Power-takeoff device for front-mounted implements

Abstract: A power-takeoff apparatus for use on a compact tractor equipped with a compound steering mechanism is disclosed wherein the chassis (10) includes a front chassis member (17) having an opening (18) formed therein to allow the passage of a power-takeoff shaft (50) therethrough for connection to a front-mounted implement (I) mounted to the steerable axle (12) for lateral movement therewith. The opening (18) in the front chassis member (17) has a sufficient transverse width to accommodate the lateral swinging movement of the power-takeoff shaft (50) in unison with the movement of the front-mounted implement (I). The front chassis member (17) is also adapted for mounting a front-mounted implement (I) thereto for providing an alternative mounting thereof so that the implement (I) will not move with the steerable axle (12).

Description: This invention relates generally to off-road motor vehicles, such as tractors, and more particularly, to a front power-takeoff drive connectable to a front mounted implement attached to the steerable axle of a compound steering mechanism. In the following description right hand and left hand references are determined by standing at the rear of the tractor facing in a direction of forward travel. Also, in the following description, it is to be understood that terms such as "forward", "rearward", "upward", etc., are words of convenience and are not to be construed as limiting terms. 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. Commonly, supplemental driving power is often provided to the steerable ground engaging wheels as well. 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 extension or retraction 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 chassis frame or the steering axle, the amount of pivotal movement of the steerable wheels relative to the steering axle is limited to a given turning angle. This maximum turning angle defines the minimum turning radius of the tractor for a given wheel base length and tread 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 resolved by a so-called compound steering mechanism incorporating a laterally shiftable 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. Because of the size and orientation of the axle support and oscillation components, known compound steering mechanisms, such as found in US-A-5.297.648, are not well suited for small tractors, particularly when front hitch and front PTO applications are desired. Economy is also a major concern with small tractors as the incremental cost of providing a compound steering mechanism becomes a greater percentage of the overall cost of the small tractor. By providing a compact pivotal support for the steerable axle and an oscillation stop package immediately behind the front axle, a front-mounted attachment could be brought closer to the axle and economies maintained. In general, front hitches for tractors are increasing in popularity, particularly in European farming operations. The adaptation of a compound steering mechanism as disclosed in the aforementioned US-A-5.297.648, cannot accommodate the use of a powered front-mounted implement as the structure of the tractor will not permit the passage of a power-takeoff shaft from the tractor engine to the implement. This is clearly visible in US-A-5.299.821 in which an implement is attached to such a compound steering axle. The pivotable support arms connecting the front axle to the chassis would interfere with an eventual power-takeoff shaft extending towards the front-mounted implement during steering movements. Moreover, by mounting the implement directly to the steerable axle, the implement will pivot with the axle about its steering axis, meaning that the implement will move laterally with respect to the chassis and the tractor engine. This lateral movement of the front-mounted implement further complicates the problem of providing a power-takeoff drive thereto as the power-takeoff shaft must be able to swing laterally in unison with the front-mounted implement. It is therefore an objective of the present invention to overcome the aforementioned disadvantages of the prior art by providing a power-takeoff drive for a tractor provided with a compound steering mechanism in which the front axle pivotally moves in response to the steering movement of the ground wheels. According to the present invention, a vehicle such as known from US-A-5299821 is provided comprising : a chassis; a generally transversely extending steering axle pivotally supported from said chassis for pivotal movement relative thereto about a steering axis, said steering axle including mounting means for connecting a front-mounted implement thereto for pivotal movement therewith about said steering axis; a pair of steerable wheels pivotally connected to the opposing transverse ends of said steering axle; steering means operably connected with said steerable wheels for selectively controlling the pivotal movement of said steerable wheels relative to said steering axle and for effecting relative pivotal movement between said axle and said chassis; and an engine supported on said chassis to provide a source of operative power for said vehicle. The vehicle according to the invention is characterized in that : said steering axle extends forwardly from said steering axis in a cantilevered manner underneath a front chassis member; and the vehicle further comprises a power-takeoff shaft extending forwardly from said engine and being adapted for connection to the front-mounted implement to transfer operative power thereto from said engine, said power-takeoff shaft passing between said front chassis member and said steering axle forwardly of said steering axis and being operable to move in unison with the pivotal movement of said front-mounted implement about said steering axis. As such, the turning radius for a tractor having a front-mounted implement mounted thereto can be decreased and a front power-takeoff drive advantageously can be provided for a tractor in which the steering axle is pivotally supported relative to the chassis by a pivot mechanism that is coupled to the steering mechanism for affecting a simultaneous pivotal movement of the steering axle relative to the chassis. The power-takeoff drive apparatus of the present invention can be combined with a compound steering design that can be adapted for small tractors to which powered front-mounted implements can be mounted and hence is compatible with front PTO applications. The present invention furthermore provides an improvement to the maneuverability and greater and more flexible utilization of small tractors while it nevertheless can be economically manufactured so as to minimize the incremental cost of providing such a steering mechanism for small, compact tractors. The advantages of this invention will be apparent upon consideration of the following detailed disclosure of the invention, especially when taken in conjunction with the accompanying drawings wherein: Figure 1 is a fragmentary top plan view of the steering axle incorporating the principles of the instant invention, located at the forward portion of a tractor chassis, the tie rod mounting plates being oriented in their inboardmost position; Figure 2 is a side elevational view of the steering mechanism shown in Figure 1, a representative engine, front PTO shaft and front steerable wheels being shown in phantom, a tie rod mounting plate oriented in its outboardmost position also being shown in phantom; Figure 3 is a cross-sectional view taken along lines 3-3 of Figure 1 to better show the details of the tie rods and hydraulic steering cylinders, the tie rod mounting plates being positioned in their outboardmost position with a front power-takeoff shaft being utilized; Figure 4 is a partial top plan view of the steering axle similar to that of Figure 1 with the steerable ground wheels being pivoted along with the steering axle into a maximum left turn position, the ground wheels are shown in an innermost mounted position to reflect the maximum inboard position of the ground wheels, the forward portion of the front chassis member being broken away to better show the steering mechanism, the tie rod mounting plates being oriented in their inboardmost position; Figure 5 is a cross-sectional view taken along lines 5-5 of Figure 1 to better show the oscillation stop mechanism and the upper and lower pivot joints forming a part of the pivot mechanism mounting the front axle to the tractor chassis; Figure 6 is a cross-sectional view similar to that of Figure 5, except that the right steerable wheel has vertically moved relative to the opposing steerable wheel sufficiently to engage the corresponding oscillation stop link; Figure 7 is a schematic cross-sectional view showing a side elevation of an alternate pivot mechanism connecting the front axle to the tractor chassis to best show the steering axis, the oscillation axis and the effective tension axis of the support link, the PTO shaft and the front wheel drive shaft being shown in phantom, a front mounted implement being mounted to the steerable axle and broken away to better show the details of the alternate pivot mechanism; Figure 8A is a schematic top plan view corresponding to the view of Figure 7 with the steering component effecting a straight ahead operation; Figure 8B is a schematic top plan view similar to that of Figure 8A, except that the right steerable wheel has been elevated to show the effect of front axle oscillation on the lower pivot and support link; Figure 9 is an enlarged detail view of the front chassis member to better depict the alternate mounting positions of the tie rod mounting plates shown in phantom, the left tie rod mounting plate being shown in the outboardmost position while the right tie rod mounting plate is shown in the inboardmost position, the related pivot mechanism and oscillation stop mechanism structure being removed for the purposes of clarity; Figure 10 is a partial cross-sectional view of the front chassis member taken along lines 10 - 10 of Figure 9 to depict an elevational view of the tie rod mounting plates in their opposite respective positions; Figure 11 is an enlarged schematic elevational view of the left oscillation stop mechanism depicting an alternative configuration of the stop link when in the straight ahead, non-turning orientation, an oppositely mounted stop link being shown in phantom; and Figure 12 is an enlarged schematic view similar to that of Figure 11, except that the steerable axle has undertaken pivotal movement relative to the chassis during a left turning operation. Referring now to the drawings and, particularly, to Figures 1-4, a compound steering mechanism incorporating the principles of the instant invention and being designed for incorporation into small, compact tractors can best be seen. The tractor chassis 10 consists of a conventional wheeled frame supported by front and rear axles having ground engaging wheels attached thereto. The chassis 10 is representatively shown throughout all of the drawings. One skilled in the art will readily recognize that the chassis 10 can also consist of a conventional "buckle-up" design in which the front axle is bolted to the engine E, which is bolted to the transmission, which is bolted to the rear axle assembly, etc., without the benefit of a formal frame structure supporting all of these components. In the drawings, only the front steerable axle 12 and the forward portion of the representative chassis 10 are depicted. The front steerable wheels 13 mounted on the opposing ends of the front axle 12 are pivotally connected to the axle 12 in a generally conventional manner so as to pivot about a king pin 14 relative to the front axle 12 to effect a steering or turning of the tractor T. The front wheels 13 can be mounted in a plurality of positions to vary the spacing between the opposing front wheels for different row crop spacings. Hydraulic steering cylinders 15 interconnect the front axle 12 with respective steering arms 16 extending rearwardly from the wheels 13 to control the pivotal steering movement thereof. The chassis 10 includes a front chassis member 17 that projects forwardly in a cantilevered manner, whether fastened to the main chassis frame 10 as depicted in the drawings or fastened to the engine block in a conventional "buckle-up" chassis design, to provide support for a radiator or other tractor or engine components. The steering mechanism 20 includes a pair of tie rods 21 pivotally connected to the respective steering arms 16 and extending inwardly therefrom to a pivotal connection with the front chassis member 17, which is provided with a plurality of bosses 19 terminating in a common plane. A detachable triangular mounting plate 25 supports a pivotal connection for the inboard end 22 of each respective tie rod 21. The mounting plates 25 are attachable to a corresponding set of bosses 19 to fix the inboard ends 22 of the tie rods 21 to the chassis 10. As will be described in greater detail below, the mounting plates 25 can be selectively mounted on alternative sets of bosses 19 to locate the inboard ends 22 of the tie rods 21 closer or further away from the longitudinal centerline of the tractor T. The front axle 12 has a rearwardly extending trumpet portion 29 connected to the front chassis member 17 by a steering pivot mechanism 30 defining a steering axis 31 about which the front axle 12 pivotally moves. The pivot mechanism 30 includes an upper pivot joint 32, preferably in the form of a spherical or ball joint to provide for proper swinging movement of the steering axis 31, as will be described in greater detail below. The upper pivot joint 32 is fixed in the front chassis member 17. The steering pivot mechanism 30 further includes a lower pivot joint 34 mounted in the trumpet portion 29 and connected to a support link 35 extending forwardly from a rearward pivot joint 38 mounted in a fixed location on the chassis 10. Both the lower and rearward pivot joints 34, 38 are preferably spherical joints to allow a multi-directional freedom of movement. During oscillation movements described in greater detail below, the lower pivot joint 34 will swing laterally relative to the upper pivot joint 32. The use of spherical joints at each of the pivots 32, 34, 38 will accommodate this oscillatory movement. One skilled in the art will readily recognize that the distance between the upper and lower pivots 32, 34 is fixed as both pivots 32, 34 are mounted to the trumpet portion 29. Likewise, the distance between the upper and rearward pivots 32, 38 is also fixed as both pivots 32, 38 are mounted to the chassis 10. The three pivots 32, 34, 38 form a "journaling triangle" to provide great flexibility in the freedom of movement of the front axle 12 in both steering and oscillation actions. To accommodate the position of the inboard front wheel 13 when located in its innermost position and undergoing a severe turning angle, as depicted in Figure 4, the front chassis member 17 is recessed in the area of the steering pivot mechanism 30. To facilitate assembly, the support link 35 is constructed as a two-piece device with a bolted joint 36 therebetween. At the connection with the rearward pivot 38, the support link 35 includes a U-shaped bracket 37 to allow the passage of a drive shaft 28 through the bracket 37 to connect with the front axle 12 to provide operative rotational power thereto. From the bracket 37 forwardly, the drive shaft 28 is shielded from below by the support link 35 as the drive shaft 28 passes between the support link 35 and the chassis 10. As best seen in Figure 7, one skilled in the art will recognize that the bolted joint 36 is located along an effective line of force passing between the lower and rearward pivots 34, 38 to minimize the forces on the fasteners connecting the bolted joint 36, as well as the fasteners retaining the pivot joints 34, 38. As can be best seen in Figures 1 - 8B, an oscillation stop mechanism 40 is provided to limit the vertical rolling oscillation of the front axle 12. As representatively depicted in Figure 6, the front axle 12 and trumpet portion 29 undergo a vertical rolling oscillation in response to undulations in the ground G, whenever one of the front wheels 13 becomes elevated, so that the chassis 10 can remain generally level. This rolling oscillatory movement of the front axle 12 is accommodated within the steering pivot mechanism 30 as the lower pivot joint 34 is free to swing laterally via the pivotal connection of the support link 35 through the rearward pivot 38. The purpose of the support link 35 is primarily to maintain the predetermined spacing between the rearward pivot 38 and the lower pivot 34, while allowing the lateral swinging movement of the lower pivot 34. Since the upper pivot 32 is a spherical joint, the steering axis 31 undergoes a corresponding movement remaining aligned with the fixed upper pivot 32 and the swingable lower pivot 34. Referring specifically to Figures 8A and 8B, the lower pivot 34 and, therefore, the front axle 12 rotate about an oscillation axis 41, corresponding to a line passing through the upper pivot 34 and the rearward pivot 38. The oscillation stop mechanism 40 provides a limit to the amount of rolling oscillatory movement permitted to the front axle 12 to prevent interference between various tractor components. The oscillation stop mechanism 40 includes a pair of laterally spaced stop links 42 positioned, respectively, on opposing sides of the steering pivot mechanism 30. Each stop link 42 passes through an upper bracket 46 formed as part of the front chassis member 17 and through a lower bracket 47 formed as part of the trumpet portion 29 of the front axle 12. Each stop link 42 has an upper and lower cupped flange 43, 44 having a curved surface engageable with a seat formed in the corresponding bracket 46, 47. One of the flanges 43, 44 is operatively engaged with an adjustment mechanism 45 to position that flange 43, 44 along the length of the stop link 42 and, thereby, selectively vary the distance between the upper and lower flanges 43, 44 to control the amount of rolling oscillation permitted the front axle 12. For ease of access, the upper flange 43 is preferably positionally adjustable. The normal operating distance between the upper and lower flanges 43, 44 is greater than the vertical distance between the upper and lower brackets 46, 47, as is best seen in Figure 5. Whenever one of the front wheels 13 rises in elevation relative to the other front wheel 13, as representatively demonstrated in Figure 6, the front axle 12 pivots about the oscillation axis 41 causing the upper and lower brackets 46, 47 corresponding to the front wheel 13 that is lower in elevation to separate a greater distance than the normal operating distance. At the point at which maximum desired rolling oscillation is reached, the bottom bracket 47 bottoms out against the lower flange 44. As a result, the stop link 42 then stops any further pivotal movement of the front axle 12 about the oscillation axis 41 and any further increases in elevation of the higher wheel will be transferred directly to the chassis 10. The oscillation stop mechanism 40 also operates to limit the rolling oscillation of the front axle 12 while steering. Since the lower brackets 47 move in a fore-and-aft direction when the front axle 12 pivots about the upper pivot joint 32, the effective distance between the upper and lower brackets 46, 47 increases as the front axle 12 pivots as part of the steering action, which in turn decreases the amount of rolling oscillation permitted to the front axle 12. One skilled in the art will readily realize that the manipulation of the adjustment mechanism 45 to reposition the upper flange 43 relative to the lower flange 44 will result in a variation of the amount of rolling oscillation permitted to the front axle 12 relative to the chassis 10. One skilled in the art will also recognize, as depicted in Figures 11 and 12, that a re-positioning of the stop link 42 relative to the upper and/or lower brackets 46, 47, such as within alternate mounting seats in the upper bracket 46, or an actual re-positioning of the upper and/or lower brackets 46, 47 to move the stop link 42 in a fore-and-aft direction will also change the operational characteristics of the oscillation stop mechanism 40 as a function of the steering angle. For example, a re-positioning of the stop links 42 within the upper brackets 46 rearwardly of the position depicted in Figure 2 would result in an increase in the permissible vertical raising of the front wheel 13 if the front wheel 13 moves forwardly relative to the chassis 10, as the effective distance between the opposing upper and lower brackets 46, 47 would decrease, and a decrease in the permissible vertical raising of the front wheel 13 when the front wheel 13 moves rearwardly relative to the chassis 10. Such an oscillation characteristic could be desirable if the chassis 10 can accommodate greater amounts of vertical movement of the front wheel 13 forwardly of the straight ahead position, such as when the front wheel 13 is positioned by the pivotal movement of the front axle 12 forwardly of the front chassis member 17, but would impact chassis 10 structure when the front wheel 13 is moved rearwardly of the straight ahead position. Referring now to all the Figures, but particularly to Figure 2, one skilled in the art will readily recognize that the engine E can be provided with a forwardly extending power-takeoff (PTO) shaft 50 to be operatively connected with an implement I positioned forwardly of the chassis 10 to provide operative power thereto. Both the front chassis member 17 and the front axle 12 are adapted with mounting bosses 52 to which forwardly positioned or front-mounted implements could be alternatively attached. By attaching a front-mounted implement to the front axle 12, the implement would pivotally move with the steering of the axle 12, as is described in greater detail in US-A-5.299.821. In some situations, however, the implement would be best operable if mounted on the chassis, which would then not move laterally with the steering motion of the front axle. Since the front chassis member 17 supports the radiator and other related structure thereabove through which the PTO shaft could not pass, the PTO shaft is routed from the engine E downwardly through an opening 18 in the rearward portion of the front chassis member 17. For the configuration of front-mounted implements attached to the front axle 12, the PTO shaft 50 must be free to swing from side to side with the steering movement of the front axle 12. Accordingly, the transverse width of the opening 18 is sufficiently large to accommodate the lateral movement of the PTO shaft. As best seen in Figure 3, further clearance for the movement of the PTO shaft 50 can be obtained by relocating the tie rod mounting plates 25 outwardly with respect to the longitudinal centerline of the vehicle to the alternate mounting bosses 25. Because of the limited amount of vertical pivoting movement permitted by the structure of conventional tie rod ball joints 23, a greater amount of front axle rolling oscillation can be obtained when the tie rods 21 are normally oriented horizontally and kept as long as possible. The attachment of the mounting plates 25 at the inboardmost set of mounting bosses provides the least restriction to front axle rolling oscillation. By moving the tie rod mounting plates 25 to the outboardmost set of mounting bosses, shorter length tie rods 21 must be used, resulting in more severe vertical pivoting at the tie rod ball joints 23 for any given amount of front axle rolling oscillation. Greater clearance for the PTO shaft 50 can be obtained by an arrangement of the outboardmost set of mounting bosses 19 to orient the mounting plate 25 in a fore-and-aft direction, as shown in Figures 3, 9 and 10. When moving the inboard ends 22 of the tie rods 21 outwardly to the alternate chassis mounts, the required overall length of the respective tie rod 21 becomes shorter, which can be accommodated by an adjustable tie rod, such as the depicted configuration in which two halves of the tie rod are threadably engaged, or by replacing the tie rod 21 with a new tie rod 21 of proper length. The trade-off for moving the tie rods 21 outwardly to provide adequate clearance for the swinging movement of the PTO shaft 50 is a more limited permissible rolling oscillation. Obviously, the operator is able to leave the tie rod mounting plates 25 at the inboardmost set of mounting bosses unless a front-mounted, PTO-driven implement is supported on the front axle 12 for lateral movement therewith, which in turn would require a lateral swinging movement of the PTO shaft and an adequate clearance for such motion. Nevertheless, whenever the tie rod mounting plates 25 are mounted on the outboardmost set of mounting bosses 19, the adjustment mechanism 45 should be manipulated to limit the amount of permissible rolling oscillation by the front axle 12 to a point below which the tie rod ball joints 23 would be damaged. An alternative configuration of the pivots 32, 34 and 38 is shown in Figure 7. The rearward pivot 38 is replaced by a thrust bearing 58 aligned with the oscillation axis 41 passing through the upper spherical pivot joint 32. The lower pivot joint 34 is replaced with a sleeve bearing 54 aligned with the steering axis 31 which also passes through the upper spherical pivot joint 32. Since the support link 35 is normally in tension while maintaining the longitudinal spacing of the lower pivot 34, 54 relative to the rearward pivot 38, 58, and since the support link 35 may not always be perpendicular to the steering axis 31, the sleeve bearings 54, 58 must be capable of resisting thrust. The lateral swinging movement of the lower pivot 34, 54 about the oscillation axis 41 is accommodated by the thrust bearing 58 and the spherical pivot joint 32. Likewise, the corresponding lateral swinging of the steering axis 31 will always have the sleeve bearing 54 aligned with the spherical pivot joint 32 to permit the front axle 12 to pivotally move about the steering axis 31.

Claims: A vehicle comprising: a chassis (10); a generally transversely extending steering axle (12) pivotally supported from said chassis (10) for pivotal movement relative thereto about a steering axis (31), said steering axle (12) including mounting means (52) for connecting a front-mounted implement (I) thereto for pivotal movement therewith about said steering axis (31); a pair of steerable wheels (13) pivotally connected to the opposing transverse ends of said steering axle (12); steering means (20) operably connected with said steerable wheels (13) for selectively controlling the pivotal movement of said steerable wheels (13) relative to said steering axle (12) and for effecting relative pivotal movement between said axle (12) and said chassis (10); and an engine (E) supported on said chassis (10) to provide a source of operative power for said vehicle; and characterized in that : said steering axle (12) extends forwardly from said steering axis (31) in a cantilevered manner underneath a front chassis member (17); and the vehicle further comprises a power-takeoff shaft (50) extending forwardly from said engine (E) and being adapted for connection to the front-mounted implement (I) to transfer operative power thereto from said engine (E), said power-takeoff shaft (50) passing between said front chassis member (17) and said steering axle (12) forwardly of said steering axis (31) and being operable to move in unison with the pivotal movement of said front-mounted implement (I) about said steering axis (31). A vehicle according to claim 1 characterized in that said front chassis member (17) has an opening (18) formed therein, said power-takeoff shaft (50) passing through said opening (18) for connection to said front-mounted implement (I). A vehicle according to claim 2 characterized in that the opening (18) in said front chassis member (10) has a sufficient transverse width to permit a lateral swinging movement of said power-takeoff shaft (50) in response to the associated pivotal movement of said front-mounted implement (I) about said steering axis (31). A vehicle according to claims 2 and 3 characterized in that said power-takeoff shaft (50) passes between said front chassis member (17) and said steerable axle (12) forwardly of the opening (18) in said front chassis member (17). A vehicle according to any of the preceding claims characterized in that said front chassis member (17) is provided with additional means (52) for mounting said front-mounted implement (I) as an alternative to said means (52) for mounting on said steering axle (12) so that said front-mounted implement (I) can be mounted on said vehicle without requiring pivotal movement thereof with said steering axle (12) about said steering axis (31). A vehicle according to any of the preceding claims characterized in that said steering means (20) effects a pivotal movement of said steering axle (12) in response to the pivotal movement of said steerable wheels (13) relative to said steering axis (31). A vehicle according to claim 3 and any claim appended thereto characterized in that said steering means (20) comprise a pair of tie rods (21) interconnecting said steerable wheels (13) and said front chassis member (17); said pair of tie rods (21) being connected at laterally outboard positions of said front chassis member in order not to interfere with said lateral swinging movement of said power-takeoff shaft (50). A vehicle according to claim 6 characterized in that the respective pivotal movements of said steerable wheels (13) and said steering axle (12) occur substantially simultaneously.

Inventors: HURLBURT JOSEPH C, LAVECCHIA GUIDO A, RONDELLI ANGELO, HURLBURT, JOSEPH C., LAVECCHIA, GUIDO A., RONDELLI, ANGELO
Applicants: NEW HOLLAND ITALIA SPA, NEW HOLLAND ITALIA S.P.A.
Application year: 1995
Main classification: B62D7
IPC codes: A01B71, B62D7, B62D9