interconnect said carrier member (31) and said second link member (35) and define a fourth pivot axis extending generally horizontally and being aligned with said first pivot joint (13); a fifth pivot joint (36) interconnecting said first link member (35) and said transverse axle (15) to define a fifth pivot axis extending generally horizontally and being aligned with said first pivot joint (13); and a sixth pivot joint (37) transversely spaced from said fifth pivot joint (36) and interconnecting said second link member (35) and said transverse axle (15) to define a sixth pivot axis extending generally horizontally and being aligned with said first pivot joint (13). A vehicle according to claim 11 characterized in that said transverse axle (15) includes a longitudinally elongated center housing (21) for connection between said first and said fifth and sixth pivot joints (13, resp. 36 and 37).

Inventors: HURLBURT JOSEPH C, LINDE GILBERT W, HURLBURT, JOSEPH C., LINDE, GILBERT W.
Applicants: NEW HOLLAND UK LTD, NEW HOLLAND U.K. LIMITED
Application year: 1993
Main classification: B62D7
IPC codes: B62D9, B62D7