Patent Publication Number: US-10321629-B2

Title: Agricultural header with ground engaging gauge member for above ground cutting

Description:
FIELD OF THE INVENTION 
     The present invention relates to an agricultural header for cutting a standing crop where the header includes ground engaging gauge members in the form of skids or wheels for supporting the cutter bar at a position spaced from the ground. 
     BACKGROUND 
     U.S. Pat. No. 6,675,568 by Patterson et al discloses and U.S. Pat. No. 8,245,489 by Talbot discloses a height control arrangement using gauge wheels supported at opposing ends of a rigid header. The gauge wheels serve to minimize any substantial deviations from a central controlled height of the header at the outboard ends of the header, however the system is only effective when used on a rigid header or a flexible header which is kept rigid. Published Application 2018/0183461 published Jun. 30, 2016 by Neudorf discloses a gauge wheel system for attachment to a harvesting header. The disclosures of the above documents are all incorporated herein by reference. 
     SUMMARY OF THE INVENTION 
     According to one aspect of the invention there is provided a crop harvesting header comprising: 
     a main frame structure extending across a width of the header for movement in a forward direction generally at right angles to the width across ground including a crop to be harvested; 
     a mounting assembly for carrying the main frame structure on a propulsion vehicle; 
     a crop receiving table carried on the main frame structure across the width of the header; 
     a cutter bar across a front of the table arranged to move through the crop in a cutting action and carrying a sickle knife operable for cutting the crop as the header is moved forwardly for depositing the crop onto the table; 
     a crop transport system on the table for moving the cut crop toward a discharge location of the header; 
     a skid element on the main frame structure for engaging the ground so as to receive lifting forces from the ground; 
     the skid element located behind the cutter bar and extending along the length of the cutter bar so that the cutter bar is supported adjacent the ground for cutting crop close to the ground as the skid element slides over the ground; 
     the harvesting header being operable in a first mode of operation with the skid element engaging the ground and the cutter bar adjacent the ground and in a second mode of operation with the skid element and the cutter bar raised away from the ground; 
     and at least one ground engaging gauge member having a surface arrangement engaging the ground at a position rearwardly of the cutter bar and in the second mode of operation maintaining the cutter bar supported away from the ground; 
     the ground engaging member being carried on a mounting assembly comprising an elongate support member connected at a forward end adjacent to and rearwardly of the cutter bar for pivotal movement about an axis parallel to the cutter bar and extending rearwardly therefrom; 
     the elongate support member being arranged to be raised and lowered to raise and lower the surface arrangement; 
     wherein the surface arrangement comprises a skid surface which extends effectively as a continuous slide surface which slides over the ground from a front edge at a position adjacent the cutter bar to a position at least adjacent to the rear edge of the table. 
     Preferably the skid surface is arched both longitudinally and transversely. 
     According to a further aspect of the invention there is provided a crop harvesting header comprising: 
     a main frame structure extending across a width of the header for movement in a forward direction generally at right angles to the width across ground including a crop to be harvested; 
     a mounting assembly for carrying the main frame structure on a propulsion vehicle; 
     a crop receiving table carried on the main frame structure across the width of the header: 
     a cutter bar across a front of the table arranged to move through the crop in a cutting action and carrying a sickle knife operable for cutting the crop as the header is moved forwardly for depositing the crop onto the table; 
     a crop transport system on the table for moving the cut crop toward a discharge location of the header; 
     a skid element on the main frame structure for engaging the ground so as to receive lifting forces from the ground; 
     the skid element located behind the cutter bar and extending along the length of the cutter bar so that the cutter bar is supported adjacent the ground for cutting crop close to the ground as the skid element slides over the ground; 
     the harvesting header being operable in a first mode of operation with the skid element engaging the ground and the cutter bar adjacent the ground and in a second mode of operation with the skid element and the cutter bar raised away from the ground; 
     and at least one ground engaging gauge member having an engagement surface arrangement to engage the ground at a position rearwardly of the cutter bar and in the second mode of operation maintaining the cutter bar supported away from the ground; 
     the ground engaging member being carried on a mounting assembly comprising an elongate support member connected at a forward end adjacent to and rearwardly of the cutter bar for pivotal movement about an axis parallel to the cutter bar and extending rearwardly therefrom: 
     the elongate support member being arranged to be raised and lowered to raise and lower the surface; 
     wherein the engagement surface arrangement comprises:
         a skid surface carried on the elongate support member which extends effectively as a continuous slide surface which slides over the ground extending from a front edge at a position adjacent the cutter bar to a rear surface;   and at least one ground engaging wheel arrangement carried on the elongate support member.       

     Preferably the wheel arrangement is removable to allow the skid surface to slide on the ground. That is the system can be used with a skid in muddy or heavy conditions or with a wheel for better movement over the ground when the wheels do not become too mired. 
     Preferably in another important aspect which can be used independently of other features described herein, there is provided a resilient suspension arrangement which provides movement between the ground engaging member, either whether this is a wheel or a skid, and the mounting to the frame of the header. In one embodiment this is provided at the rear of the elongate support member so as to allow the support member to pivot upwardly and downwardly in a resilient suspension movement relative to its pivot at the forward end. Preferably this is provided as a pivotal link at the connection of the member to the adjustment post at the rear of the frame. Alternatively in another embodiment the suspension can be provided between the elongate support member and the wheel arrangement allowing up and down floating movement of the wheel relative to the elongate member. This may counteract tendency for the wheels to dance over the surface causing undesirable motion of the cutter bar. 
     Preferably the ground engaging wheel arrangement comprises a pair of wheels each on a respective side of the skid with transverse axis of rotation across the top of the skid allowing the wheels to rise relative to the skid. 
     According to a further aspect of the invention there is provided a crop harvesting header comprising: 
     a main frame structure extending across a width of the header for movement in a forward direction generally at right angles to the width across ground including a crop to be harvested; 
     a mounting assembly for carrying the main frame structure on a propulsion vehicle; 
     a crop receiving table carried on the main frame structure across the width of the header; 
     a cutter bar across a front of the table arranged to move through the crop in a cutting action and carrying a sickle knife operable for cutting the crop as the header is moved forwardly for depositing the crop onto the table; 
     a crop transport system on the table for moving the cut crop toward a discharge location of the header; 
     a skid element on the main frame structure for engaging the ground so as to receive lifting forces from the ground; 
     the skid element located behind the cutter bar and extending along the length of the cutter bar so that the cutter bar is supported adjacent the ground for cutting crop close to the ground as the skid element slides over the ground; 
     the harvesting header being operable in a first mode of operation with the skid element engaging the ground and the cutter bar adjacent the ground and in a second mode of operation with the skid element and the cutter bar raised away from the ground; 
     and at least one ground engaging gauge member having an engagement surface arrangement engaging the ground at a position rearwardly of the cutter bar and in the second mode of operation maintaining the cutter bar supported away from the ground; 
     the ground engaging member being carried on a mounting assembly comprising an elongate support member connected at a forward end adjacent to and rearwardly of the cutter bar for pivotal movement about an axis parallel to the cutter bar and extending rearwardly therefrom; 
     the elongate support member being arranged to be raised and lowered to raise and lower the surface; 
     wherein the engagement surface arrangement comprises at least one ground wheel mounted on the elongate support member for rotation about an axis parallel to the cutter bar; 
     and wherein there is provided a resident suspension arrangement which provides movement between the ground engaging member and the mounting to the frame of the header. 
     In one embodiment this is provided at the rear of the elongate support member so as to allow the support member to pivot upwardly and downwardly in a resilient suspension movement relative to its pivot at the forward end. Preferably this is provided as a pivotal link at the connection of the member to the adjustment post at the rear of the frame. Alternatively in another embodiment the suspension can be provided between the elongate support member and the wheel arrangement allowing up and down floating movement of the wheel relative to the elongate member. This may counteract tendency for the wheels to dance over the surface causing undesirable motion of the cutter bar. 
     The arrangements defined above are preferably used in a header construction wherein; 
     the main frame structure includes a center frame portion, a first wing frame portion and a second wing frame portion; 
     the first wing frame portion is connected to the center frame portion by a first pivot coupling which provides pivotal movement of the first wing frame portion relative to the center frame portion about a first pivot axis extending in a plane parallel to the forward direction; 
     the first pivot coupling acts to support weight from the first wing frame portion while outboard weight from the first wing frame portion outboard of the first pivot coupling rotates the first wing frame portion about the first pivot coupling in a downward direction; 
     the second wing frame portion is connected to the center frame portion by a second pivot coupling which provides pivotal movement of the second wing frame portion relative to the center frame portion about a second pivot axis extending in a plane parallel to the forward direction; 
     the second pivot coupling acts to support weight from the second wing frame portion while outboard weight from the second wing frame portion outboard of the second pivot coupling rotates the second wing frame portion about the second pivot coupling in a downward direction; 
     the mounting assembly includes a float suspension system connected to the center frame portion providing a variable lifting force from the propulsion vehicle acting to support the main frame structure for floating movement relative to the propulsion vehicle; 
     a first interconnecting float linkage is connected between the center frame portion and the first wing frame portion which communicates a first variable lifting force from the center frame portion to the first wing frame portion against the outboard weight of the first wing frame portion; 
     a second interconnecting linkage is connected between the center frame portion and the second wing frame portion which communicates a second variable lifting force from the center frame portion to the second wing frame portion against the outboard weight of the second wing frame portion; 
     in the first mode of operation with the skid element engaging the ground, the float suspension system and first and second interconnecting linkages provide a downforce from the skid element on the ground which is balanced between the center frame portion and the first and second wing frame portions. 
     However the header can also be of a structure which uses a rigid frame or where the frame is fixed so as to be rigid when used in a particular mode. 
     It is more preferable that the cutting height in the second mode is greater than 14 inches. 
     Preferably in this arrangement the first and second ground engaging members are mounted at respective outer ends of the first and second wing frame portions additional ground engaging members are mounted on the first wing frame portion closely adjacent to the pivot axis and closely adjacent the pivot axis, and the center frame portion is supported only by said float suspension system and not by any additional ground engaging members. 
     Preferably each of the elongate support members extends rearwardly under the table to a rear end rearward of the table and there is provided an upstanding extendible member connected at a lower end to the elongate support member and to the frame structure above the lower end and rearward of the table to raise and lower the cutter bar relative to the ground. 
     Preferably the extendible member comprises a pair of telescopic members with an outer with an inner member slidable within an outer member, wherein the inner member has a plurality of longitudinally spaced holes for receiving a pin of the outer member to locate the inner and outer members at an extension position defined by the selected hole, wherein the holes are spaced transversely of the inner member and the pin is carried on a rotatable member which acts when rotated to move the pin transversely across the outer member so that the transverse position of the pin when rotated acts automatically to select one of the holes of the inner member. 
     Preferably the main frame structure includes a frame beam and a plurality of frame members located at spaced positions across the main frame structure; 
     each frame member extending from the frame beam in a first portion downwardly behind the table and in a second portion forwardly under the table to support the cutter bar; 
     the second portion forming a channel member with a downwardly facing open face: 
     the elongate support members each being located in a second portion of a respective one of said frame members and extending rearwardly under the table. 
     Preferably each of the ground engaging surface arrangements is located under the table. 
     Thus one key feature is that the system mounts a skid or skid and wheel on a long arm which is attached to an upstanding actuator at the rear of the frame. Another key feature relates to the location and arrangement of the skid and wheel in relation to the fact that it is pivoted at the front on a lug at the frame and is carried on a beam which is attached to an upstanding adjustable leg (cylinder or telescope) at the back of the frame. 
     Another key feature relates to the location and arrangement of the skid and/or wheel so that the wheel can be fully retracted to allow the header to operate in the first mode with the cutter bar and skid element on the ground. 
     Another key feature relates to the long skid which extends from the pivot just behind the cutter bar right back to the rear of the table or at the upstanding adjustment post. 
     One system uses four wheel assemblies (one at each end of the header and one adjacent to or more particularly just outside or just inside of the two hinge locations near the center of the header. The wheel assemblies pivot near the cutter bar and have a short skid that is part of the structure that the header rides on when cutting directly on or close to the ground. The adjustment of all four wheel assemblies is done at the rear of the header. 
     The long skid, like the wheel assembly, is located at each end of the header and also near each hinge point for a total of four skids. These skids also pivot at the cutter bar with an adjustment mechanism at the rear of the header. 
     For the height adjustment of the wheel/skids, this can be effected by a mechanical adjustment using a telescoping tube with a series of holes and a pin that can be used to position the wheels or skids to a predetermined height. A second option is the use of hydraulic cylinders that replace the mechanical adjuster and a switch in the combine cab that allows the operator to adjust the wheel height using the combine&#39;s hydraulics. 
     For both the wheels and the skids using either the mechanical or hydraulic adjuster, a maximum out height of approximately 14 to 18 inches can be achieved. In addition, with the wheels or skids being fully retracted while remaining in place on the header, the operator can cut with the cutter bar/skid element touching the ground without ever needing to remove the wheels/skids from the header. 
     The three section frame is designed to cut on the ground and such that the cutter bar pressure is consistent or balanced across the full length of the cutter bar by means of a balance linkage that uses the weight of the header to balance the weight of the wings. This works very well for crops like soybeans, peas, lentils, where it is desirable to cut as close to the ground as possible. In these crops, the cutter bar is skidded along the ground and the flex balance linkage and header float system allow the header to follow contours with minimal pressure between the cutter bar and the ground. Current standard skid shoes provide some cutter bar height adjustment in the order of up to 5 inches. 
     In crops like cereals it is sometimes desirable to cut at a height of up to 14 to 18 inches while following the ground contour. Furthermore, it is desirable to easily go from cutting at this height, and back to cutting on the ground with minimal effort. It is thus desirable for the device that allows for cutting off the ground to stay on the header when cutting on the ground, and for the adjustment to be quick and easy. 
     The device includes contour wheels or long skid shoes. It consists of four separate assemblies located such that the skid shoe or wheel assembly make contact with the ground and cause the header to flex and follow the contour of the ground, much like the header does when cutting on the ground. The locations of the wheels or long skid shoes is such that they provide enough of a moment about the virtual balance points of the flex header to overcome friction and cause the header to flex. This virtual balance point is located on the header wing, approximately one third the distance from the hinge point to the end of the header. 
     There are a total of four wheel assemblies across the width of the header. Two are at each end of the header, and two are near the hinge points. These locations ensures enough moment about the virtual balance point of the header to overcome friction and cause the header to flex. This allows the operator to use the header while in flex mode in order to achieve better ground following while cutting as high as 18 inches off the ground. Ground following was previously only possible while cutting with the cutter bar resting on the ground or else on the short skid shoes for a maximum height of 5 inches. 
     The wheel assemblies can also be used on a header that does not have a flexing frame in that the frame is rigid or the flexing action is locked out. In this case, there may be only two assemblies used and the wheels allow the operator to maintain consistent cut height from pass to pass, however cut height variation can still occur due to changing ground contours across the width of the header. 
     The wheel assembly contains an isolator or suspension system to aid in eliminating header bounce and stress on components as the wheels travel over bumps and other incompressible objects. One embodiment of the isolator consists of a torsional rubber isolator which is mounted to the elongate support member that spans from the cutter bar to the rear adjuster. In this case, the wheel assembly contains two links bolted to the torsional isolator. As the wheel strikes an object, the links convert the force into a moment which causes the isolator to rotate and absorb the load. Other means of providing shock absorption such as a rubber block, or spring and shock absorber or accumulator can be used. 
     The means of adjusting the height of the wheel assembly can be a manual adjuster or a hydraulic wheel height adjustment system. With the manual adjuster, the operator sets all four adjusters to a height which is close to the desired cut height and fine adjustments can then be made to the cut height by changing the tilt of the header using the tilt cylinder that attaches the header to the adapter. With the hydraulic adjustment which contains four hydraulic cylinders in a series circuit in a master slave arrangement, and a switch in the combine cab, the operator can adjust the height of the wheels by actuating the cylinders using the in cab switch while harvesting and can adjust the tilt to obtain an increase in the height using the same switch. 
     One embodiment of the manual adjuster includes two telescoping tubes with a pin adjustment system to lock the position. In one embodiment, the outer tube utilizes a series of holes in a circular pattern with each of the holes aligning with one of the holes on the inner tube. This arrangement allows the user to select the height of the adjuster by pulling the pin and rotating the pin holder to the desired setting after which the inner tube can either be extended or retracted until the pin engages in the hole on the inner tube. 
     Where the ground engaging member comprises a long skid shoe, this comprises a skid member positioned such that the header rides on the shoes when in cutting position. The operator may choose to retract the shoes such that the header can cut on the ground, effectively removing the long skid shoes from operation. This enables the operator to adjust cut height such that a desired stubble length can be achieved. The embodiment shown allows for a stubble height ranging from 1.25 inch up to 14 inches. This allows a flexible or rigid header to maintain a consistent cutter bar to ground spacing. In the case of a rigid header, cut height can still vary due to uneven ground across the full width of the header. The skid may use metal, poly, or other desirable material as the ground contacting surface. This surface may be either permanent or replaceable. The means of adjusting the cut height is the same as described above with the contour wheels by means of a manual or automatic method, either using hydraulic or electric components. The long shoe may either be integrated into standard short skid shoes near the front of the header, or exist in addition to short standard skid shoes. 
     In another embodiment the device can comprise the long skid shoe, with the addition of a ground-contacting wheel or wheels mounted on each side of the skid. 
     The wheels can be permanently attached to the skid shoe, removable, or retractable as desired. The wheels may be supported in a variety of ways, including but not limited to a rotational damping arm. The wheel may consist of a variety of materials, including a solid material or a pneumatic wheel. The wheel may be fixed position or include an adjustable member such that the wheel&#39;s position in proximity to the shoe may be altered. The wheel may be used to increase the stubble height beyond the range of the shoe. In this embodiment, 18 inches can be achieved using the wheels. The wheel offers all of the benefits of the skid shoe, while increasing the life of the device in abrasive conditions, as well as reducing friction and increasing cut height. 
     Various embodiments of the invention will now be described in conjunction with the accompanying drawings in which: 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a rear elevational view of a prior art multi-section header. 
         FIG. 2  is a top plan view of the prior art multi-section header according to  FIG. 1 . 
         FIG. 3  is an end elevational view of the multi-section header according to  FIG. 1 . 
         FIG. 4  is a schematic representation of the balancing linkage of the multi-section header according to  FIG. 1 . 
         FIG. 5  is a schematic elevational view of the balancing linkage in relation to the suspension system supporting the header according to  FIG. 1  on the feeder house of a combine harvester. 
         FIG. 6  is a isometric view of one gauge wheel assembly for use in the harvesting header of  FIGS. 1 to 5  according to the invention. 
         FIG. 7  is a side elevational view of the gauge wheel assembly of  FIG. 6  located on a cross-sectional view of the header of  FIGS. 1 to 5  showing the gauge wheel in the retracted position with the cutter bar in the ground position of the first mode. 
         FIG. 8  is a side elevational view of the gauge wheel assembly of  FIG. 6  located on a cross-sectional view of the header of  FIGS. 1 to 5  showing the gauge wheel in the extended position with the cutter bar in the maximum raised position of the second mode. 
         FIG. 9  is an enlarged view of the wheels and suspension of the embodiment of  FIGS. 6 to 8 . 
         FIG. 10  is an enlarged view of the extendible post of the embodiment of  FIGS. 6 to 8 . 
         FIG. 11  is a further enlarged view of the extendible post of the embodiment of  FIGS. 6 to 8 . 
         FIG. 12  is a isometric view of a second embodiment of one gauge wheel assembly for use in the harvesting header of  FIGS. 1 to 5  according to the invention where the resilient suspension arrangement is located at the rear. 
         FIG. 13  is a cross-sectional view along the lines  13 - 13  of the embodiment of  FIG. 12 . 
         FIG. 14  is a cross-sectional view along the lines  14 - 14  of the embodiment of  FIG. 12 . 
     
    
    
     In the drawings like characters of reference indicate corresponding parts in the different figures. 
     DETAILED DESCRIPTION 
     Referring to the accompanying figures, there is illustrated a gauge system generally indicated by reference numeral  5 . The gauge system is particularly suited for use with an agricultural header  10  manufactured by Macdon Industries Ltd. under the model number FD70/FD75/FD1/FD2. U.S. Pat. No. 6,675,568 by Patterson et al, the disclosure of which is incorporated herein by reference discloses the general operation of the header. For convenience, FIGS. 1 through 3 from U.S. Pat. No. 6,675,568 are attached herewith and some of the description with regard to operation of the header from U.S. Pat. No. 6,675,568 is reproduced in the following. 
       FIGS. 1 and 2  show in rear elevational view and in plan view respectively the header  10  carried on an adapter  11  attached to the feeder house  12  of a combine harvester. In  FIG. 1  the adapter is omitted for convenience of illustration. 
     The header  10  includes a frame  13  defined by a main rear beam  14  and a plurality of forwardly extending arms  15  which extend downwardly from the beam  14  and then forwardly underneath a table  16  which extends across the header. At the forward end of the table  16  is provided a cutter bar  17 . On top of the table  16  is provided a draper transport system  18  which carries the crop from the cutter bar across the header to a discharge location at the feeder house  12 . The draper thus include two side drapers extending from respective ends of the header inwardly toward the feeder house and a center adapter section  18 B which acts to feed the crop from the side drapers  18 A rearwardly to the feeder housing. 
     Reference is made to prior application Ser. No. 09/810,425 filed Mar. 19, 2001 and to application Ser. No. 09/965,119 filed Sep. 28, 2001 which disclose details of the adapter and its inter relation to the side drapers  18 A, the disclosure of which is incorporated herein by reference. 
     The header further includes a reel  19  including a beam  19 A on which is mounted a plurality of reel bats (not shown) which are carried on the beam  19 A for rotation with the beam around the axis of the beam. The beam is carried on reel support arms  19 B which extend from the beam rearwardly and upwardly to a support bracket attached to the transverse main beam  14 . The reel arms can be raised and lowered by hydraulic cylinders  19 D connected between the respective arm and the beam  14 . 
     In the embodiment shown the reel is mounted on three arms  19 B including two arms at the ends of the header and a single center arm. However additional arms may be provided so that there are four such arms with two center arms being spaced apart either side of the adapter  11 . It is well known to provide an arrangement of the beam  19 A and the bats which accommodate flexing movement of the reel so that one end can be higher than the other end without damaging the bats or the reel structure. Various different arrangements for accommodating such flexing movement are known and can be incorporated into the arrangement described herein, as is well known to one skilled in the art. 
     The adapter  11  provides a center support for the header at a center frame portion  10 A and comprises a frame  20  which attaches to the feeder house  12  and carries at its lower end a pair of forwardly extending pivotal arms  21  which extend forwardly underneath respective ones of the frame members  15  of the header. The pivotal arms  21  can pivot upwardly and downwardly about a respective pivot pins  23  each independently of the other arm. Each arm is supported by a respective spring  24  carried on a respective stub arm  25  attached to the respective arm  21 . Thus the spring  24  provides tension on the stub arm  25  pulling it upwardly around the pin  23  which acts to pull up the respective arm  21  and provide a lifting force underneath the header at a lifting point partway along the respective frame member  15  and underneath the draper  18  and the table  16 . 
     At the center of the adapter is provided a link  26  which extends from the frame  20  forwardly to the central bracket  19 C of the beam arm support brackets. The link  26  is provided in the form of a hydraulic tilt cylinder which allows adjustment of the length of the cylinder thus pivoting the header forwardly and rearwardly about the support point of the arms  21  on the underside of the header. Thus the attitude of the header, that is the angle of the table  16  to the horizontal can be tilted by operation of the cylinder forming the link  26 . 
     In addition the attitude of the header about an axis extending forwardly of the direction of movement that is at right angles to the transverse beam  14  is effected by the independent pivotal movement of the arms  21  provided by the springs  24  which act as a floatation system. In addition the whole header can float upwardly and downwardly on the springs  24  with the link  26  pivoting to accommodate the upward and downward movement and the arms  21  pivoting about the respective pin  23 . 
     The table  16  provides behind the cutter bar  17  a skid plate  16 A typically including a polymeric wear shield which is arranged to engage the ground. Thus upward force is provided from the ground which tends to lift the header taking weight off the support springs  24 . In practice the springs are adjusted so that the springs act to support the majority of the weight of the header leaving a relatively small proportion of the weight to rest on the ground. Thus the header can float upwardly and downwardly as the ground provides areas of different height with one end of the header being movable upwardly independently of the other end by independent flexing of the springs  24 . Thus the header tends to follow the ground level. 
     The header is formed in a number of sections which are independently pivotal each relative to the next and in which adjustment of the lifting force provided by the springs  24  is transferred to each of the sections proportionally so that each section can float upwardly and downwardly and each section applies a force to the ground which is proportional to the total force of the whole header. 
     Thus the beam  14  is divided into a number of separate pieces depending upon the number of sections of the header. In the embodiment shown there are three sections including a center frame portion or section  10 A carried on the propulsion vehicle by the adapter or center support  11 , a first wing frame portion or section  10 B and a second wing frame portion or section  10 C. The center section  10 A is mounted at the adapter so that the arms  21  extend into engagement with the center section. The wing sections are pivotally connected to the center section such that each can pivot upwardly and downwardly about a respective pivot axis generally parallel to the direction of movement. 
     Thus the beam  14  is split into three portions each co-operating with a respective one of the sections  10 A,  10 B and  10 C and defining a main beam therefor. Each section of the beam  14  includes respective ones of the frame members  15  which support the respective portion of the table. Thus as best shown in  FIG. 1 , there is a break between the beam sections  14  of the center section  10 A and one wing section  10 B. The end most frame member  15 A of the wing section  10 B is arranged at the break. The end frame member  15 B of the center section  10 A is spaced inwardly from the break leaving space for a pivot coupling  27  extending from the frame member  15 A to the frame member  15 B and defining a pivot pin  27 A lying on the pivot axis between the wing section  10 B and the center section  10 A. In a rear elevational view, the cutter bar  17  is also visible underneath the header at the forward end of the frame members  15  and at the front of the table  16 . 
     In the embodiment shown the cutter bar  17  is split at a junction lying along the axis of a hinge pin so as to provide a pivot within the cutter bar allowing the cutter bar to bend at the junction. 
     In an alternative arrangement (not shown) the cutter bar can be formed in a manner which allows it to flex on the axis of the pin thus avoiding the necessity for a break in the cutter bar. 
     The cutter bar is of conventional shape including a U shaped member with generally horizontal legs and a front curved nose to which is attached the knife support flange of a conventional nature. The knife support flange includes a plurality of holes for mounting conventional knife guards. 
     A bridging link is connected across the break so as to hold the sections of the cutter bar  17  aligned while the pivotal movement occurs. The link comprises a plate welded to one part of the cutter bar with the link or plates spanning the break and extending to a pin which is welded to the other part of the cutter bar with the link being held in place by a nut. 
     Thus the two sections  10 A and  10 B are supported each relative to the other for pivotal movement of the wing section  10 B about an axis extending through the hinge pin and through the break in the cutter bar  17  so that the wing section is supported at its inner end on the center section but can pivot downwardly at its outer end so that the weight at the outboard end is unsupported by the center section and causes downward or counter clockwise pivotal movement of the wing section  10 B. 
     The wing section  10 C is mounted in an identical or symmetrical manner for pivotal movement about the other end of the center section  10 A. The amount of pivotal movement allowed of the wing section relative to the center section about the axis of the pivot pin is maintained at a small angle generally less than 6° and preferably less than 4° as controlled by suitable mechanical stop members which are provided at a suitable location with the required mechanical strength to support the wing frame section against upward or downward movement beyond the stop members. Suitable stop members can be designed by a person skilled in the art and the details of the stop members are not described herein. 
     The outboard weight of the wing section  10 B is supported on an interconnecting linkage  30  which communicates that weight from the inner end of the beam  14  of the section  10 B through to the support for the center section  10 A at the springs  24 . The linkage is shown particularly in  FIGS. 4 and 5  as described in further detail below. 
     In general the linkage operates to transfer the outboard weight of the wing section inwardly to the center section and at the same time to balance the lifting force provided by the springs  24  so that if is proportionally applied to the center section and to the wing section. 
     Thus in general the header is attached to the combine feeder house using the float system described previously that supports the header so that it can be moved up when a vertical force about 1% to 15% of its weight is applied to the cutter bar from the ground. The reaction of the float linkage that typically supports 85% to 99% of the header weight on the header is used to balance the weight of the wings. 
     The system is designed so that if the operator sets the float so that the float system supports 99% of the header weight then the remaining 1% will be evenly distributed across the cutter bar. If the operator changes the float so that 85% is supported by the combine harvester then the remaining 15% would also be evenly distributed across the cutter bar without the operator making adjustments. Thus, not only is the total lifting force to each sections varied in proportion to the total lifting force but also that lifting force on each section is balanced across the width of section. As the sections are rigid between the ends, this requires that the lifting forces be balance between the ends to ensure the even distribution across the cutter bar of each section and thus of all the sections. This provides an arrangement in which the force required to lift the header is the same force at any location along the length of the cutter bar, whether that location is at the center section, at a junction between the center section and the wing section or at the wing section. This is achieved in this embodiment by the balancing system which transfers lifting force between the sections with the forces being balanced by a balance beam of the linkages  30 . 
     The header frame sections and the reel sections are hinged and supported so that the reel will stay in approximately the same position relative to the cutter bar. Thus the balance beam as described in more detail hereinafter balances the lifting force applied to the ends of the center section relative to the lifting force which is applied to the outboard weight of the wing section so that the lifting force is even across the width of the header. Thus if a lifting force is applied by the ground or any other lifting mechanism for example merely manually lifting the header at a particular location across its width, that would cause the header to rise at that point and to fall at other points. The amount of force necessary to lift the header at that point will be the same as it is at other points and this lifting force can be varied for the total header and proportioned across the width of the header automatically by the balance beams as described hereinafter. 
     It will be appreciated that the inboard weight of the wing section is transferred through the pivot  27  to the outboard end of the center section and that weight is transferred directly to the balance beam. Also the outboard weight of the wing section is transferred through the linkages  30 . Yet further a lifting force from the arm  21  is applied to the balance beam. 
     The whole support assembly including the linkages  30 , the lift arm  21  and the springs  24  are arranged to provide a floating movement for each of the first and second frame portions that is the center and wing frame portions relative to each other and relative to the propulsion vehicle such that upward pressure from the ground on the skid element  16 A which is greater in a downward force for a part of the weight of the header and supported by the lifting force tends to lift each of the center and wing frame portions relative to the propulsion vehicle. 
     The balance beam arrangement is arranged such that the first and second lifting forces are varied proportionally as the total lifting force F τ  is varied. 
     The height of the header is primarily controlled by controlling the height of the feeder house  20  of the combine harvester relative to the ground using a height control mechanism  100 . Typically the feeder house is pivotally supported on a main frame of the combine harvester and an actuator member is mounted between the feeder house and the main frame to raise and lower the feeder house. 
     The height of the main structure of the header is in turn supported for up and down movement relative to the adapter  11  by supporting the main frame structure on the pivot arms  21  which are supported for floating movement by the springs  24  by providing a total spring lifting force to the header. The linkages  30  in turn distribute this total spring force into a center lifting force F c  which provides lift to the center frame section and the inboard ends of the wing frame sections pivotally coupled thereto as well as a first lifting force and a second lifting force acting upon the first and second wing frame sections respectively in a direction intending to cause the outboard ends of the wing frames to be raised upwardly. 
     The linkages  30  supporting the main frame structure on the pivot arms  21  comprises two balance linkages associated with the two pivot arms respectively. Each balance linkage includes a balance beam  102  pivotally supported at an intermediate location between front and rear ends on the forward ends of the pivot arms  21 . The forward ends of the two balance beams  102  are pivotally connected to respective locations on the center section of the main frame structure at transversely spaced apart locations. The forward ends of the balance beams  102  serve to provide the center lifting force F c  to the main frame structure. The opposing rear ends of the two balance beams  102  provide the first and second lifting forces to the first and second wing frame sections. 
     More particularly, the rear end of each balance beam  102  is pivotally connected to an upright compression link  104  which extends upwardly from the balance beam  102  below the main frame structure to a top end in proximity to a fop end of the main frame structure. Each balance linkage further includes a bell crank  106  pivotally supported on the main frame structure adjacent the top end in which the bell crank includes a first lever  108  pivotally coupled to the top end of the respective compression link  104  and a second lever portion  110  extending upward to a pivot connection with a respective tension link  112 . 
     Pivotal connection of the second lever  110  with the respective tension link  112  is located substantially directly above the pivotal connection of the bell crank to the main frame structure such that an upward force acting on the compression link  104  tends to rotate the bell crank in a direction corresponding to a laterally inward tension on the tension link  112  which is pivotally coupled at its outer end to a respective one of the wing frame sections which tends to pivot the wing frame section in a direction about its pivotal coupling to the center frame section in a direction corresponding to the outboard and of the wing frame section being raised upwardly. 
     The balance linkages  30  serve to balance the total lifting force provided by the combine harvester through the pivot arms  21  to the center lifting force at the forward ends of the balance beams  102  and the first and second lifting forces at the rear ends of the balance beams so as to vary the lifting forces as the total lifting force varies and so as to balance the lifting forces from the ground applied along the length of the skid element. 
     The header further includes a stop member  114  which is arranged to limit downward movement of the main frame structure of the header relative to the adapter. A distance sensor  116  is provided for sensing a distance of a point on the header which moves with the header in suspension movement relative to the bottom stop  114  which is stationary relative to the combine harvester. The distance sensor therefore generates a signal indicative of the sensed changes in the measured distance. The height control mechanism  100  which is arranged to raise and lower the feeder house of the combine harvester, receives the signal from the sensor  116  as an input and is automatically operated so as to attempt to maintain the sensed distance at a required set value. The set value is selected so that the header is free to float between the bottom stop and the upper limited movement both upwardly and downwardly to accommodate changes in ground height. 
     The gauge system  5  according to the present invention is particularly suited for use with the above described header  10  to permit the header to operate in a balanced manner with the wing sections floating relative to the center section when operating at a raised cutting height with the cutter bar and skid member  16 A supported well above the ground. 
     Thus as shown in  FIGS. 1 to 5  there is provided a crop harvesting header  10  with center and wing sections  10 A,  10 B and  10 C. Each includes a main frame structure so that together the combined frame structure extends across a width of the header. The main frame structure as best shown in  FIGS. 7 and 8  includes a main frame beam  40  across the rear at the top of the header and a plurality of frame members  41  located at spaced positions across the main frame structure. Each frame member  41  extends from the frame beam  40  in a first portion  42  downwardly behind the table  43  and in a second portion  44  forwardly under the table to support the cutter bar  45 . The second portion  43  forms a channel member with a downwardly facing open face  46 . 
     The frame structure is attached to a mounting assembly defined by the adapter  11  of  FIG. 5  for carrying the main frame structure on the feeder house  12  of a propulsion vehicle such as a combine harvester by which the header is transported in movement in a toward direction generally at right angles to the width across ground including a crop to be harvested. 
     The crop cut by the sickle knife  47  of the cutter  45  falls onto the crop receiving table  44  carried on the main frame structure across the width of the header. 
     A skid element  48  on the main frame structure is located just behind the sickle knife of the cutter bar for engaging the ground so as to receive lifting forces from the ground. The skid element  48  is located behind the cutter bar and extends along the length of the cutter bar so that the cutter bar is supported adjacent the ground for cutting crop close to the ground as the skid element  48  slides over the ground. 
     A crop transport system  49  such as a draper system or auger is provided on the table for moving the cut crop toward a discharge location of the header. As described above, the harvesting header is operable in a first mode of operation shown in  FIG. 7  with the skid element  48  engaging the ground and the cutter bar  45  adjacent the ground and in a second mode of operation shown in  FIG. 8  with the skid element  48  and the cutter bar raised away from the ground. 
     As explained previously and shown in  FIG. 4 , the first wing frame portion  10 B is connected to the center frame portion  10 A by a first pivot coupling  102  which provides pivotal movement of the first wing frame portion  10 B relative to the center frame portion  10 A about a first pivot axis extending in a plane parallel to the forward direction. Symmetrically the second wing frame portion  10 C is mounted on the other side if the center section. 
     The first pivot coupling  102  is provided to support weight from the first wing frame portion  10 B while outboard weight from the first wing frame portion  10 B outboard of the first pivot coupling rotates the first wing frame portion  10 B about the first pivot coupling in a downward direction. Symmetrically the second wing frame portion  10 C is mounted on the other side if the center section and supported by a symmetrical coupling. 
     As explained previously, the mounting assembly including a float suspension system  24  connected to the center frame portion providing a variable lifting force from the propulsion vehicle acting to support the main frame structure for floating movement relative to the propulsion vehicle. A first interconnecting float linkage  108  is connected between the center frame portion  10 A and the first wing frame portion  10 B which communicates a first variable lifting force from the center frame portion to the first wing frame portion against the outboard weight of the first wing frame portion. A second symmetrical interconnecting linkage communicates a second variable lifting force from the center frame portion to the second wing frame portion against the outboard weight of the second wing frame portion. 
     In the first mode of operation with the skid element  48  engaging the ground, the float suspension system  24  and first and second interconnecting linkages  108  provide a downforce from the skid element  48  on the ground which is balanced between the center frame portion  10 A and the first and second wing frame portions  10 B,  10 C. 
     As set out hereinbefore, the above arrangements are conventional and further details can be obtained from the referenced patents or from machines well known in the industry and manufactured by MacDon. 
     In accordance with the arrangement described herein, there is provided a gauging system  50  used in the second mode of operation to hold the cutter bar in the raised position of  FIG. 8 . 
     This includes four separate ground engaging members  51  located in the positions shown in  FIG. 1 . This includes a first ground engaging member  51  supported on the first wing frame portion  10 B at a location spaced outwardly from the center frame portion and particularly at the outer end of the portion at the crop divider and end sheet of the header for engaging the ground so as to receive lifting forces from the ground, a second ground engaging member  51  supported on the second wing frame portion  10 C also at the outer end and two additional ground engaging member  51  supported on the wing frame portions immediately proximate the center frame portion  10 A for engaging the ground so as to receive lifting forces from the ground. The two additional members  51  can be located on the center section. The outer members are preferably located at the ends but also can be moved inboard. 
     The location of the four ground engaging elements  51  at the locations specified provides a proper balance of the header relative to the nominal balance points P on the wing frame portions  10 B and  10 C. The points P represent the locations where the three sections will be balanced if supported by members at the points. It will be noted that the actual ground engaging members are located at spaced positions from these points. Thus the outermost member  51  is located at the outer end of the wing and the innermost member  51  is located closely adjacent the pivot coupling. These locations are spaced sufficiently from the points P so that ground forces transmitted to the frame through the members  51  will allow the wings to flex around the pivot points and keep all three sections at a common spacing from the ground. 
     In the embodiment of  FIGS. 6 to 9 , each of the ground engaging members  51  has a surface arrangement defined by the periphery  53  of a pair of wheels  54  carried on an axle  55 . The surface  53  engages the ground at a position rearwardly of the cutter bar and underneath the table such that, in the second mode of operation, the ground engaging members collectively support the skid element  48  spaced above the ground while the first and second wing frame portions are allowed to pivot relative to the center frame portion in response to changes in ground height. 
     The wheels  54  defining each of the surface arrangements are mounted by the axle  55  on an elongate support member  56  connected at a forward end  57  adjacent to and rearwardly of the cutter bar  47  for pivotal movement about an axis  58  parallel to the cutter bar  47 . The elongate support member  56  forms a rigid beam arranged to be raised and lowered to raise and lower the wheels  54  and the surface arrangement  53  defined thereby; 
     As shown in  FIG. 8 , each of the wheels is fully retractable, by raising of the elongate support member or beam  56  to an uppermost raised position within the channel  43 , to a height of the wheel underneath the table to cause the skid element  48  or cutter bar polymer shield to engage and run across the ground in the first mode of operation cutting at ground level. In this mode the header will ride either on the cutter bar shield or on the skid shoe depending on the header angle. 
     Thus the first and second ground engaging members are mounted at respective outer ends of the first and second wing frame portions and the two inner additional ground engaging members  51  are mounted on the first wing frame portion closely adjacent to the pivot axis and on the second wing frame portion closely adjacent the pivot axis. In the second mode of operation and in this arrangement where the ground engaging members are mounted only on the wing sections, the center frame portion is supported only by said float suspension system and not by any additional ground engaging members  51 . 
     Each of the elongate support beams  56  extends rearwardly under the table to a rear end  59  rearward of the table. At the rear end there is provided an upstanding telescopically extendible member  60  connected at a lower end  61  to the elongate support beam  56  and to a lug  63  of the frame structure at the upper end  62  rearward of the table to raise and lower the beam relative to the frame and thus the cutter bar relative to the ground. 
     As best shown in  FIGS. 10 and 11  the extendible member comprises a pair of telescopic members  65  and  66  including an outer member  65  with an inner member  66  slidable within the outer member. The inner member  66  has a plurality of longitudinally spaced holes  67  for receiving a pin  68  of the outer member to locate the inner and outer members at an extension position defined by the selected hole. The holes  67  are spaced also transversely across the inner member and the pin is carried on a rotatable member  69  which acts when rotated to move the pin  68  transversely across the outer member into a selected one of a plurality of holes  70  so that the transverse position of the pin is adjusted as the member  69  is rotated and when rotated acts automatically to select one of the holes of the inner member, thus determining the telescopic length of the member  60 . The elongate support members are each located in a second channel portion  46  of a respective one of said frame members  41  and extends rearwardly under the table to the rear member  60  for adjustment. 
     Each of the ground engaging surfaces  53  is located under the table so that it is forward of the rear of the table. Thus when raised, the amount of movement allowed is relatively small. In order to achieve the required height of the cutter bar of at least 12 inches and preferably greater than 14 inches, the mounting assembly includes the tilt cylinder  26  connected to the frame structure of the header for tiling the frame structure and the cutter bar carried thereby forwardly and rearwardly. Thus when actuated by a switch  72  the tilt cylinder can be retracted to pull the front of the header upwardly to further increase the height of the cutter bar, although the arrangement described herein provides a required height of the cutter bar even without the tiling action of the cylinder  26 . 
     In a case where the manual adjustment of the member  60  is replaced by a hydraulic cylinder, common operation of the lowering of the elongate support members  60  and the tilt cylinder causes the cutter bar to be raised such that the cutter bar is located at a cutting height from the ground of greater than 12 inches. 
     As shown in  FIGS. 6, 7 and 8 , the forward end  57  of the member  56  can include a skid plate  73 . The forward end is pivotally connected to a transverse mounting pin attached to the frame behind the skid element  48 . Suitable lugs are attached to the frame member  41  at the forward end to receive the pin. As an alternative, the skid plate  73  can form a part of the header and is mounted to the frame permanently by a pin for pivotal movement about the pin. In this arrangement the toward end of the member  56  is attached by a coupling to the skid plate. 
     As shown in  FIGS. 6 and 9 , the axle  55  of the wheels  54  is mounted on a suspension linkage  74  which allows the axle to move up and down on the linkage about a pivot pin  75  at the forward end with a resilient block or spring  76  resisting the upward movement of the wheels toward the member  56 . This provides a resilient suspension arrangement between the elongate support member and the wheels allowing up and down floating movement of the wheels. 
     In  FIGS. 12, 13 and 14  is shown an alternative arrangement where the surface arrangement for engaging the ground comprises a skid surface  77  which extends from a forward edge  78  effectively as a continuous slide surface rearwardly to a rear end  79  at the extendible member  60  just behind the rear edge of the table. The surface  77  thus forms a continuous surface which slides over the ground from a front edge at a position adjacent the cutter bar to a position at least adjacent to the rear edge of the table. As shown in the cross-sections of  FIGS. 13 and 14 , the skid surface  77  is arched both longitudinally and transversely. 
     The skid surface is carried on the member  56  as a permanent attachment thereto and can be used alone to run over the ground. Alternatively the skid member can be used in conjunction with a pair of ground wheels  54 A mounted on the member  56  by a suspension arrangement similar to that previously described. Thus when the wheels are used they can float upwardly relative to the skid surface so that primarily the wheels run on the ground and provide the support. The wheels can be removed in some conditions such as heavy mud where they may be ineffective or may collect mud. That is the wheel arrangement is removable to allow the skid surface to slide on the ground. 
     As can be seen in  FIGS. 6 and 12 , the wheel assemblies pivot near the cutter bar and have a short skid  57  that is pail of the structure that the header would only ride on when cutting directly on the ground. The device of  FIG. 6  comprises a short skid shoe  57  on the leading edge near the cutting edge of the header with a member  56  extending rearward allowing the attachment of ground following wheels  54  and an adjustment device  60  at the rear of the header. 
     The location of the four wheel assemblies where are at each end of the header, and two are near the hinge points as displayed in  FIG. 1  ensures enough moment about the virtual balance point of the header to overcome friction and cause the header to flex. This allows the operator to use the header while in flex mode in order to achieve better ground following while cutting as high as 18″ off the ground. 
     The wheel assembly contains an isolator  74  to aid in eliminating header bounce and stress on components as the wheels travel over bumps and other incompressible objects. One embodiment of the isolator consists of a torsional rubber isolator which is mounted to the member  76  that spans from the cutter bar to the rear adjuster. In this case, the wheel assembly  54  and axle  55  which contains two links is bolted to the torsional isolator  76 . As the wheel  54  strikes an object, the links convert the force into a moment which causes the isolator  74  to rotate and absorb the load. 
     The means of adjusting the height of the wheel assembly can be a manual adjuster such as is explained later or a hydraulic wheel height adjustment system. With the manual adjuster, the operator would set all four adjusters to a height which is close to the desired cut height and fine adjustments can then be made to the cut height by changing the tilt of the header using the cylinder  26 . With the hydraulic adjustment which contains four hydraulic cylinders in a series circuit in a master slave arrangement, and a switch  72  in the combine cab, the operator can adjust the height of the wheels by actuating the cylinders using the in cab switch while harvesting. 
     The long skid shoe embodiment of  FIGS. 12, 13 and 14  consists of a member positioned such that the header rides on the shoes when in cutting position. The operator may choose to retract the shoes such that the header can cut on the ground, effectively removing the long skid shoes from operation. This enables the operator to adjust cut height such that a desired stubble length can be achieved. The embodiment shown allows for a stubble height ranging from 1.25″ up to 14″. 
     The long shoe  77  may either be integrated into standard short skid shoes  57  near the front of the header, or exist in addition to short standard skid shoes  57 . 
     The wheels  54 A can be permanently attached to the skid shoe or removable as desired. 
     The wheels  54 ,  54 A may consist of a variety of materials, including a solid material as shown in this embodiment, or a pneumatic wheel. 
     The wheels  54  may be fixed position along the member  56  or include an adjustable member (not shown) such that the distance of the wheel from the cutter bar may be altered. 
     The wheels  54 A may be used to increase the stubble height beyond the range of the shoe. In this embodiment, 18 inches may be achieved using the wheels. The wheels  54 A offer ail of the benefits of the skid shoe, while increasing the life of the device in abrasive conditions, as well as reducing friction. 
     The preferred method of providing shock absorption is to install a resilient isolator  80  at the connection of the vertical post  60  and rear of the beam  56  carrying the skid shoe member  77 . The isolator provides a hinge with a resilient rubber restrictor at the hinge which provides flexibility between the rear of the skid and the post  60  so that the skid can ride up and down to accommodate changes in terrain. Various arrangements for providing flexibility at this location are possible.