DRIVE NEUTRALIZING MEANS FOR HEADER REEL FOR AGRICULTURAL MACHINE

Abstract: A header for an agricultural machine is provided and which comprises, a cutterbar (1), an auger (3) and a rotatable reel (4). The reel (4) has a main shaft (5) defining a rotational main axis (83) around which, in use, it is rotated in one direction (89). Crop-engaging members (6, 7) rotatably are mounted on the reel (4) around respective further axes (84) disposed around the main shaft (5). Inclination control means (86) including steering means (87) positioned eccentrically of the main axis (83) are operable, during rotation of the reel (4) in said one direction (89) , to rotate the crop-engaging members (6, 7) around the respective further axes (84) in the opposite direction (90) so as to maintain the crop-engaging members (6, 7) at a fixed positional inclination relative to the horizontal whereby the free ends of the crop-­ engaging members (6, 7) define a circularly shaped locus. Drive means (34) are associated with the steering means (87) for oscillating said steering means (87) during rotation of the reel (4) whereby the crop-engaging members (6, 7) equally are oscillated back-and-­ forth around their respective further pivot axes (84) on the reel (4) and the locus (63) of the free ends of the crop-engaging members (6, 7) deviates from said circular shape. Means (101) are provided for neutralizing said drive means (34) associated with the steering means (87) so that the reel (4) may be operated with either a circular or a non-circular locus (62, respectively 63).

Description: This invention relates to headers for agricultural machines and, although it will be discussed primarily in conjunction with combine harvesters, it is to be understood that it is applicable to other agricultural machines as well. The invention more specifically is concerned with reels provided on such headers. Conventionally, a header for an agricultural machine comprises a cutterbar operable to cut standing crop, an auger which receives cut crop material and normally feeds it to a central opening through which it passes to be processed by the machine to which the header is fitted, and a rotatable reel mounted generally above the cutterbar and operable to sweep standing crop towards the cutterbar and then to transport the cut crop material over the cutterbar to the auger. The reel normally comprises a plurality of tine bars (typically six) from which extend tines along the length thereof; the tine bars being mounted on the ends of spider arms spaced along the reel for rotation about the main axis of the reel. If no other mechanism were employed, the tines of each tine bar would undergo one revolution for each revolution of the reel but this is unacceptable because, to date, the tines have been required to maintain a constant orientation as the reel rotates, primarily to prevent the tines carrying cut crop material over the reel as opposed to disengaging or withdrawing from the cut crop material as the latter reaches the vicinity of the auger. To this end, the tine bars have been made rotatable about their respective own axes on the reel and have been connected at their ends by respective crank arms to second spiders which are held offset from the first spiders. In operation, the reel including the first spiders is driven about the main axis which in turn drives the second spiders around an offset axis through the intermediary of the crank arms and in a manner so that the tine bars are rotated about their respective own axes in a direction opposite to that of the reel and by an equal amount, whereby the tines are maintained in a given orientation which is set by adjusting the position of the offset axis of the second spiders relative to the main axis of the reel. With this conventional arrangement, the tips of the tines describe a circular path which can be positioned relative to the cutterbar by adjusting (usually by hydraulic cylinders) the reel in both a generally vertical direction and in a generally horizontal direction. Ideally, the tine path lies closely adjacent and above the cutterbar on the one hand and closely adjacent the forward edge of the auger on the other hand. However, this positioning may be adversely affected if the reel is moved forwardly and downwardly which may become necessary in order to let the tines pick up down crop, i.e. crop which is no longer standing upright due to inclement weather. In SU-A-1063315 there is disclosed a reel for a combine harvester which basically is of the same type as described above but which includes a modification whereby the second or offset spiders are moved by a crank mechanism so as to vary the tine orientation during reel rotation with a view to minimizing crop losses due to flattened or down crop not being lifted by the tines for cutting by the cutterbar. Thus this modification concentrates on the problem of harvesting down crop and does not address the related problems of optimum spacing between reel and cutterbar, and transporting cut crop to the auger. The present invention is concerned with a header including a reel for an agricultural machine and of which the reel has an optimal tine path and tine orientation from the standpoints of crop engagement prior to cutting, reel/cutterbar spacing, and crop transportation to the auger after cutting. This type of header for an agricultural machine comprises : a cutterbar operable to cut standing crop; a rotatable reel having a transverse shaft defining the rotational main axis thereof and including a plurality of crop-engaging members rotatably mounted thereon about respective further axes disposed around the main shaft; reel supporting means adjustably supporting the reel on the header frame to which the cutterbar is attached so as to permit generally vertical adjustment of the reel relative to the cutterbar; first drive means for rotatably driving the reel in one direction; inclination control means including steering means and operable, during rotation of the reel in said one direction, to rotate the crop-engaging members around the respective further axes in the opposite direction so as to maintain the crop-engaging members in a fixed orientation relative to the horizontal whereby the free ends of the crop-engaging members define a circularly shaped locus; and further drive means associated with the steering means for oscillating said steering means during rotation of the reel whereby the crop-engaging members equally are oscillated back-and-forth around their respective further pivot axes on the reel and the locus of the free ends of said crop-engaging members deviates from said circular shape. This oscillation of the steering means by the further drive means enables the crop-engaging members to be oriented and displaced so as to fulfil the required three primary functions without the fulfilment of any one of these requirements detracting from the fulfilment of any other, namely : the lifting of any down crop; the supporting of the engaged crop close to the cutterbar for cutting; and the transporting of the cut crop from the cutterbar to the auger and the disengaging of the crop immediately adjacent the auger. However, whilst the optimum orientation of the crop-engaging members to meet all three of the primary requirements referred to above, is needed from time to time, it is not necessarily permanently required. For example, when normal upstanding crop is being harvested, it is sufficient to have the normal circular locus of the outer ends of the crop-engaging members because this is adequate to achieve a generally satisfactory presentation to the cutterbar of the standing crop and transportation of the cut crop material over the cutterbar to the auger. Accordingly, it is the objective of the present invention to permit rendering the further drive means inoperative when not required to thereby save power and reduce component wear. In accordance with the present invention, a header of the type as identified above and comprising said inclination control means including steering means for controlling the positional inclination of the crop-engaging members of the reel on the one hand and also comprising said further drive means associated with the steering means for oscillating the crop-engaging members back-and-forth around their pivotal mountings on the reel on the other hand, is characterized in that it further also comprises neutralizing means which operably are associated with the further drive means and the reel supporting means; the arrangement being such that, as the reel is raised from its lowermost operative position, said neutralizing means automatically place the steering means in a fixed nominal position and make the further drive means inoperative thereby preventing these further drive means from oscillating the steering means so that the locus of the free ends of the crop-engaging members has said circular shape and, as the reel is lowered toward said lowermost operative position, said neutralizing means automatically make the further drive means operative thereby permitting these further drive means to oscillate the steering means so that the locus of the free ends of the crop-engaging members has said non-circular shape. The neutralizing means may comprise disengageable coupling means provided within said further drive means and operable by the raising and lowering of the reel relative to the cutterbar; the arrangement being such that, as the reel is raised from its lowermost operative position, the coupling means are disengaged and the steering means are positioned in said fixed nominal position and, as the reel is lowered toward its lowermost operative position, the coupling means are engaged to permit the aforementioned further drive means to oscillate said steering means. The principles of the present invention alternatively also may be realized by the combination wherein : the aforementioned further drive means comprise a linkage mechanism incorporating an oscillating member mounted for oscillatory movement and arranged to be oscillated in synchronism with the rotation of the reel, and a link connected between the oscillating member and the steering means of the inclination control means; and the neutralizing means comprise a slide which is slidably coupled relative to the oscillating member and which accomodates a pivot by which one end of the link is attached thereto thus adjustably coupling said link to said oscillating member; the arrangement being such that, when the slide pivot is offset from the rocking pivot of the oscillating member, the further drive means are made operative and, when the slide pivot is aligned with said rocking pivot of the oscillating member, the aforementioned further drive means are neutralized. Headers for agricultural machines in accordance with the invention will now be described in greater detail by way of example with reference to the accompanying drawings, in which : Figure 1 is a schematic side view of a header according to the present invention and with portions broken away for the sake of clarity; said header being adapted for use in combination with an agricultural machine such as a combine harvester, Figure 2 is a detail, to a larger scale, of Figure 1, Figure 3 is a detail, to a larger scale, of Figure 2 with components in different relative positions, Figure 4 is a section on the line IV-IV of Figure 3, Figure 5 is a partial view in the direction of arrow V in Figure 1, with some components shown in section, Figure 6 is a view similar to that of Figure 1 but showing some components in different relative positions, Figures 7 and 8 are partial schematical views of Figure 1 showing two different variations in orientation of the crop-engaging members in relation to the cutterbar and auger of the header, and Figure 9 is a view similar to Figure 6 but showing a second embodiment of header. The terms "forward", "rearward", "fore-and-aft", "transverse", "left", "right", etc. used in connection with the combine harvester and/or components thereof, are determined with reference to the direction of forward operative travel of the combine harvester but should not be considered as limiting. Referring first primarily to Figures 1 to 5, the header shown therein typically may be employed on a combine harvester (not shown) and comprises a cutterbar 1 which is mounted on a header frame 2, the latter further also supporting an auger 3 having oppositely directed flights 3' at respective ends for feeding cut crop material to a central outlet (not shown) in the header through which the crop material passes for processing by the combine harvester. The cutterbar 1 conventionally is mounted at a distance forwardly of the auger 3. A header floor 81 shaped in a particular manner as is conventional extends rearwardly from the cutterbar 1 and beneath the auger 3. The header floor 81 and the auger 3 define a generally triangularly shaped crop transfer zone 67 therebetween. The header further comprises a reel 4 mounted for rotation about the axis 83 of a main shaft 5 (comprising a tube carrying a stub shaft at each end) and which includes six crop-engaging members in the form of tine bars 6, equispaced around the main shaft 5 and each having a plurality of spring tines 7 extending therealong. The reel 4 is mounted between the generally forward ends of two arms 8, the rearward ends of which are pivotally attached to the header frame 2 and which can be raised and lowered, together with the reel 4, by respective hydraulic cylinders 9. The main shaft 5 carries at each end a spider 11 having six radial arms 12 equispaced around, and connected at one end to, a ring 13 which itself rigidly is attached to said main shaft 5. The radial arms 12 are interconnected at their other ends by chord arms 14. A plurality of intermediate spiders (not shown) of similar form as the end spiders 11 also are provided. The radial arms 12 of each spider 11 rotatably carry at their outer ends stub shafts 15. Crank arms 16 are connected at one end to the inwardly facing ends of the stub shafts 15 associated with the outer spiders 11 and to the respective opposite ends of the stub shafts 15 associated with the intermediate spiders. The other ends of corresponding adjacent crank arms 16 are interconnected by tine bar sections 6 in a manner so as to define the aforementioned six crop-engaging members 6, 7 which extend across the full width of the reel 4 at equiangular intervals around the circumference of said reel 4 and in offset relationship relative to the outer ends of the spider arms 12. Said crop-engaging members 6, 7 thus are mounted on the outer ends of the spider arms 12 for rotational movement around the axes 84 defined by the stub shafts 15. Alternate crop-engaging members 6, 7, each comprising a plurality of tine bar sections 6, have a further crank arm 17 coupled to the outwardly facing ends of the associated stub shafts 15 rotatably mounted on one end spider 11. The other crop-engaging members 6, 7 have a similar further crank arm 17 coupled to the outwardly facing ends of the associated stub shafts 15 rotatably mounted on the opposite end spider 11. Thus three further crank arms 17 are associated with each spider 11. Inclination control means 86 for the crop-engaging members 6, 7 are provided which include a.o. an eccentric spider 18 associated with each one of the outer spiders 11. Each eccentric spider 18 comprises three radial arms 19 which are equispaced around a flanged ring 21 which itself is mounted concentrically with each eccentric spider 18; the axis of rotation of which is offset from that of the main shaft 5. The eccentric spider radial arms 19 are interconnected at their outer ends by chord arms 22 and further also rotatably receive further stub shafts 85 connected to the free ends of corresponding further crank arms 17. Thus the crop-engaging members 6, 7 are split into two sets of three members which are associated with respective eccentric spiders 18. The inclination control means 86 further also comprise, at each transverse end of the reel 4, a steering means 87 in the form of a set of three rollers 23 mounted on a generally triangular plate 24 which itself is mounted for oscillating movement around the main axis 83 at a point offset from its center, whereby the plate 24 acts as a crank arm. The interior of each flanged ring 21 is arranged to be supported on the three rollers 23 of the associated plate 24. Only one eccentric spider 18 and associated steering means 87 in the form of said plate 24 with the three rollers 23 thereon, is shown in the Figures 1, 2 and 5. However, as already said, two eccentric spiders 18 and associated steering means 87 are provided with the two steering means 87 being angularly offset from each other, when seen in side view of the header and relative to the main axis 83, so that successive crop-engaging members 6, 7 are presented in the correct manner, as will be described, over their operative arc of operation 82 relative to the cutterbar 1 and the auger 3. By the operative arc 82 of the tine bars 6 is meant the arc over which the tine bars 6 are moved when the associated tines 7 generally commence engaging crop material close to the ground 26 until said tines 7 finally generally disengage cut crop material as will be described in greater detail hereinafter. In as much as each eccentric spider 18 controls the position of only three crop-engaging members 6, 7, the latter are spaced 120° apart and this basically corresponds to the angular dimension of the operative arc 82 of the crop-engaging members 6, 7. This operative arc 82 is shown in Figures 1, 7 and 8 by a line 25 extending from the axis 83 of the main shaft 5 toward the auger 3 and being generally parallel to the ground line 26, and a line 27 which is spaced 120° back from the line 25. When the stub shafts 15 of one crop-engaging member 6, 7 coincide with the line 25, then the stub shafts 15 of another crop-engaging member 6, 7 of the same set of crop-engaging members 6, 7 coincide with the line 27. The portion of the locus 63 of the free ends of the tines 7 which corresponds with this operative arc 82 further will be referenced hereinafter with the reference 88. It will be appreciated that this operative section 88 of the locus 63 and the operative arc of operation 82 of the crop-engaging members 6, 7 are offset relative to each other to the extent that the free ends of the tines 7 are spaced at a distance from the corresponding stub shafts 15. The reel 4 is driven in the direction 89 by first drive means 28 comprising a drive pulley 29 (which itself is driven from the combine harvester), a belt 31 extending from the drive pulley 29 over an idler pulley 32 to a pulley 33 mounted concentrically on the main shaft 5, and back to the pulley 29. On rotation of the drive pulley 29, the main shaft 5 is rotated by the pulley 33 and thus the spiders 11 (and intermediate spiders) and hence also the crop-engaging members 6, 7 equally are rotated in said direction 89 around the main axis 83 of the reel 4. However, in view of the presence of the crank plates 24 with the rollers 23 thereon and the eccentric spiders 18 (which together form the inclination control means 86), the crop-engaging members 6, 7 are caused to rotate, during said rotation of the reel 4 around the main axis 83 in the direction 89, by an equal angular displacement in the opposite direction 90 around the respective further axes 84 of the stub shafts 15 whereby the tine bars 6, and hence the tines 7 carried thereby, are maintained in a resultant nominal fixed orientation. The locus of the outer tips of the tines 7 under these operating conditions is a circle. This basic operation of the reel 4 is conventional. However, during operation and provided the reel 4 is in an operative position close to the cutterbar 1, the angular position of the steering means 87 is varied continuously by further drive means 34 associated therewith. These further drive means 34 are split into two identical drives, one for each eccentric spider 18. Essentially, the further drive means 34 cause the steering means 87 to oscillate to advance and retard the tine bars 6 so as to alter the nominal fixed orientation of the tines 7. Each drive of the second or further drive means 34 comprises an adjustable con rod 35 pivoted at one end to a lug 36 attached to the associated crank plate 24 and pivotally attached at the distal end by a pivot 37 to a slide block 38 (Figures 3 and 4) which is slidably mounted in slots 39 in a bifurcated arm 41 of a bell-crank lever 42, the con rod 35 passing between the bifurcations of the arm 41. Thus the one (upper) pivot of the bell-crank lever 42 is the pivot 37 which is adjustably positioned by virtue of the slide block 38 for a reason to be explained hereinafter. The central pivot of the bell-crank lever 42 is a pivot 43 provided on the associated reel arm 8, and the third bell-crank pivot is a pivot 44 to which is attached one end of a rod 45 the distal end of which is pivotally attached to one end of a crank arm 46 (best seen in Figure 5), the other end of which is attached to a crank shaft 47 carrying a sprocket 48 driven by a chain 49 from a sprocket 51 attached to the main shaft 5 of the reel 4. The sprocket 51 has three times as many teeth as the sprocket 48 whereby, for each revolution of the reel 4, the crank arm 46 makes three revolutions and hence the steering means 87 also makes three complete oscillations. A pull rod 52 (Figures 3 and 4) is pivotally connected at one end to the pivot 37 and is disposed between the bifurcations of the bell- crank lever arm 41. The other end of the pull rod 52 is pivotally connected at a pivot 53 to as well one end of a support link 54 (which itself is pivotally attached at the other end to a lug 55 carried by the associated reel arm 8) as to one end of a rod 56 which is telescopically received in a tube 57 which in turn is pivotally mounted at 58 on the associated side wall 91 of the header. A compression spring 59 (Figures 2 and 4) has one end hooked around the pivot 58 and the other end hooked over the end of the rod 56 which is in the form of a tube as shown in Figure 4. In use, the header is mounted on the combine harvester via a transverse beam 61 forming part of the header frame 2. The reel 4 is lowered to the required working height by contracting the hydraulic cylinders 9 on the respective sides of the header. In the fully lowered position of the reel 4, the slide blocks 38 of the two drives together forming the second drive means 34 are pushed to the top of the respective bell-crank lever arms 41 by virtue of the rods 56 bottoming in the associated tubes 57 on lowering of the reel 4. This operative position is that illustrated in Figures 1 and 2 of the drawings. When the crop is to be harvested, drive to the reel 4 is initiated and the latter rotates in the direction 89. If the further drive means 34 were inoperative, the tines 7 would be maintained in a nominal fixed orientation by the presence of the eccentric spiders 18 and the steering means 87 as already described. However, with the reel 4 in a lowered position relative to the cutterbar 1, the further drive means 34 are made operative as still will be described in further details. On rotation of the main shaft 5 of the reel 4, the sprockets 51 also are rotated and thus the sprockets 48 are driven so as to drive the crank shafts 47 and hence the crank arms 46. Rotation of the crank arms 46 reciprocates the associated rods 45 which in turn rocks the bell-crank levers 42 about the pivots 43. This rocking of the bell-crank levers 42 effects reciprocation of the con rods 35 which in turn rocks the associated crank plates 24 whereby the positional inclination of the tines 7 is varied. In view of the 3:1 ratio of the respective sets of sprockets 51 and 48, the bell-crank levers 42 are rocked three times per revolution of the reel 4, whereby the crank plates 24 also are rocked in the same manner so that the tines 7 are oscillated three times back-and- forth around the respective further axes 84 on the spider arms 12 per one revolution of the reel 4 around the main axis 83. In other words, one full oscillation cycle of the steering means 87 corresponds to one third or 120° of a full revolution of the reel 4. Furthermore, and as already explained, the operative arc 82 of the tine bars 6 as defined by the lines 25 and 27 also extends over an angle of 120°. This operative arc 82 is the result of one oscillation cycle of the steering means 87. From what precedes it also will be appreciated that the movement of the reel tines 7 is accelerated during half of each oscillation cycle of the steering means 87 and decelerated during the other half of said oscillation cycle. The result thereof is that the locus 63 of the free ends of the tines 7 deviates from the conventional circular shape. If the crop conditions are good and there is, for example, an absence of flattened or down crop, then the combine harvester operator normally elects to raise the reel from the position shown in Figure 1 to an alternative operative position which is shown in Figure 6. By this movement, the second drive means 34 are neutralized through the intermediary of drive neutralizing means 101 which saves wear on the drive components which are thereby arrested, and also effects a saving in power consumption. This neutralizing of the second drive means 34 is effected as follows. When the reel arms 8 are raised, the bell-crank levers 42 also are raised but the respective slide blocks 38 are held stationary by the springs 59 which are presently in extension. Thus, the bell-crank levers 42 move past the slide blocks 38 until such time as the slide block pivots 37 coincide with the respective central bell-crank pivots 43. At this point, no further relative movement between the bell- crank levers 42 and the slide blocks 38 is possible so that continued raising of the reel arms 8 pulls the rods 56 out of the tubes 57. It will be appreciated that the arresting of the relative movement between the bell-crank levers 42 and the slide blocks 38 is effected by the latter bottoming in the slots 39 in the bell-crank arms 41. It will also be appreciated that, when the respective pairs of pivots 37 and 43 coincide, the rocking of the bell-crank levers 42 on rotation of the reel 4 (this part of the drive not being neutralized) no longer causes reciprocation of the con rods 35 whereby the second drive means 34 is neutralized. Returning briefly to Figure 6 of the drawings, it will be seen that the locus 62 of the outer tips of the tines 7 is a circle which is as with a conventional header. However, Figures 1, 7 and 8 illustrate the non-circular loci 63 which result from the present invention. These loci 63 comprise the operative section 88 as already described and which basically is the section wherein the tines 7 engage crop material and sweep it across the cutterbar 1 in a generally rearward direction to finally release said crop material at a location rearwardly of the cutterbar 1 and in front of the auger 3. The operative section 88 of the non-circular locus 63 basically has three distinct portions; the first portion 64 being arcuate but lying close to the ground 26 in order to pick up any flattened crop. The following portion 65 of the operative section 88 of the locus 63 is seen to be substantially linear and extends upwardly from the first portion 64 very close above the cutterbar 1. The final portion 66 of the operative section 88 of the locus 63 which follows the second portion 65 is also substantially linear and extends generally vertically very close to the forward edge of the auger 3 to which the crop material cut by the cutterbar 1 needs to be transported in an efficient manner. The transition between the second and third portions 65 and 66 extends into the generally triangular (as seen in side view) dead space 67 which traditionally exists between the cutterbar 1 and the auger 3 of a header. This extension into the dead space 67 helps to clear, at least to a better extent than normal, any crop material which tends to lodge in this space. It will be seen from Figure 8 when compared with Figure 7 that a larger oscillation stroke of the steering means 87 causes the tines 7 to sweep deeper into the dead space 67 on the one hand and is such as to make the second and third portions 65, 66 of the operative section 88 of the locus 63 more linear on the other hand. It will be appreciated that the tines 7 preferably should be oriented generally vertically when they enter into the crop material at the forward end of the operative section 88 of the locus 63 so as to facilitate this entrance (especially when the crop material is flattened) and to reduce cutterbar losses (i.e. grain losses occurring in front of the cutterbar 1 due to a.o. the reel components shaking grain kernels out of the ears). Similarly the reel tines 7 preferably also should be oriented generally vertically at the rearward end of the operative section 88 of the locus 63 so as to facilitate the release of crop material to the auger 3. However, inbetween these two extreme positions the reel tines 7 preferably should be generally inclined relative to vertical in a manner to facilitate lifting of the crop material and positively conveying it across the cutterbar 1 in a rearward direction. These desirable features are obtained by the reel under consideration o.a. by timing the first and further drive means 28, 34 so that, in the operative section 88 of the locus 63, the movement of the tines 7 changes from an accelerated to a decelerated movement at a location 94 generally vertically above the cutterbar 1 with the positional inclination of the crop-engaging members and more specifically of the reel tines 7 thereof relative to the horizontal being the smallest at this location. In other words, the steering means 87 pass through an extreme position when the reel tines 7 pass across the cutterbar 1. Furthermore, the operative section 88 of the non-circular locus 63, i.e. the section of the locus 63 where the reel tines 7 are in contact with the crop material, should correspond substantially with one full oscillation cycle of the steering means 87. Thus the steering means 87 start from one extreme position when the reel tines 7 are at the forward end 95 of said operative section 88 of the locus 63 and pass via the other extreme position (when the reel tines 7 are positioned generally vertically above the cutterbar 1) to finally return to said one extreme position when the reel tines 7 are at the rearward end 96 of the operative section 88 of the locus 63. Accordingly the portion 92 of the non-circular locus 63 associated with the half of said one full oscillation cycle wherein the crop-engaging members 6, 7 are accelerated, is positioned generally in front of the cutterbar 1 and the portion 93 of the non-circular locus 63 associated with the half of said one full oscillation cycle wherein the crop-engaging members 6, 7 are decelerated, is positioned generally rearwardly of the cutterbar 1. The reel tines 7, when in their position of maximum inclination relative to the horizontal at or proximate to the rearward end 96 of the operative section 88 of the locus 63, have their free ends located generally proximate to the forward edge of the header auger 3 so that the portion 93 of the operative section 88 of the locus 63 wherein the reel tines 7 are decelerated, extends generally between the cutterbar 1 and the header auger 3. Returning now briefly to the transition between the second and third portions 65 and 66 of the locus 63 as already described, it further also will be appreciated that, at this transition, the straight line 97 between the free end of the reel tines 7 and the further pivot axis 84 of said reel tines 7 on the reel 4 (as seen in side view of the reel) should be aligned with the radius of the reel 4 extending between the main axis 83 and said further axis 84, whereby maximum penetration of the reel tines 7 into the dead space 67 is obtained. This is obtained by proper dimensioning and positioning of various components of the reel as will be appreciated. Also the timing of the first and further drive means 28 and 34 should be such that this alignment between the radius of the reel and said straight line 97 is obtained when the reel tines 7 have their free ends positioned substantially midway between the cutterbar 1 and the forward edge of the header auger 3. This alignment is obtained upon completion of substantially three quarters of the oscillation cycle of the steering means 87. To illustrate the difference in the depth of penetration of the reel tines into the crop transfer zone 67 when comparing a conventional header with the header embodying the present invention, the circular locus 162 of a conventional reel also has been added in Figures 1, 7 and 8 illustrating the non-circular locus 63 of the arrangement according to the present invention. Both loci 63 and 162 are positioned in the close vicinity of both the cutterbar 1 and the auger 3. When positioned with their free ends at the turning point 94 of the locus 63 (i.e. at the position where the accelerated movement of the reel tines 7 turns into a decelerated movement, or where the reel tines 7 are at their maximum positional inclination relative to the vertical), the reel tines 7 are oriented so that the straight line 97 between said free ends of the reel tines 7 and the associated further pivot axes 84 defines an angle 98 in the range of 0°-20° relative to the horizontal. When positioned in the positions 95, 96 corresponding with the start and end of an oscillation cycle of the steering means 87 (i.e. at the position where the reel tines 7 are at their minimum positional inclination relative to the vertical), said straight line 97 defines an angle 99 in the range of 30°-60° with the horizontal. It will be appreciated that, by virtue of the tine bars 6 being mounted via crank arm 16 in offset relationship relative to the respective further pivot axes 84, the main dimension of the reel tines 7 is inclined at a different angle relative to the horizontal than said straight line 97 between the free ends of the tines 7 and the associated further axes 84. To the extent that the aforementioned offset is in the direction toward the auger 3, said main dimension of the reel tines 7 always is inclined at a steeper angle relative to the horizontal than said straight line 97. By this offsetting of the reel tines 7 it has become possible to orient said reel tines 7 so that, when positioned in the vicinity of the cutterbar 1, the main dimension of said reel tines 7 is oriented generally perpendicularly to the non-circular locus 63 at this location. This is advantageous to the extent that, when the tines are excessively loaded over this portion of the locus 63 and thus are flexed against their general direction of movement, they will not interfere with the cutterbar 1. As described above, each steering means 87 controls the oscillating movement of three tine bars 6 which are 120° spaced apart. The steering means 87 further also completes three cycles per one revolution of the reel 4. One oscillation cycle of the steering means 87 thus also corresponds to one third or 120° of a full revolution of the reel 4. This relationship between the number of tine bars 6 of which the angular position is controlled by a steering means 87 on the one hand and the number of oscillations of this steering means 87 on the other hand is essential to ensure that the operative section 88 of the locus 63 always remains properly positioned relative to the cutterbar 1 and the auger 3. This condition can be stated in more general terms as follows : The (or each) steering means 87, which controls the angular position of n tine bars 6 having their respective further pivot axes 84 equiangularly spaced around the main axis 83 of the reel 4, also should complete n oscillation cycles during one full revolution of the reel 4. Thus, one oscillation cycle of the steering means 87 corresponds to 360/n° of a full revolution of the reel and, as this 360/n° generally should correspond to the operative section 88 of the locus 63, it will be appreciated that n in this formula cannot vary widely. From a practical viewpoint, n may equal only 2, 3, 4 or 5 with 3 clearly being the preferred value. As already mentioned, the tine bars 6 are divided in two sets such that one tine bar 6 of one set alternates with one tine bar 6 of the other set. Stated otherwise, one tine bar 6 of one set is positioned precisely in the middle between two tine bars 6 of the other set. In the preferred embodiment illustrated in the drawings, the two sets of tine bars 6 are 60° offset relative to each other. This offsetting of the tine bars 6 of both sets also necessitates a corresponding timing of the oscillations of the respective steering means 87 to the extent that, when one tine bar 6 of one set e.g. is positioned at the turning point 94 of the locus 63 above the cutterbar 1, the adjacent tine bars 6 of the other set are positioned at the forward, respectively rearward ends 95 and 96 of the operative section 88 of the locus 63. As already mentioned, the tines 7, when positioned with their free ends at the turning point 94 of the locus 63, assume a maximum positional inclination relative to the vertical and, when positioned at the forward or rearward ends 95, 96 of the operative section 88 of the locus 63, assume a minimum positional inclination relative to the vertical. Accordingly, when one steering means 87 associated with the one set of tine bars 6 is in one extreme position, the other steering means 87 associated with the other set of tine bars 6 should be in the other extreme position. This also means that the cranks 46 of the further drive means 34 on both sides of the reel 4 should be 180° out of phase. If this requirement is respected, the loci 63 of the reel tines 7 associated with both sets of tine bars 6 overlap each other as will be appreciated. Thus all crop-engaging members 6, 7 have identically positioned operative arcs 88 of the loci 63 in the cutterbar area. Keeping in mind that all tines 7, of which the positional inclination is controlled by one and the same steering means 87, at all times assume identical positional inclinations, it also can be derived from the foregoing that, when one tine bar 6 has its tines 7 positioned at the turning point 94 of the locus 63, all tines 7 of one set of tine bars 6 assume one positional inclination which is different from the positional inclination of the tines 7 of the other set of tine bars 6. The foregoing is illustrated in the figures 7 and 8. However, as the reel 4 rotates further in the direction 89, the foregoing changes and, when the tines 7 of one tine bar 6 have their free ends at the point of maximum penetration into the dead space 67, i.e. when the oscillation cycle of the corresponding steering means 87 is 3/4 complete, all tines 7 of both sets of tines bars 6 have the same intermediate positional inclination. This condition is illustrated in Figure 1. The nominal fixed orientation of the tines 7 is set by angular adjustment of the crank plates 24 about the main shaft 5 of the reel 4. The adjustability of the con rods 35 enables this initial nominal orientation to be set as required. The extent of rocking movement of the bell-crank levers 42, and hence the extent of oscillation of the crank plates 24, is determined a.o. by the length of the crank arms 46 and Figures 7 and 8 illustrate two different extents of said oscillating movement; said figures illustrating an overall stroke of the steering means 87, of respectively 30° and 40°. It will be seen that the employment of the foregoing arrangement presents the tines 7 over the operative arc 88 adjacent the cutterbar 1 and auger 3 in an optimum manner in order to fulfil the three basic requirements of lifting flattened crop, taking it close to the cutterbar 1 for cutting, and transporting cut crop as close as possible to the auger 3 before disengaging it. In the latter respect, it will be noted that, during operation, the tines 7 initially have their main dimension oriented generally vertically and have their operative ends moving downwardly along a generally vertical section of the locus 63 when entering the crop material on the field (see the section of the locus 63 immediately forwardly of the portion 88 in Figure 1). This movement quickly changes into a generally rearwardly and horizontally directed movement in the section 64 of the locus 63 while that, at first, the general orientation of the tines remains substantially the same i.e. with the main dimension oriented generally vertically. The foregoing taken in combination with the forward movement of the combine harvester ensures that the reel tines 7 enter the crop material smoothly whereby cutterbar losses are reduced and the reel tines 7 positively engage the crop material without any hesitation for subsequently lifting and conveying said crop material. Thereafter, the rearward movement of the reel tines 7 gradually changes into a slightly upwardly and rearwardly directed movement while that the tines 7 equally gradually are inclined towards an inclined orientation for providing a scooping effect whereby crop material is presented in a positive manner to the cutterbar 1 for cutting and subsequently is conveyed rearwardly over the cutterbar equally in a positive manner. As the movement of the reel tines 7 changes from a generally rearward movement into a generally vertical movement at the transition from section 65 to section 66 of the locus 63, said reel tines 7 penetrate much deeper into the dead zone 67 than is conventional, whereby possible hesitation in the transfer of crop material from the cutterbar 1 to the auger 3 is greatly reduced. Simultaneously as the reel tines 7 move rearwardly beyond the cutterbar 1, the orientation of said tines 7 gradually returns to a generally vertical orientation. This generally vertical orientation combined with the upward movement in a generally vertical direction of the reel tines 7 in the last portion 66 of the operative section 88 of the locus 63 and in the immediate vicinity of the forward edge of the auger 3 effects a clean disengagement of the crop material so that the latter is not carried around the reel 4 by the tines 7 and a smooth transfer of the crop material to the auger 3 is guaranteed. It will be appreciated from the foregoing description that the splitting of the tine bars 6 into two sets in order to provide an adequate operative arc of the tines 7 over which the necessary variation in orientation of the tines 7 can be effected is a significant advance. It will be appreciated that, whilst in the embodiment illustrated in the present drawings the two sets of tines are driven from respective ends of the header, the drive also can in fact be effected from the same end although space and weight consideration make it more convenient to arrange the drive as in the illustrated embodiment. Turning now to Figure 9, this shows an alternative arrangement of the drive neutralizing means 101 associated with the second drive means 34. The basic construction of the header is as in the first embodiment and like components are allocated similar reference numerals. The second drive means 34 comprises as before, two identical drives and these are constructed, in the main, in the same manner as with the first embodiment, the difference being that each telescopic arrangement 56, 57 and spring 59 are replaced by a bell-crank lever 68, which is pivotally mounted on the associated reel arm 8 at 69 and of which one arm is pivoted to the associated pull rod 52 and the other arm has attached thereto one end of a spring 71; the other end of which is attached to a lug 72 connected to the corresponding reel arm 8. Figure 9 shows the second drive means 34 in the neutralized position which has already been described in respect of the embodiment of Figures 1 to 6. This position is obtained by the springs 71 urging the bell-crank levers 68 in the anti-clockwise direction, as seen in Figure 9, until the pivots 37 and 43 coincide. When the reel 4 is lowered in a direction toward the cutterbar 1 by contracting the hydraulic cylinders 9, the arms 76 of the bell-crank levers 68 eventually engage corresponding stops 78 on the header. Continued lowering of the reel 4 subsequently results in the bell-crank levers 68 pivoting in the clockwise direction, as seen in Figure 9, whereby the rods 52 push the slide blocks 38 upwardly within the slots 39 whereby the further or second drive means 34 are activated. This activated condition is obtained when the reel 4 is positioned with its tine path in close proximity to and above the cutterbar 1. Thus, the second drive means 34 is neutralized and rendered operative automatically, as with the first embodiment, on raising and lowering of the reel 4, respectively. However, with the alternative embodiment of Figure 9, the second drive means 34 also can be neutralized even with the reel 4 in the lowermost position which is shown in Figure 1 of the drawings. This is because, when the arms 76 of the bell-crank levers 68 are lowered relative to the reel arms 8 either by actually raising the reel 4 as if the neutralizing of the second drive means 34 is to be effected automatically as in normal operation, or by manually forcing the arms 76 downwardly, then, when the arms 76 are in the position shown in Figure 9, a pin 75 can be inserted in aligned apertures provided in a lug 73 attached to each arm 76 and a lug 74 attached to the corresponding reel arm 8, whereby the bell-crank levers 68 are locked in the neutralizing position. If the movement of the bell-crank levers 68 has been effected by raising the reel 4, the latter can now be lowered to the operative position of Figure 1 and no relative movement between the reel arms 8 and the bell-crank levers 68 will take place so that the neutralization of the second drive means 34 is made permanent. It will be appreciated that, when the bell-crank levers 68 are locked in the neutralizing position, it also is necessary to either remove or shift the stops 78 so as to permit a lowering of the reel 4 toward its position in close proximity of the cutterbar 1. This option of neutralizing the second drive means 34 even in the lowermost position of the reel 4 is not possible with the embodiment of Figures 1 to 6. It will be understood that changes to the details, which have been described and illustrated to explain the nature of this invention, and which fall within the scope of the claims, will occur to and may be made by those skilled in the art upon a reading of this disclosure. It will e.g. be appreciated that, in a simpler form, the drive neutralizing means 101 may consist of a disengageable coupling means provided within the further drive means 34 and which are arranged so that, when the coupling means are disengaged, the steering means 87 are positionable in a fixed position. The coupling means may be operated by the raising and lowering of the reel 4 relative to the cutterbar 1; the arrangement being such that, as the reel 4 is raised from its lowermost operative position, the coupling means are disengaged and the steering means 87 are positioned in a fixed nominal position and, as the reel 4 is lowered toward its lowermost operative position, the coupling means are engaged to permit the further drive means 34 to oscillate said steering means. It will be appreciated from the foregoing description that the present invention affords a significant advance in the art of presenting crop material to the cutterbar of a header and transporting cut crop material to the header auger, whereby harvesting efficiency is considerably increased. Nevertheless, when the crop condition is such that less attention needs to be paid to the presentation of the crop to the cutterbar 1, whereby the reel 4 can be raised to the position of Figure 6, then the further drive means 34 can be neutralized thus effecting a saving in power consumption and component wear. Aspects of the header with the reel as described herein are claimed in the co-pending patent applications no. EP-A-0.280.790 and no. EP-A-0.280.792.

Claims: A header for an agricultural machine comprising : a cutterbar (1) operable to cut standing crop; a rotatable reel (4) having a transverse shaft (5) defining the rotational main axis (83) thereof and including a plurality of crop-engaging members (6, 7) rotatably mounted thereon about respective further axes (84) disposed around the main shaft (5); reel supporting means (8) adjustably supporting the reel (4) on the header frame (2) to which the cutterbar (1) is attached so as to permit generally vertical adjustment of the reel (4) relative to the cutterbar (1); first drive means (28) for rotatably driving the reel (4) in one direction (89); inclination control means (86) including steering means (87) and operable, during rotation of the reel (4) in said one direction (89), to rotate the crop-engaging members (6, 7) around the respective further axes (84) in the opposite direction so as to maintain the crop-engaging members (6, 7) at a fixed orientation relative to the horizontal whereby the free ends of the crop engaging members (6, 7) define a circularly shaped locus (62); and further drive means (34) associated with the steering means (87) for oscillating said steering means (87) during rotation of the reel (4) whereby the crop-engaging members (6, 7) equally are oscillated back-and-forth around their respective further pivot axes (84) on the reel (4) and the locus (63) of the free ends of said crop-engaging members (6, 7) deviates from said circular shape, and characterized in that neutralizing means (101) operably are associated with the further drive means (34) and the reel supporting means (8); the arrangement being such that, as the reel (4) is raised from its lowermost operative position, said neutralizing means (101) automatically place the steering means (87) in a fixed nominal position and make the further drive means (34) inoperative thereby preventing these further drive means (34) from oscillating the steering means (87) so that the locus (62) of the free ends of the crop-engaging members (6, 7) has said circular shape and, as the reel (4) is lowered toward said lowermost operative position, said neutralizing means (101) automatically make the further drive means (34) operative thereby permitting these further drive means (34) to oscillate the steering means (87) so that the locus (63) of the free ends of the crop-engaging members (6, 7) has said non-circular shape. A header according to claim 1 characterized in that the neutralizing means (101) are formed by disengageable coupling means provided within said further drive means (34); the arrangement being such that, when the coupling means are disengaged, the steering means (87) automatically are positioned in said fixed nominal position. A header according to claim 1 characterized in that : the further drive means (34) comprise a linkage mechanism incorporating an oscillating member (42) mounted for oscillatory movement and arranged to be oscillated in synchronism with the rotation of the reel (4), and a link (35) connected between the oscillating member (42) and the steering means (87) of the inclination control means (86); and the neutralizing means (101) comprise a slide (38) which is slidably coupled relative to the oscillating member (42) and which accomodates a pivot (37) by which one end of the link (35) is attached thereto thus adjustably coupling said link (35) to said oscillating member (42); the arrangement being such that, when the slide pivot (37) is offset from the rocking pivot (43) of the oscillating member (42), the further drive means (34) are made operative and, when the slide pivot (37) is aligned with said rocking pivot (43) of the oscillating member (42), the further drive means (34) are neutralized. A header according to claim 3 characterized in that : the oscillating member is formed by a bell-crank lever (42) mounted for oscillatory movement on the header, and said slide (38) is slidably coupled to one arm (41) of said bell-crank lever (42) between the rocking pivot (43) thereof and a position at a distance from said rocking pivot (43); the bell-crank lever (42) receiving driving power at the other arm to oscillate said bell-crank lever (42) in synchronism with the rotation of the reel (4). A header according to claim 4 characterized in that the linkage mechanism of the further drive means (34) further also comprises a crank (46) which is drivingly coupled to the reel shaft (5) to receive rotational driving power therefrom and which further is operatively coupled to said other arm of the bell-crank lever (42) so as to translate rotational movement of the crank (46) into oscillatory movement of the bell-crank lever (42). A header according to any of the claims 3 to 5 characterized in that, for each revolution of the reel (4), the oscillating member (42) completes n oscillations with n equaling either 2, 3, 4 or 5. A header according to claim 4 or 5, characterized in that said one arm (41) of the bell-crank lever (42) is bifurcated with each bifurcation being slotted (39). A header according to any of the claims 4, 5 or 7 characterized in that the further drive means (34) including the bell-crank lever (42) are mounted on the reel supporting means (8) and position control means (52, 56, 57, 59) are coupled between the slide (38) and the header frame (2) for automatically neutralizing the further drive means (34) when the reel (4) is raised from its lowermost operative position and for automatically activating said further drive means (34) when the reel (4) is lowered toward its lowermost operative position. A header according to claim 8 characterized in that the position control means (52, 56, 57, 59) comprise a telescopic member (56, 57) and a tension spring (59) associated therewith for urging the telescopic member (56, 57) toward its contracted position; the telescopic member (56, 57) being provided between the slide (38) and the header frame (2) whereby the spring force (59) is operable to urge the slide (38) toward the position in alignment with the rocking axis (43) of the bell-crank lever (42) while permitting extension of the telescopic member (56, 57) when the reel (4) is raised relative to the cutterbar (1) to thereby neutralize the further drive means (34), and whereby the telescopic member (56, 57) is operable to urge the slide (38) toward an operative position spaced from the rocking axis (43) of the bell-crank lever (42) upon said telescopic member (56, 57) reaching its fully contracted position when the reel (4) is lowered toward its lowermost operative position relative to the cutterbar (1) to thereby activate the further drive means (34). A header according to claim 9, characterized in that the position control means (52, 56, 57, 59) further also comprise a pull rod (52) pivotally coupled at one end to the slide (38) and at its opposite end to the telescopic member (56, 57); the pull rod (52) having a length which substantially corresponds to the length of the stroke of the slide (38) along the one arm (41) of the bell-crank lever (42). A header according to claim 10, characterized in that the position control means (52, 56, 57, 59) further also comprise a support link (54) pivotally coupled at one end to the reel supporting means (8) and at the other end to the telescopic member (56, 57) and/or the pull rod (52) for stabilizing the position of said telescopic member (56, 57) and said pull rod (52). A header according to any of the claims 4, 5 or 7, characterized in that the reel supporting means (8) further also support, on the one hand, the further drive means (34) including the bell-crank lever (42) and, on the other hand, position control means (52, 68, 71) for the slide (38) of the further drive means (34); said position control means (52, 68, 71) including : a bell-crank mechanism (68) pivotally mounted intermediate its ends on the reel supporting means (8) and pivotally connected at one end via a pull rod (52) to the slide (38), and a tension spring (71) extending between the other end of said bell-crank mechanism (68) and a fixation point on the reel supporting means (8); said tension spring (71) being operable to urge the bell-crank mechanism (68) in a direction for moving the slide (38) toward a position in alignment with the rocking axis (43) of the bell-crank lever (42) when the reel (4) is raised from its lowermost position to thereby neutralize the further drive means (34) and said bell-crank mechanism (68) being engageable with a stop (78) when the reel (4) is lowered toward its lowermost operative position to thereby pivot said bell-crank mechanism (68) in a direction opposite to the spring force (71) so that the slide (38) is moved toward an operative position spaced from the rocking axis (43) of the bell-crank lever (42) to thereby activate the further drive means (34). A header according to claim 12 characterized in that the bell- crank mechanism (68) is fixedly connectable (73, 74, 75) to the reel supporting means (8) in a position wherein the slide (38) is aligned with the rocking axis (43) of the bell-crank lever (42) so that the further drive means (34) remain neutralized even when the reel (4) is positioned in its lowermost operative position relative to the cutterbar (1). A header according to any of the preceding claims characterized in that : the crop-engaging members (6, 7) are divided into two sets such that one crop-engaging member (6, 7) of one set alternates with one crop-engaging member (6, 7) of the other set; and further drive means (34), inclination control means (86) including steering means (87) and neutralizing means (101) are associated with each set of crop-engaging members (6, 7).

Inventors: DECOENE, FRANS,JOSEPH,GERARD,C., NAAKTGEBOREN, ADRIANUS, VAN STEELANT, JAN,RONNY,
Applicants: FORD NEW HOLLAND N.V.
Application year: 1987
Main classification: A01D57
IPC codes: A01D57