Patent Publication Number: US-2013240223-A1

Title: Folding agricultural tool carrier having compact storage position

Description:
FIELD 
     The present disclosure relates to a folding carrier for supporting agricultural tools. 
     SUMMARY 
     The carrier includes a boom support frame pivotally connected to a carrier frame for pivoting about a fore-and-aft frame axis between a working position outwardly of the carrier frame and a narrow inwardly directed storage position above the carrier frame. An elongated tool support boom or wing beam is connected by reinforced hinge structure to the boom support frame for pivoting about a boom axis which is upright when the boom support frame is in the working position in the field. An activator connected to the boom support frame and to the tool support boom pivots the boom outwardly about the boom axis towards an extended position when the boom support frame is in the working position and inwardly from the extended position to a fore-and-aft flat-folded position adjacent the carrier frame. The boom support frame with the folded boom pivots upwardly above the carrier frame to lift the boom and supported tools upwardly and inwardly over the carrier frame. 
     The support frame may be constructed to extend along all or a substantial portion of the side of the carrier frame to provide a sturdy support with spaced hinges and facilitate mounting and pivoting of a diagonal boom brace. In one embodiment, an articulated diagonal brace may be provided between the boom and the boom support frame which collapses compactly into itself between the boom and support frame prior to the upward pivoting of the boom and support frame. Use of an elongated support frame permits the brace to be conveniently rotated with the boom support frame and boom upwardly into the storage position without need for cumbersome linkages or complicated joints or the disconnection of components. The diagonal brace may also be used to provide increased torque resistance to the boom or wing beam and may include hinge structure that reduces the stress on the brace as the boom flexes and twists relative to the boom support frame. 
     In a possible embodiment, the boom support frame includes an offset defining with the side of the carrier frame a fore-and-aft extending wheel structure accommodation space receiving wheel structure such as tracks, belts, multiple wheels or any other suitable ground support structure. The accommodation space has dimensions larger than the envelope of the wheel structures and accommodates different sizes and types of the wheels, tracks, and tires. The space facilitates adjustments of the wheel or track tread and provides more convenient access to the wheel structure and to adjacent areas. 
     The boom or wing axis may be located adjacent the wheel structure at the innermost end of the tool support boom. Reinforced hinge structure may include torque-resisting plates receiving the innermost end of the tool support boom and sandwiching the end between the plates. Additional boom torque resistance may be provided by extending a torque tube through the beam and securing the torque tube to the innermost and outermost ends of the boom. The innermost end of the tube may be secured within the reinforced hinge. 
     To reduce overall width in the folded position of the boom, the boom pivot may be offset in a direction of travel from an aft end of the carrier, and the activator may comprise a hydraulic cylinder connected at a cylinder end to the boom support frame. In this configuration, the cylinder may be extended to rotate the tool support boom towards the folded position and assume a flat-fold position approaching a parallel condition with the boom for compactness. The above-described flat-fold arrangement of the activator and boom also tends to distribute more of the weight of the booms and mounted tools forwardly on the carrier frame and helps balance the weight distribution more evenly, which is particularly useful when a rear mounted toolbar with rearwardly projecting tools is connected to the aft end of the carrier frame. Wheel scuffing when the carrier is turned from the forward direction may be reduced by positioning the boom pivot adjacent the wheel structure. 
     In another possible configuration, boom support wheels may support the boom above the ground in the extended position and may include a wheel axis located adjacent the fore-and-aft frame axis when the tool support beam is in the folded position. In this configuration, the wheels may be lifted upwardly with pivoting of the boom support frame towards the storage position, and the close proximity of the frame and wheel axes provides improved mechanical advantage and weight distribution for reducing component stresses and the force required for the pivoting of the boom support frame. The axis of the boom support wheels may lie close to or in a plane that passes through the boom pivot to reduce scuffing when the boom is pivoted towards the transport position. 
    
    
     
       DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a front perspective view of a tracked implement carrier in a partially folded condition. 
         FIG. 2  is a top view of an implement carrier in the partially folded condition similar to the carrier in  FIG. 1 , but having ground wheels rather than tracks. 
         FIG. 3  is an enlarged front perspective view of a portion of the carrier of  FIG. 1  showing a boom support frame and tool support boom approaching a fully folded position and illustrating a compact flat-fold transport configuration and an accommodation space provided for wheel structure by the frame structure. 
         FIG. 4  is an enlarged rear perspective view of the tool support boom pivot area of the structure of  FIG. 3  with the boom in the fully folded position to illustrate the flat-fold transport configuration, the compact arrangement of a folding diagonal brace, the torque tube and reinforced pivot area and the extendible fold cylinder connected between an aft end of the boom support frame and the reinforced pivot area. 
         FIG. 5  is a top enlarged perspective view of the pivot area of one side of the implement carrier of  FIG. 1  showing the boom support frame pivoted downwardly to the working position with the fold cylinder retracted so the tool support boom is in the extended position and illustrating the solid torque-resisting configuration of the boom hinge. 
         FIG. 6  is an enlarged front perspective view of the central portion of the diagonal brace in an extended working position and illustrating joint structure for accommodating misalignment between the tool support boom and the boom support frame. 
     
    
    
     DETAILED DESCRIPTION 
     Referring to  FIGS. 1 and 2 , therein is shown an agricultural implement carrier  10  including a fore-and-aft extending and generally rectangular central carrier frame  12 . The frame  12  has opposite sides  12   a  and  12   b  and forward and aft ends  12   c  and  12   d . The frame  12  is supported by wheel structures  14  at rearward locations adjacent the sides  12   a  and  12   b . The wheel structures  14  may be of any suitable configuration, including but not necessarily limited to tracks ( FIG. 1 ), tandem wheels, and walking-beam supported wheels ( FIG. 2 ) or other offset types of wheels, and may be transversely adjustable to vary tread. Hitch structure  16  ( FIG. 2 ) adapted for connection to a towing vehicle (not shown) is supported at the forward end  12   c  of the carrier frame  12  for moving the carrier  10  in a working direction F. 
     Boom support frames  20  and  22  are pivotally connected to the carrier frame sides  12   a  and  12   b  for pivoting about corresponding fore-and-aft frame axes  20   a  and  22   a . The frames  20  and  22  support right- and left-hand (as viewed in the working direction F) pivoting wing frame assemblies  24   a  and  24   b , respectively. In  FIGS. 1 and 2 , the left-hand wing frame assembly  24   b  is shown in the fully extended field-working position, and the right-hand wing frame  24   a  is shown in a folded position adjacent the side  12   a.    
     Fore-and-aft spaced frame cylinders  26   a ,  26   b  and  26   c  ( FIGS. 2 and 3 ) are connected between the carrier frame  12  and the boom support frame  20  for pivoting the frame  20  about a frame axis  20   a  between a working position outwardly of the carrier frame as shown in  FIG. 5  and an upwardly and inwardly directed storage position above the carrier frame  12  and the wheel structure  14  ( FIG. 3 ). Similarly, frame cylinders  28   a ,  28   b  and  28   c  are connected between the carrier frame  12  and the boom support frame  22  for pivoting the frame  22  about a frame axis  22   a.    
     As shown, rearwardmost cylinders  26   b ,  26   c  and  28   b ,  28   c  are located at opposite ends of wheel structure accommodation spaces indicated generally at  30  and  32 , respectively, and the forward cylinders  26   a ,  28   a  are supported near a forwardmost extremity of the carrier frame  12 . Reinforced hinge structures  36   a ,  36   b  and  36   c  connected to the carrier frame side  12   a  and to the boom support frame  20  define the frame axis  20   a  about which the boom frame  20  rotates and include slotted plates  37  ( FIG. 3 ) with slots  40  receiving the respective rod ends of the cylinders  26   a ,  26   b  and  26   c . The slots allow some pivoting of the boom support frame  20  independently of cylinder action when the cylinders  26   a ,  26   b  and  26   c  are fully extended in the field so that the implement can flex. A similarly constructed and operated set of hinge structures  38   a ,  38   b  and  38   c  are connected to the opposite frame side  12   b  to define the opposite frame axis  22   a  about which the boom support frame  22  pivots. 
     Each of the accommodation spaces  30  and  32  generally is located above the corresponding wheel structure  14  and extends beyond the extremities of the wheel structure to accommodate different sizes, types and positional adjustments of the wheel structure within the space. Also, if desired, the carrier frame  12  may be raised or lowered on the wheel structure  14 , and the accommodation spaces  30  and  32  eliminate interference between the frame and the wheel structure during such vertical adjustments. 
     To establish the spaces  30  and  32 , U-shaped offsets are located in the sides  12   a  and  12   b  of the carrier frame between the respective rear and center hinge pairs  36   c ,  36   b  and  38   c ,  38   b . As best seen in  FIGS. 1-3 , the corresponding boom support frames  20  and  22  include mating offsets opening towards the offsets in the sides  12   a  and  12   b . Extending the frame cylinders  26   a - 26   c  and  28   a - 28   c  rotates the boom support frames  20  and  22  downwardly and outwardly from the storage position ( FIG. 3 ) to the working position ( FIGS. 1 and 2 ), and the mating offsets define the spaces  30  and  32  which are generally open above the entire envelopes of the wheel structures  14 . In the storage positions, all or a substantial portion of the boom support frames  20  and  22  may be located inwardly of the outermost extremities of the wheel structures  14  for narrow transport and more central weight distribution, and the offsets in the boom support frames  20  and  22  provide additional vertical clearance for transport and access to areas around the wheels or tracks. 
     The boom support frames  20  and  22  may be constructed as shown in  FIGS. 1 and 2  to extend along all or a substantial portion of the sides  12   a  and  12   b  of the carrier frame and provide a sturdy support with hinges ( 36   a - 36   c  and  38   a - 38   c ) spaced along the length. In addition, the elongated support frames  20  and  22  facilitate mounting the forward ends of diagonal boom braces, described in detail below, directly on the support frames so the entire wing frames  24   a  and  24   b  with braces may pivot with the support frames  20  and  22  to the transport position. For implements having a different working width than shown in the figures, the number of hinges and length of the boom support frames may be changed accordingly. 
     The right- and left-hand wing frame assemblies  24   a  and  24   b  are generally mirror images of each other and identical in construction and therefore only one will be described in full detail below. Each includes an elongated boom  44  fabricated from a tubular member of rectangular cross section. The boom  44  includes an inner end  46  sandwiched between plates  48  of hinge structure  50  ( FIGS. 4 and 5 ). An edge-reinforced, saddle shaped bracket structure  52  is attached to opposite sides of an aft portion of a fore-and-aft extending beam  54  forming a part of the boom support frame ( 20  of  FIGS. 4 and 5 ). As shown in  FIG. 4 , the beam  54  is fabricated from a pair of tubular frame members to increase the strength and rigidity of the boom support frame  20  for a given beam cross-section. The bracket structure  52  forms the mating portion of the hinge structure  50  and includes opposed planar surfaces  56  which receive the plates  48  and the inner end  46  therebetween. A pivot pin  60  extends through a reinforced journal area  62  in the bracket structure  52  and through the plates  48  and journal area  62  and defines a boom pivot  60   a  which assumes a substantially vertical attitude in the field-working position of the boom  44 . 
     As best seen in  FIGS. 3 and 4 , a torque tube  64  extends through the boom  44  and is secured to the end  46  and to the plates  48  by a hinge end member  66  welded between the plates  48 . The end member  66  includes cylinder rod accommodation notch  68 . A cylinder bracket  70  is fixed to the aft end of the beam  54  and to the rear hinge structure  36   c  of the boom support frame  20 . A boom fold cylinder  74  includes a cylinder end connected to the bracket  70  by a pivot pin  76 . A pivot pin  78  connects the rod end of the cylinder  74  to the plates  48  at a pivot location radially outwardly of the hinge pin  60  and the boom end  46 . The bracket structure  52  and the plates  48  are elongated and extend radially from the pin  60  so that in the field-working position of the boom  44  ( FIG. 5 ) an extended aft portion of the plates  48  are sandwiched between the an extended aft portion of the saddle shaped bracket structure  52 . In addition, the area of the connection of the end  64   a  of the torque tube  64  to the hinge structure  50  is closely contained within the opposed planar surfaces  56  of the bracket structure  52 . The secure connection of the boom end  46  and the torque tube end  64   a  within the plates  48 , and the sandwiching of the offset portion of the plates  48  in the bracket structure  52  provide a strong boom hinge joint that resists overloads on the pivot pin  60  and journal area  62  as extremely large torsional forces are exerted on the boom  44  while operating in the field. 
     After the boom support frame  20  is rotated downwardly and outwardly from the position shown in  FIG. 3  to the position shown in  FIG. 4  by extending the cylinders  26   a - 26   c , the cylinder  74  may be retracted to rotate the boom  44  outwardly to the transverse position shown in  FIG. 5 . Extending the cylinder  74  returns the boom  44  to the folded position shown in  FIG. 4 , whereupon the cylinders  26   a - 26   c  may be retracted to pivot the boom upwardly and inwardly over the carrier frame  12  ( FIG. 3 ). 
     To provide positional support for the boom  44  in the unfolded field-working position, a collapsible diagonal brace  80  is connected at a trailing end to an outer end portion  82  of the boom  44  by a boom brace bracket  84  and at a forward end to the forward end of the corresponding boom support frame  20  or  22  by a pivot or ball joint connection  86 . The central portion of the brace  80  includes a brace hinge  88  that allows the brace  80  to fold and collapse within itself between the beam  44  and the boom support frame beam  54  ( FIG. 4 ) for a compact, closely aligned folded package. When the boom  44  is unfolded towards the field-working position, the brace  80  automatically unfolds to the position shown in  FIGS. 1 and 2  for supporting the boom  44 . To prevent the brace  80  from collapsing when the carrier  10  is backed up and tension is removed from the brace, an actuatable brace lock  90  is connected between the brace  80  and the boom  44 . Although shown as a cylinder, the brace lock  90  may be a mechanical linkage or any other suitable device for preventing pivoting of the brace  80  relative to the boom  44  when tension is removed from the brace other than during folding. 
     The diagonal brace  80  may be constructed to additionally reduce torquing of the boom  44  and reduce stresses in brace hinge  88 . For example, as shown in  FIGS. 1 ,  2   4  and  6 , the brace  80  includes stacked central brace links  92  and  94  connected by a pivot  96  to lower and upper links  102  and  104 . The aft ends of the links  102  and  104  are connected to pivot brackets  84   a  and  84   b , respectively, located above and below the boom  44  as seen in  FIG. 1 . The brace  80  therefore acts as a long lever on the boom  44  acting through a relatively large moment arm to help resist twisting of the boom. To help relieve excessive forces in the brace hinge  88  when the boom  44  moves or twists relative to the boom support frame  20  or  22 , the brace hinge  88  may be provided with one or more additional degrees of freedom. One possible embodiment to provide such freedom is shown best in  FIG. 6  and includes a generally horizontal pivot (horizontal in the working position of the boom  44 )  106  connecting the lower link  102  to the bottom of the pivot  96  and a resilient mount structure  108  connecting the upper link  104  to the upper end of the pivot  96 . Other types of connections at various locations on the brace  80  may also be used to provide the desired freedom of motion to allow limited movement of the links  92 ,  94  and  102 ,  104  away from a parallel aligned relationship that is normally assumed by the links when the boom frame and boom are in alignment with each other. 
     When the boom  44  is to be moved from the unfolded working position, the brace lock  90  is first released and the cylinder  74  is extended to pivot the boom  44  forwardly about the upright pivotal axis  60   a  of the pin  60 . The pairs of links  92 ,  94  and  102 ,  104  collapse into each other about the pivot  96  ( FIG. 4 ) with the links  92 ,  94  aligning in parallel relationship with the links  102 ,  104 . As can be appreciated best from  FIGS. 3 and 4 , the above-described configuration provides a closely stacked compact arrangement including the boom  44 , the fold cylinder  74 , the brace  88  and the boom frame beam  54 . 
     A rear transversely extending toolbar  110  having a width approximately equal to the width of the frame  12  may be mounted on the aft end  12   d  of the carrier frame  12 . Lift cylinders  112  move the rear toolbar  110  vertically relative to the aft end  12   d  to adjust the height of the toolbar. 
     One or more vertically adjustable ground wheel assemblies  114  may be mounted on each of the outer end portions  82  of the booms  44 . The wheel assemblies  114  as shown in  FIGS. 1 and 2  extend downwardly and forwardly from the boom  44  and include a wheel axis indicated generally at  114   a . As illustrated in  FIG. 2  on the unfolded assembly  24   b , the wheel axis  114   a  may lie along or near an upright plane that passes through the boom pivot pin  60  and through the wheel assemblies  14  to reduce tire scuffing when the boom  44  is folded about the boom pivot  60   a  and when the carrier  10  is turned from the forward direction with the boom  44  extended. 
     When the boom  44  is rotated to the folded position alongside the boom support frame  20  or  22 , the axis  114   a  may be closely adjacent the corresponding boom support frame axis (see, for example, axis  20   a  in  FIGS. 1 and 2 ). If such an axis location is used with the wheel axis  114   a  lying close to and generally parallel to the boom support frame axis  20   a , the moment arm through which the frame  20  has to operate to move the wheel assemblies  114  upwardly towards the transport position is reduced so that the force required to move the wing frame assembly  24   a  to the transport or storage position over the frame  12  is reduced compared to assemblies wherein the wheels are offset a greater distance from the pivotal axis. 
     To help stabilize the boom  44  in the folded position ( FIG. 3 ) brackets  118  may be connected to corresponding boom support frame  20  or  22  to funnel the boom  44  into position and cradle it during transport. The diagonal brace  80  may include similar brackets to stabilize the linkages in the folded position such as are shown adjacent the boom brace bracket  84  and the connection  86  in  FIG. 2 . 
     The boom support frames  20  and  22  may be pivoted to an over-center position over the carrier frame  12  for further transport stability of the wing frame assemblies  24   a  and  24   b . Hoppers  120  for containing soil and plant treatments, fertilizer, seeds or the like may be carried on the frame  12  at locations inwardly of the stored wing frame assemblies  24   a  and  24   b . The material in the hoppers  120  may be distributed to the ground by tools  122  and  124  ( FIG. 1 ) extending rearwardly from the rear toolbar  110  and the booms  44 . The tools  124  typically are rotated upwardly and inwardly over the frame  12  with the booms  44  as the boom support frames  20  and  22  are pivoted to their storage positions. 
     While various embodiments of the carrier structure have been specifically described above it is to be understood that many changes and variations will be possible by those skilled in the art and various modifications can be made without departing from the scope of the invention as defined in the accompanying claims.