AU2017101797B9

AU2017101797B9 - Feeder Drum

Info

Publication number: AU2017101797B9
Application number: AU2017101797A
Authority: AU
Inventors: Michael FELS
Original assignee: Ip Machinery Pty Ltd
Current assignee: Ip Machinery Pty Ltd
Priority date: 2017-02-24
Filing date: 2017-12-22
Publication date: 2018-11-01
Anticipated expiration: 2025-10-21
Also published as: AU2017101797B4; AU2017101797A4

Abstract

Abstract There is disclosed a feeder device, for use in a harvester front for cutting and collecting crop material, the front including a rear opening arranged such that crop material cut by the front is transferred therethrough so as to be delivered to a feeder house of the harvester, the feeder device comprising: a shaft which has a central axis and is mountable in the harvester front so as to be rotatable about the central axis, the shaft having opposed end sections and a centre section located between the end sections, and being dimensioned such that the centre section is arranged in front of said opening when the shaft is mounted; flighting on the end sections to direct crop material received into the harvester front laterally inwardly towards a position below the centre section as the shaft rotates; and one or more paddles projecting from the centre section and extending diagonal to the central axis so as to urge cut crop material lying below the centre section towards said opening as the shaft rotates.

Description

Feeder Drum

The entire disclosures of Australian provisional patent application no. 2017900619 and international patent application no. PCT/AU2017/051153 as originally filed are incorporated herein by reference.

The present invention relates to a feeder drum for use in a harvester draper front for cutting and collecting crop material, and to a draper front including such a feeder drum.

The following discussion of the background art is intended to facilitate an understanding of the present invention only. The discussion is not an acknowledgement or admission that any of the material referred to is or was part of the common general knowledge as at the priority date of the application.

Agricultural harvesting machines typically comprise harvester fronts for collecting the crop material during the harvesting process. The crop material includes grain and crop material residue such as straw requiring separation. After the separation process, the grain is stored in a grain tank and any crop material residue such as straw is typically returned to the ground through the rear of the harvester.

Two commonly used types of header fronts are draper fronts (shown in Figure 1) and auger fronts.

Typically, auger fronts include: (1) a cutting bar for cutting the crop material, (2) a platform to receive the crop material cut by the cutting bar, to which platform the cutting bar is attached, (3) a rear opening, through which harvested crop material passes to be received through a feeder house opening in the harvester for processing, (4) a reel including a bat or finger assembly for picking up the cut crop material, and (5) an auger for conveying the cut crop material towards the centre of the platform, the auger including a feeder drum adjacent the rear opening for delivery of the harvested crop material through the rear opening during rotation of the feeder drum.

In contrast, draper fronts comprise "draper mats" which are effectively conveyor belts which travel perpendicular to the motion of the harvester which deliver the cut crop material from the cutter bar to the centre of the front. The auger visible in Fig 1 is an optional attachment referred to as a "cross auger" for draper fronts which assists the movement of crop material in bulky crops like canola. Many draper fronts, however, are not provided with such a cross auger attachment.

Typically, draper fronts include: (1) a cutting bar for cutting the crop material, (2) a platform to receive the crop material cut by the cutting bar, to which platform the cutting bar is attached, (3) a rear opening, through which harvested crop material passes to be received through a feeder house opening in the harvester for processing, (4) side draper mats for conveying the crop material towards the centre of the platform, (5) a reel including a bat or finger assembly for picking up the cut crop material, from which reel the crop material can fall onto the draper mats during rotation of the reel, (6) a centre draper mat running parallel to the motion of the harvester, or smooth surface located at or near the centre of the platform for receiving the crop material from the side draper mats and conveying it rearwards, and (7) a feeder drum, located in line with the centre mat or smooth surface, for receiving the crop material, and adjacent the rear opening for delivery of the harvested crop material through the rear opening during rotation of the feeder drum.

Figure 1 shows a harvester 10 comprising a harvester vehicle and a header front, attached to a front section of the vehicle, for cutting the crop material and delivering it to a threshing mechanism of the harvester 10, which mechanism may comprise a drum. The front shown in Figure 1 is a draper front, having side conveyors for conveying the crop material to the centre of the header front.

As shown in Figure 1, the front is located at a forward end of the harvester. The front, during operation of the harvester, cuts the crop material and delivers the crop material to the threshing mechanism for separating the crop material residue from the grain. Harvested crop material is moved from the front to the threshing mechanism; to this end, the front comprises a rear opening, through which the crop material from the conveyor passes for delivery, via a feeder house opening (behind the rear opening), to the threshing mechanism; typically, the rear opening is located at or near to the centre location of the front, necessitating movement of the crop material towards the centre of the platform; movement of the crop material to the centre is accomplished via the auger or draper mats that, during rotation thereof, move the crop material from the outer sections of the platform to the centre section of the platform for movement through the opening.

Movement of the crop material through the rear opening is facilitated by a feeder drum which consolidates the crop material and directs it in a rearwards direction to the opening. This particular feeder drum (also referred to as a crop material consolidating auger conveyor), during rotation thereof, causes the crop material to move into the opening for delivery to the threshing mechanism. Rotation of the draper mats conveys the crop material towards the centre of the platform, where the feeder drum can consolidate it and direct it rearwardly to the opening.

Feeder drums of conventional draper fronts are adapted to consolidate the crop material at the central region of the front and to convey the crop material through the opening for processing. Such feeder drums may include a retractable fingers assembly to move the crop material through the opening; cyclical extension and retraction of the fingers occurs via a crankshaft adapted to govern the timing of the finger retraction during rotation of the feeder drum. The fingers may be located in a central part of the feeder drum. Conventional feeder drums typically include helical flanges (referred to also as "flights") at opposite ends of the drum.

Conventional draper front feeder drums typically comprise a tubular shaft, having a centre section and ends, and helical flanges defining an auger structure of the ends. The centre section may be provided with a plurality of retractable fingers, which are arranged in a helix or spiral extending around and along the centre section, in which case the centre section of the drum comprises openings for permitting the fingers to be selectively displaced between the retracted condition (when the fingers are located, to a large extent or fully, within the shaft) and an extended condition (when the fingers project from the shaft). The helical flanges are attached at each end of the tubular shaft of the feeder drum; these helical flanges surround exclusively the ends of the shaft and extend inward from the outer ends of the shaft a specific distance to leave the centre section free of helical flanges.

The flighting in conventional draper front feeder drums can fail to "grab" the cut crop material in order to convey it to the rear opening.

Further, conventional draper front feeder drums have several other drawbacks.

One of these drawbacks is crop material blocking and jamming the front at the feeder drum, impeding delivery of the crop material to the threshing mechanism - this is particularly true when harvesting crops that have a high bulk of volume in relation to their weight, such as canola, lupins, peas and beans, in which instance the conventional feeder drums are insufficiently aggressive to reliably grab and feed the crop material into the feeder house of the harvester in a continuous and smooth fashion.

Another drawback of conventional draper front feeder drums is that they can suffer from a process referred to as "repeating" of crop material. A particular cause of repeating is the build-up of thrashed crop material (particularly partly processed grain and other fine crop material) under the shaft thereby creating a high-friction surface beneath the shaft, resulting in the additional incoming material remaining caught on, and thus rotating with, the feeder drum. Directing of the material to the opening by conventional draper front feeder drums relies on the retractable fingers engaging intertwined material within the crop material, to which the grain in the crop material is typically attached, so as to impart a rearward motion to the crop material, and disengaging the crop material such that the rearward motion continues and the crop material is received through the opening.

Repeating typically results in a large accumulation of crop material in front of and below the feeder drum that can potentially stall the feeder drum or damage the harvester machine; thus, once repeating escalates, the harvester has to be stopped for clearing purposes by reversing the harvester and/or manual clearing by an operator.

The incidence of repeating can be reduced by configuring the end flighting such that it extends , partially or completely, around the centre section of the shaft, whereby the crop material is concentrated into a thicker band, which engages with the thrashed material to carry it rearwards into the rear opening.

However, this extended configuration of the end flighting can lead to other negative consequences as follows.

Configuring the flighting such that it extends around the central section results in the crop material being concentrated into a narrow band adjacent the centre of the feeder drum, which may be incapable of adequately passing through the gap between the shaft and the floor on which the crop material rests, thus overloading the feeder drum and the threshing mechanism located within the harvester, and increasing the strain in the centre of the front. A further consequence of delivering the crop material to the harvester in a narrow band is that it may restrict the capacity of the harvester into which the crop is being delivered, by not fully utilising the full width of the harvester's threshing and cleaning mechanism.

Fatigue caused by frequent jamming of crop material and the resultant shock load created by uneven flow of crop material past the feeder drum can damage the feeder drum and associated parts; for example, the crankshaft may be severely damaged; typically, this type of damage requires removal of the feeder drum to replace, for example, supports that permit the movement of the fingers.

Further, conventional draper front feeder drums may include internal reverse clutches that jam in reverse position and on many occasions fall apart. Repair of such clutches is often expensive and time consuming.

Conventional draper front feeder drums typically have end plates, which close open ends of the tubular shaft, and stub shafts, connected to the end plates, for mounting the feeder drum. Lump feeding and regular reversing can cause cracking of the end plates and bending of the stub shafts. Also, blockages due to jamming of crop material at the feeder drum can wear out the slip clutch in the adaptor drive. And, the uneven flow of crop material through the combine harvester as a result of these deficiencies often leads to blocking of and potential damage to the combine harvester itself.

Deficiencies of conventional feeder drums as mentioned above can slow down harvesting speed by more than 50%, particularly in the case of relatively bulky crops such as canola.

According to a first aspect of the present invention, there is provided a feeder drum, for use in a harvester draper front for cutting and collecting crop material, the front including a rear opening arranged such that crop material cut by the front is transferred therethrough so as to be delivered to a feeder house of the harvester, the feeder drum comprising: a shaft which has a central axis and is mountable in the draper front so as to be rotatable about the central axis, the shaft having opposed end sections and a centre section located between the end sections, and being dimensioned such that the centre section is arranged in front of said opening when the shaft is mounted; flighting on the end sections to direct crop material received into the draper front laterally inwardly towards a position below the centre section as the shaft rotates; and paddles on the centre section and projecting therefrom, the paddles extending diagonal to the central axis and being arranged to either side of a plane which is perpendicular to said axis and which, when the shaft is mounted in the draper front, passes substantially centrally through said opening, such that surfaces thereof are arranged to contact cut crop material lying below the centre section so as to urge it towards said opening as the shaft rotates; fingers mounted at distributed positions along and around the shaft; and a mechanism which is configured to reciprocate the fingers, as the shaft rotates, such that each finger assumes an extended condition during downward movement thereof, so as to penetrate crop material received into the draper front and urge that material under the shaft, and assumes a retracted condition during rearward movement thereof, so as to separate from that material, wherein the fingers are dimensioned such that each projects from the shaft a distance equal to at least a third of a diameter of the shaft when in its extended condition.

Preferably, each paddle is a flight and a leading edge thereof is curved and/or inclined whereby a degree of engagement between the paddle and crop material in front of and/or below the centre section increases progressively as the shaft rotates.

According to a second aspect of the present invention, there is provided a draper front comprising a feeder drum in accordance with said first aspect, wherein the shaft is mounted so as to be rotatable about said central axis and such that the centre section is arranged in front of said opening and said plane passes substantially centrally through said opening.

According to a third aspect of the present invention, there is provided a feeder drum for a draper front to be attached to a harvester, the feeder drum comprising: a rotatable drum; flights extending along the length of said rotatable drum, the flights being arranged in a spaced apart relationship with respect to each other and comprising: outer flights located adjacent ends of said rotatable drum; and a plurality of inner flights, which is located between said outer flights, the inner flights comprising paddle flights to increase crop material grabbing and feeding action in the area located between the outer flights, and to prevent build-up of accumulated stationary crop material under a centre of said rotatable drum by an effect of wiping the floor under the rotatable drum with every revolution of the rotatable drum; and a plurality of rows of fingers, the rows being arranged in a spaced apart relationship with respect to each other and surrounding said rotatable drum, the fingers being movable from a retracted condition to an extended condition to grab and pull the crop material for delivery into a feeder house of the harvester.

According to a fourth aspect of the present invention, there is provided a draper front comprising: a rear opening; and a feeder drum in accordance with said third aspect, wherein the feeder drum is located adjacent the rear opening such that said delivery is through the rear opening.

In feeder drums embodying the invention, the flighting will, in addition to directing crop material received into the harvester front laterally inwardly, direct crop material received into the harvester front rearwardly.

In feeder drums embodying the invention, the paddles may, in addition to urging cut crop material lying below the centre section towards said opening, engage crop material which is forward of and/or above the shaft and urge it under the shaft and thence rearwardly towards the opening.

Preferably, the paddles consist of paddles arranged at substantially equal angular intervals around the shaft.

Preferably, each paddle is shaped to conform to an imaginary helix extending around the shaft from one of the end sections to the other.

Preferably, the paddles are arranged to either side of a plane which is perpendicular to said axis and, when the shaft is mounted, passes substantially centrally through said opening, such that surfaces of the paddles which are arranged to contact the crop material lying below the centre section, so as to urge it towards said opening, face in directions which intersect with said plane. Preferably, the paddle(s) to one side of the plane and the paddle(s) to the other side of the plane respectively conform to imaginary helices extending around the shaft from the one of the end sections to the other in opposite rotational directions.

The flighting on each end section may wrap up to one turn around the shaft. The flighting on each end section may wrap up to half a turn around the shaft. The flighting on each end section may wrap about half a turn around the shaft. The flighting on each end section may extend substantially throughout the entire length of that end section.

Preferably, each paddle is shaped such that the imaginary helix to which it conforms has a pitch of up to three times a diameter of the shaft. Preferably, each paddle is shaped such that the pitch is not less than about one times the diameter. In one preferred embodiment of the invention, each paddle is shaped such that the pitch is about twice the diameter.

Preferably, each paddle is shaped such that the imaginary helix to which it conforms has a pitch of up to about three times the diameter of the shaft. Preferably, each paddle is shaped such that the pitch is at least about one times the diameter of the shaft. In one preferred embodiment of the invention, each paddle is shaped such that the pitch is between about one and half times the diameter of the shaft and about two and a half times the diameter of the shaft.

Preferably, each paddle is shaped such that the pitch is about 600 mm.

Preferably, said paddles are angularly offset around the shaft. Preferably, an offset angle of the paddles is approximately 360 degrees divided by the number of paddles, whereby the angular offset of the paddles is substantially regular.

In a preferred embodiment of the invention, the number of paddles is two.

Preferably, said paddles are equiangularly offset around the shaft.

Preferably, each paddle wraps up to one half of a turn around the shaft. More preferably, each paddle wraps up to one third of a turn around the shaft. Each paddle may wrap up to one quarter of a turn around the shaft. Each paddle may wrap about one quarter of a turn around the shaft.

Preferably, the end sections each have a length between a quarter and a half of a length of the centre section.

Preferably, the flighting on each end section conforms to a respective one of imaginary helices extending around the shaft from one of the end sections to the other in opposite rotational directions. The flighting on each end may comprise a single flight or plural flights. In the latter case, the plural flights may, for example, consist of two flights offset from each other by about half a turn of the shaft.

Preferably, the flighting on one end section is offset from the flighting on the other end section by half a turn around the shaft.

Preferably, each paddle has a leading edge which is curved and/or inclined, whereby a degree of engagement between the paddle and crop material in front of and/or below the centre section increases progressively as the shaft rotates whereby the material is urged towards said opening. In one embodiment, the leading edge is inclined with respect to a surface of the shaft at a respective position on the shaft from which it extends. In another embodiment, the respective leading edge is orthogonal to the surface at that position and curves rearwardly from that position.

Preferably, the leading edge of each paddle is convex.

Preferably, the leading edge of each paddle has a radius of curvature which is between three quarters of a maximum dimension the paddle in a direction radially outward from the shaft ("depth") and all of the depth. Preferably, the radius of curvature is about 85% of the depth.

Preferably, each paddle has a radially outer edge arranged to follow the leading edge of the paddle. Preferably, the radially outer edge is substantially concentric with a circumferential surface of the shaft.

Preferably, the radially outer edge of each paddle defines the depth of the paddle.

In one preferred embodiment of the invention, each paddle is configured in the form of a fin.

Each paddle may have a trailing edge which extends from a position on the shaft so as to be perpendicular to a surface of the shaft at that position.

Preferably, said spaced positions are equally spaced.

Preferably, the fingers in each row are laterally offset from the fingers in the or each row adjacent to it.

Preferably, said mechanism comprises a crankshaft arranged within the shaft and connecting members interconnecting the crankshaft and fingers such that the fingers reciprocate relative to the shaft as the shaft rotates.

The spacing of the fingers in the rows may be such that there are in total between 12 and 30 fingers per metre in a direction parallel to said axis. There may be about 20 fingers in total per metre in that direction. In one embodiment, the drum has a length of about 1.25 to 2 meters and there are about 25 fingers.

The fingers may be spaced apart by about 0.2m within each row.

In one embodiment of the invention, the fingers are located on the centre section. In another embodiment of the invention, the fingers are located on the centre section and the end sections.

In a preferred embodiment of the invention, the flighting intersects at least one said row.

In a preferred embodiment of the invention, at least one said paddle intersects at least one said row.

In a preferred embodiment of the invention, each paddle intersects at least one said row.

According to a preferred form of the present invention, the shaft has a diameter which is between twice a distance that each finger projects from the shaft when in its extended condition and two and a half times that distance.

In a preferred embodiment of the invention, the ratio of the shaft diameter to said distance is about 2.3.

According to a preferred embodiment of the present invention, the shaft has a diameter which is between twice a depth of the flighting and two and a half times the depth of the flighting.

In a preferred embodiment of the invention, the ratio of the shaft diameter to the flight depth is about 2.3.

Preferably, the centre section has a length approximately equal to a width of the feeder house opening.

Preferably, the shaft is defined by a barrel.

Preferably, the draper front is operable such that the shaft rotates at between about 100 rpm and about 250 rpm. Preferably, the draper front is operable such that the shaft rotates at between about 120 rpm and about 250 rpm. Preferably, the draper front is operable such that the shaft rotates at between about 120 rpm and about 200 rpm. Preferably, the draper front is operable such that the shaft rotates at between about 125 rpm and about 175 rpm. Preferably, the draper front is operable such that the shaft rotates at between about 150 rpm and about 160 rpm. Preferably, the draper front is operable such that the drum rotates at about 150 rpm or about 160 rpm.

Preferably, the draper front includes conveyors configured to travel laterally inwardly to carry crop material received into said front laterally inwardly for receipt under said shaft.

Preferably, the draper front includes a central conveyor configured to travel rearwardly to carry crop material under said shaft.

In the preferred embodiments of the invention, the ratio of the shaft diameter to the flight depth is smaller than in conventional drums. Advantageously, for a given spacing between the shaft axis of rotation and the floor/platform of the front, the spacing between the shaft and the floor/platform is greater, allowing passage of more cut crop material under the shaft. Preferably, the fingers in their extended conditions project a distance from the shaft which is approximately equal to the flight depth, whereby their "effective length" is greater than in conventional feeder drums.

According to a preferred embodiment of the invention, said feeder drum is rotatably mountable in said draper front, the front being attached or attachable to a harvester, and the flighting comprises flights provided on the end sections, each flight wrapping less than one turn around the shaft, the flights conforming to imaginary helices extending from a first end of the shaft to a second end of the shaft in opposite rotational directions, so as to convey the cut crop laterally inwardly to a position below the centre section, each imaginary helix having a pitch which is such that a force applied to crop material by that flight has a component tangential to a direction of rotation of the shaft and a component parallel to an axis of rotation of the shaft, the former component being equal to or greater than the latter component.

Preferably, each imaginary helix has a pitch which is about twice the diameter of the shaft.

Preferably, each flight has a curved outer end, adjacent an outer end of the end section on which it is provided, and an inner end defining a straight edge extending radially from the shaft.

Preferably, the feeder drum is configured such that, when it is mounted rotationally in the front, the centre section is aligned with the feeder house opening, and the centre section has a length the same as or less than a width of the feeder house opening. In a preferred embodiment of the invention, the width of the feeder house opening is about 1.1m and the length of the centre section is about 1.0m. In one embodiment of the invention, the width of the feeder house opening is 1100mm and the length of the centre section is 1000mm.

In a preferred embodiment of the invention, a said first flight wraps less than a full turn around a first one of the end sections, and another said first flight wraps less than a full turn around the second end section.

In a preferred embodiment of the invention, each first flight comprises a proximal end, attached to a respective one of the ends of the shaft end comprising a curved edge, and a distal end, at a respective location spaced inwardly from the end of the shaft, defining a straight edge that extends perpendicularly from an outer surface of the shaft.

The length of said section of the shaft may be less than the width of the feeder house opening by, for example, 100 mm.

Preferably, each first flight extends laterally inwards a distance (B), in a direction parallel to an axis of rotation of the shaft, from a respective one of the outer ends of the shaft ; in other words, lengths of respective sections of the shaft over which the first flights extend are B. The numerical value of the distance (B) is dependent on the particular harvester with which the feeder drum will be operating.

Preferably, the distance (B) is about half the difference between a length (A) of the shaft and the distance (F) between the first flights in a direction parallel to an axis of rotation of the shaft (i.e. the length of a section of the shaft which extends between the laterally inner/distal ends of the first flights).

The distance (F) may be about 100mm less than a width of the rear opening.

In several commonly available harvester models to which the invention is suited, the opening width is about 1100mm or 1.1m, resulting in the distance (F) being about 1000mm or a metre.

The distance (B) may be between about 300mm and about 500mm. The distance (B) for the feeder drum to be suitable for the MacDon D60 or D65 model, MacDon older models, Honeybee model and Case/New Holland model can be, respectively, about 337.5 mm, about 280 mm, about 412.50 mm and about 492 mm. In particular, the distance (F) for such models is about 1000 mm.

The length (A) for the feeder drum to be suitable for the MacDon D60 or D65 model, MacDon older models, Honeybee model and Case/New Holland model can be, respectively, about 1675 mm, 1560 mm, 1825 mm and 1984 mm.

In a preferred embodiment of the invention, the depth of each first flight is about 130mm.

In a preferred embodiment of the invention, the first flights comprise a first flight having a right-hand thread wrapping less than a full turn around the first end section of the shaft, and a first flight having a left-hand thread wrapping less than a full turn around the second end section of the shaft, the first flight having a right-hand thread is provided on the end section of the feeder drum which is on the left when the feeder drum is viewed from the rear (the first end section), and the first flight having a lefthand thread is provided on the end section of the feeder drum which is on the right when the feeder drum is viewed from the rear (the second end section).

In a preferred embodiment of the invention, said paddles wrap about one third of a full turn around the shaft.

In the preferred embodiments of the invention, the paddles comprise a paddle having a right-hand thread wrapping around the centre section and a paddle having a lefthand thread wrapping around the centre section.

The feeder drum according to a preferred embodiment of the invention is designed to be operated in a harvester comprising a feeder house opening having a width of 1100 mm. In that embodiment, said paddles are spaced apart a distance (D), in a direction parallel to an axis of rotation of the shaft, of about 280mm.

In a preferred embodiment of the invention, trailing edges of the paddle having a right-hand thread and the paddle having a left-hand thread are offset by an azimuth angle Φ around the axis. The azimuth angle Φ may be about 180°.

In a preferred embodiment of the invention, the feeder drum is to be operated in a harvester with a feeder house opening having a width of 1100 mm, and the distance (C), in a direction parallel to an axis of rotation of the shaft, between the first flight having a right-hand thread and the paddle or flight section having a left-hand thread is about 640 mm.

In a preferred embodiment of the invention, the feeder drum is to be operated in a harvester with a feeder house opening having a width of 1100 mm, and the distance (C), in a direction parallel to an axis of rotation of the shaft, between the first flight having a left-hand thread and the paddle or flight section having a right-hand thread is about 640 mm.

In a preferred embodiment of the invention, the feeder drum is to be operated in a harvester with a feeder house opening having a width of 1100 mm, and the distance (G), in a direction parallel to an axis of rotation of the shaft, between the first flight having a right-hand thread and the paddle or flight section having a right-hand thread is about 360 mm.

In a preferred embodiment of the invention, the feeder drum is to be operated in a harvester with a feeder house opening having a width of 1100 mm, and the distance (G), in a direction parallel to an axis of rotation of the shaft, between the first flight having a left-hand thread and the paddle or flight section having a left-hand thread is about 360 mm.

In a preferred embodiment of the invention, neighbouring ones of the fingers in each row are spaced apart 200 mm.

In a particular embodiment, the fingers of each row extend along a particular section of the shaft.

Preferably, adjacent ones of the fingers, or centres thereof, in each row are spaced apart by a distance proportional to the width of the feeder house opening. Preferably, that distance is about equal to or slightly larger than the distance F.

In a particular embodiment, there are 25 fingers extending along a particular section of the shaft, and the particular section of the shaft has a length of about 1.25 to about 2 meters.

In a particular embodiment, adjacent ones of the fingers, or centres thereof, in each row are spaced apart by about 200 mm.

In one embodiment of the invention, each row extends from one end of the shaft to the other end of the shaft. In another embodiment of the invention, the rows of fingers extend along a particular section of the shaft, the particular section extending between said first flights.

In one embodiment of the invention, said rows of fingers are intersected by the flights and/or flight sections or paddles.

There may be about 12 to 30 fingers/m of shaft.

In a particular embodiment, there are four linear rows of fingers.

Preferably, neighbouring rows of fingers are spaced apart from each other at a constant azimuth angle Φ around the shaft.

Preferably, the azimuth angle Φ is about 90°.

The fingers of neighbouring rows may be offset with respect to each other.

Preferably, the flighting has a coarse pitch, and the rows of fingers extend throughout the length of the shaft.

Preferably, (i) the shaft diameter is relatively small shaft and the flight depth is relatively large, and/or (ii) the fingers project a relatively large distance from the shaft when extended. Feature(ii) is particularly advantageous because it results in the retractable fingers penetrating further into the crop material, thereby more reliably moving the crop material rearwardly for receipt through the opening. A further benefit is that there is a taller gap between the shaft and the floor or platform under the feeder drum, allowing more bulk of crop material to flow unimpeded under the shaft and through to the feeder house opening.

According to a preferred form of the invention, there is provided a draper front comprising (1) a cutting bar for cutting the crop material, (2) a platform adapted to receive the crop material cut by the cutting bar, (3) delivery means for moving the crop material towards a centre of the platform, (4) a rotatable reel, including an assembly of teeth for picking up the cut crop material, from which the crop material can fall onto the delivery means, and (5) said feeder drum, rotatably mounted in the harvester front and located adjacent the delivery means so as to receive the crop material therefrom, wherein the feeder drum is arranged to direct the crop material rearwardly such that the crop material is received into the harvester during rotation of the feeder drum, wherein the delivery means comprises at least one conveyor.

The delivery means may comprise conveyors to opposite lateral sides of the feeder drum.

Further features of the present invention are more fully described in the following description of several non-limiting embodiments thereof. This description is included solely for the purposes of exemplifying the present invention. It should not be understood as a restriction on the broad summary, disclosure or description of the invention as set out above. The description will be made with reference to the accompanying figures in which:

Figure 1 is a side perspective view of a conventional harvester draper front;

Figure 2 is a rear side perspective view of a feeder drum in accordance with an embodiment of the invention incorporated in the front shown in Figure 1;

Figure 3 is a front side perspective view of the feeder drum shown in Figure 2;

Figure 4 is a front side perspective view of one of two opposite end sections of the feeder drum shown in Figure 2;

Figure 5 is a front side perspective view of the other end section;

Figure 6 is a rear perspective view of the feeder drum shown in Figure 2, incorporated in the front shown in Figure 1, in operation;

Figure 7 is a rear schematic view of the feeder drum showing dimensions therein;

Figure 8 is a table providing numerical values of the dimensions for different type of models of harvester fronts;

Figure 9 is a schematic front/side perspective view of the of the feeder drum shown in Figure 2; and

Figure 10 is a rear view of the feeder drum shown in Figure 2.

Shown in the figures is a feeder drum 26 embodying the invention and a harvester front 12, within which the feeder drum is to be rotatably mounted, for cutting and gathering crop material for receipt through a feeder house opening in a harvester vehicle 10 to which the harvester front 12 is attached.

The feeder drum 26 comprises a shaft 30 and sectional screw flighting 32, comprising screw flight sections 32a, 32b, 32c and 32d, on the shaft 26.

The feeder drum 26 has a first end section 33a with first screw flighting (32a), a second end section 33b with other first screw flighting (32d), and a centre section with second screw flighting (32b and 32c). The first flight 32a has a right-hand thread, and the first flight 32d has a left-hand thread. The second flight 32b has a right-hand thread and the second flight 32c has a left-hand thread.

The first end section 33a when viewing the rear of the feeder drum 26 is the left-hand end. The second end sections 33b when viewing the rear of the feeder drum 26 is the right-hand end.

The feeder drum 26 is for use in a harvester front for cutting and collecting crop material, the front including a rear opening arranged such that cut crop material is transferred therethrough into a feeder house opening of the harvester.

Figure 2 shows a particular arrangement of a feeder drum 26. The feeder drum 26 is located at the centre section 24 of the front 12 and adjacent the opening such that the crop material is moved to the feeder house for processing within the harvester 10.

The feeder drum 26 comprises a shaft 30 which is mountable in the harvester front 12 so as to be rotatable about a central axis of the shaft and has opposed end sections 41 and a centre section 39 located between the end sections 41a and 41b as shown in figure 7. The shaft 30 is dimensioned such that the centre section 39 is arranged in front of the rear opening when the shaft 30 is mounted on the front 12. The end sections 41 each have a length between a quarter and a half of a length of the centre section 39.

The feeder drum 26 is adapted to rotate during operation of the harvester 10 for delivering the crop material through the rear opening and thence the feeder house opening in the harvester 10. Rotation of the feeder drum 26 effects movement of crop material which has been delivered to a position below the shaft by delivery means, such as a centre draper mat, through the rear opening. The feeder drum 26 includes fingers 28 which, during rotation of the shaft, are extendable to engage the crop material and move it rearwardly, and thence retractable to permit the rearwardly moving crop material to become disengaged from them so as to be received through the rear opening.

The sectional flights 32, which confer enhanced operation to the feeder drum 26, comprising (1) first flights 32a and 32d and (2) second flights 32c and 32b. As will be described in greater detail below, the feeder drum 26 is configured to feed the crop material through the feeder house opening in an improved manner.

The feeder drum 26 has paddling means, for engaging and moving crop material resting below the drum into the feeder house opening, which means comprises paddles projecting from the centre section 39 and extending diagonally to the central axis or shaft so as to urge crop material lying below the centre section 39 towards said rear opening as the shaft rotates. The paddles are defined by flights 32b and 32c ("paddle flights") arranged at spaced positions on the shaft 30 and being located laterally inward of the first and second end sections 33.

The paddles 32b and 32c wrap, for example, about a quarter of a turn around the shaft 30 or a third of a turn around the shaft 30.

The paddles are configured to conform to imaginary helices extending from a first end of the shaft 30 to a second end of the shaft 30 in opposite rotational directions.

In the particular embodiment illustrated, each imaginary helix has a pitch of about 600 mm. More generally, the pitch may be between about one times the diameter of the shaft and about three times the diameter of the shaft.

Further, the paddles 32b and 32c are arranged to either side of a plane which is perpendicular the axis of rotation of the shaft and passes substantially centrally through the rear opening, such that leading surfaces of the paddles 32b and 32c face in directions which intersect with said plane. The paddles 32b and 32c are arranged to contact the crop material lying below the centre section of the shaft 30, so as to urge the crop material towards said rear opening.

The paddles are angularly offset around the shaft. An offset angle between adjacent ones of the paddles is about 360 degrees divided by the number of paddles, whereby the angular offset of the paddles is regular.

Without departure from the invention, numerical values of dimensions of the feeder drum 26 may be varied such that the feeder drum is configured for use with different type of harvesters. Figure 7 is a schematic drawing of the feeder drum 26, in which the dimensions of the feeder drum 26 the values of which can be adjusted are labelled using letters A through F. Figure 8 shows the numerical values for different types of harvester draper front.

Configuring the feeder drum 26 such that the features thereof shown in Figure 7 have dimensions as shown in Figure 8 permits operating of the feeder drum 26 in the respective harvester fronts 12 referenced in Figure 8. In alternative feeder drums embodying the invention, which include the features shown in Figure 7, those numerical values of the dimensions of those features can differ from the values listed in Figure 8, whereby the feeder drums are suitable for other type of harvester and harvester front not referenced in Figure 8.

Referring to Figures 2 to 5, the feeder drum 26 comprises a shaft 30 and a plurality of flights 32 arranged on the shaft. The flights 32 extend substantially along the entire length of the shaft 30 and are arranged in a spaced apart relationship with respect to each other.

In the particular embodiment shown in the Figures, there are four flights 32a to 32d, the flights 32a and 32b having right-hand threads, and flights 32c and 32d having left-hand threads.

The flight 32a comprises a curved laterally outer end 35a adjacent the first end 33a of the shaft 30 - see figure 2. The flight 32d comprises a curved laterally outer end 35d adjacent the second end 33b of the shaft 30 - see figure 3.

Further, the flight 32a comprises a laterally inner end 37a spaced apart from the first end 33a - see figure 3. The flight 32d comprises a laterally inner end 37b spaced apart from the second end 33b - see figure 3.

The flights 32a and 32d define flighting wrapping around the end sections 41a and 41b of the shaft 30. The flighting on each end section 41 extends substantially throughout the entire length of that end section. The flight 32a on the first end section 41a is offset from the flight 32d on the second end section 41b by half a turn around the shaft 30.

The first and second flights 32 partially wrap around the shaft 30 such that the flights 32 do not complete one full turn of 360° around the shaft 30 but instead wrap around the shaft 30 at azimuth angles around the longitudinal axis of the shaft 30 less than 360°.

In particular, the flights 32a and 32d, forming one pair, wrap around the shaft 30 a particular azimuth angle Φ of about 180° such that the flights 32a and 32d wrap about a half (1/2) of one turn around the shaft 30.

In an alternative arrangement, the first and second flights on each end section 41 wrap up to one turn around the shaft.

The flights 32b and 32c, forming another pair, wrap around the shaft 30 a particular azimuth angle Φ of about 120° such that the flights 32b and 32c wrap about one third (1/3) of a turn of the shaft 30.

In an alternative arrangement, each of the flights 32b and 32c on the centre section 39 wraps up to or about a quarter of a turn around the shaft.

Referring to Figures 2 to 5, the flights 32a to 32d partially surround the shaft 30; this can be appreciated when comparing the rear views (Figures 2 and 6) of the feeder drum 26 against the front views (Figures 3 to 5) of the feeder drum 36. In fact, the flights 32a and 32c shown in Figure 2 extend around the shaft 30 of the feeder drum 26 from a particular location, shown in Figure 2, to another particular location, shown in Figure 3, that is offset an angle of less than 360° from the particular location shown in Figure 2.

Similarly, the flights 32b and 32d extend around the shaft 30 from a particular location, shown in Figure 3, to another particular location, shown in Figure 2, that is offset an angle of less than 360° from the particular location shown in Figure 3.

The flight 32a wraps a particular angle Oa around the shaft 30 and flight 32b wraps a particular angle Ob around the shaft 30, the angle Ob being smaller than the angle Oa. Similarly, flight 32d extends a particular angle Od around the shaft 30 and flight 32c extends a particular angle Oc around the shaft 30, the angle Oc being smaller than the angle Od.

The values of the angles Ob and Oc may be about 120° and the values of the angles Oa and Od about 180° though these values may vary without departure from the invention.

Each of the second flights 32b and 32c on is configured in the form of a fin having a leading edge 38, configured in a bevelled form, and a trailing edge 40 configured in a square form. These flights 32b and 32c, advantageously, take the form of paddles, which can engage the crop material and move it from the section of the floor or platform of the front which underlies the shaft, particularly the centre section thereof, to the rear opening.

The leading edges 38 of the paddles 32b and 32c are substantially identical, albeit oppositely handed, as are the trailing edges 40 of those paddles. Figure 4 shows the leading edge 38b and the trailing edge 40b of the paddle 32b and the trailing edge 40c of the paddle 32c. The leading edge 38c of the paddle 32c is also configured in a bevelled form, as can be seen in Figure 7.

The leading edge 38 of each of the paddles 32b and 32c is a curved edge defined by the outer edge 42 (the outer edge 42 being the edge that is opposite to the edge 44 that is attached to the outer surface of the shaft 30) with the radial dimension or height of the curved edge of the paddle flights 32b and 32c decreasing to zero as the paddle 32 partially wraps around the shaft 30 as shown in Figure 4 or 7. In the particular embodiment shown in the Figures, the curved edge has a radius of curvature being about 85% of the flight depth. In a particular arrangement, the flight depth is 130mm and the curvature radius is about 110mm.

Further, as mentioned before, the paddles 32b and 32c comprise square trailing edges 40 that define an end edge extending radially, or perpendicularly to the outer surface of the shaft 30, and have a height equal to the flight depth of the flights 32 -see figure 4.

In a particular arrangement, the leading edge of the or each paddle has a radius of curvature, about a position on the shaft from which a trailing edge of the paddle extends, which is between half of a maximum dimension the paddle in a direction radially outward from the shaft ("depth") and about 190 mm or more.

Furthermore, in the particular arrangement shown in the Figures, the trailing edges 40b are offset by about 180° as can be appreciated in Figure 4 or 7. In other words, the trailing edges 40b and 40c are spaced apart an angle Φ of 180° around the axis of the shaft 30.

Advantageously, the curvature of the leading edges 38 of the paddles 32b and 32c prevents catching of crop material on the edges 42 of the paddles 32b and 32c (in particular, the leading edges 38 themselves) during rotation of the shaft 30. Thus, the inclusion of paddles 32b and 32c provides for increased engagement of crop material and movement thereof through the rear opening, thus preventing formation of a stationary build-up of crop material that rests under the centre section of the shaft 30.

The amount that the first flights 32a and 32d extend along the shaft 30 from the ends of the feeder drum 26 is related to the width of the feeder house of the harvester to which the front is mounted.

The first flights 32a and 32d extend away from the outer ends 33 of the shaft 30 a distance such that their laterally inner ends 37a and 37d are substantially in front of respective laterally outer sides of the feeder house opening in order for the distance (F) as shown in figure 7, between laterally the ends 37a and 37d of the first flights to be substantially the same as or slightly (e.g. about 100mm) less than the width (i.e. distance between the laterally outer sides) of the feeder house opening.

The angles Oa, and Od are less than 360°, whereby the flighting on each end section of the shaft 30 is coarse, i.e. has a large pitch, at odds with such flighting in conventional feeder drums, which wraps around the end sections several time and thus is fine, i.e. has a small pitch.

The flights 32a and 32d are configured to conform to imaginary helices extending from the first end 33a to the second 33b of the shaft 30 in opposite rotational directions, the helices being coarse. In the particular embodiment shown in the figures, each imaginary helix has a pitch of about two times the diameter of the shaft.

That the pitch of each imaginary helix is relatively large is advantageous because the tangential component of a force applied to the crop material by flighting conforming to that helix (flights 32a and 32b) is relatively large, and in particular is equal to or greater than the component of the force in a direction parallel to the axis of rotation of the shaft, whereby a rearward pushing effect of the flights on the crop material is greater than in smaller-pitch flighting in conventional feeder drums.

The distance (B), parallel to the shaft axis, that each of the first flights 32a and 32d extends from the respective outer end of the shaft 30 - i.e. the length of each outer section of the shaft - may vary depending on the particular harvester 10 and harvester front (12) in/with which the feeder drum 26 is to operate, this distance being labelled as B in Figure 7 and numerical values thereof being listed in figure 8 for particular harvester fronts 12, when fitted to a harvester vehicle a feeder house opening in which may have a width of 1100mm.

As indicated in Figure 8, the particular distance (B) is half the difference between the shaft length (A) and the distance (F), parallel to the shaft axis, between the laterally inner ends of the first flights 32a and 32d, i.e. the length of the centre section. Also, the distance (F) in the feeder drum is substantially the same as or smaller than the width of the rear opening in the harvester front in which the feeder drum is mounted (in a manner such that the centre section is aligned with the opening).

Further, in the feeder drum 26 according to the embodiment shown in Figures 2 to 6, the numerical value of dimension B may differ depending on the particular type of harvester 10 or harvester front 12 with/in which the feeder drum 26 is to operate. Figure 8 shows particular numerical values for dimension B that feeder drums 26 may have in order to operate satisfactorily with different type of harvester fronts 12, when fitted to a harvester vehicle a feeder house opening in which may have a width of 1100mm.

For the first flights 32a and 32d to extend the distance (B) and wrap less than a full turn around the shaft 30, in order that the feeder drums 26 is suitable for models such as those referenced in Figure 8, the first flights 32a and 32d have a relatively coarse flighting.

Advantageously, the coarse pitch of the flights 32a and 32d renders those flights relatively aggressive, enhancing their ability to "grab" the cut crop material in order to convey it towards the rear opening.

In particular, in one arrangement, the trailing edges of the paddles 32b and 32c are spaced apart a distance (D) in a direction parallel to the axis of the shaft (i.e. a section of the shaft extending between the trailing edges has length D) for a feeder drum 26 to suitable for a front in a harvester with a feeder house opening which may have a width of 1100 mm. Figure 8 shows particular numerical values of the distance D for different types of harvester fronts when fitted to a harvester with a feeder house opening width of 1100mm.

Furthermore, the distance (C), in a direction parallel to the axis of the shaft, between the distal ends of the first flight 32a and 32d and of the paddles 32b and 32c (i.e. the length of the section of shaft extending between the distal ends of the first flight 32a and 32d and of the paddles 32b and 32c) will be such that the paddles 32b and 32c are forward of and aligned with the feeder house opening, permitting the paddles 32b and 32c to move the crop material into the feeder house opening.

In particular, for a feeder drum 26 to be operated in the case of the harvester 10 mentioned in figure 8 and which all have a feeder house opening having a width of 1100mm, the distance (C) between the laterally inner end 37 of the first flight having a right-hand thread and of the paddle having a left-hand thread is about 640 mm. Also, for a feeder drum to be operated in the case of the harvester 10 with a feeder house opening having a width of 1100 mm, the distance (C) between the distal ends 37 of the first flight having a left hand thread and of the paddle flight having a right hand thread is about 640 mm.

Furthermore, the distance (G), in a direction parallel to the shaft axis, between the laterally inner end 37 of each of the first flights 32a and 32d and the laterally inner end of the respective one of the paddles 32b and 32c adjacent to it will be such that the paddles 32b and 32c are forward of and aligned with the feeder house opening, permitting the paddles 32b and 32c to move the crop material into the feeder house opening, for a feeder drum 26 to be suitable a harvester with a feeder house opening which may have a width of 1100 mm, the distance (G), in a direction parallel to the shaft axis, between the laterally inner end 37d of the first flight having a right-hand thread and the paddle having a right-hand thread is about 360 mm.

Further, for the feeder drum 26 to be suitable for a harvester which may have a feeder house opening having a width of 1100 mm, the distance (G), in a direction parallel to the shaft axis, between the laterally inner end 37a of the first flight having a left-hand thread and the paddle having a left-hand thread is about 360 mm.

Moreover, the feeder drum 26 according to the illustrated embodiment has an overall diameter (dimension E shown in figure 7) being the diameter of the shaft 30 plus the flight depth, the flight depth being the maximum radial dimension of the flights 32. In the feeder drum 26 according to the embodiment shown in the figures 2 to 6, the diameter of the shaft 30 is about 300 mm and the flight depth (also referred as the strip width) is about 130 mm. Thus, the ratio between the overall diameter of the feeder drum 26 (being the diameter of the shaft 30 plus the flight depth) and the diameter of the shaft 30 is about 1.87- i.e. ((560)/(560-260).As shown in Figure 8, this feeder drum 26 is suitable for MacDon D60 and D65 models, MacDon older models, and Honeybee models.

Without departure from the invention, the diameter of the shaft 30 and the flight depth in feeder drums 26 may have dimensions differing from those mentioned above; thus the ratio between the overall diameter of the feeder drum 26 and the diameter of the shaft 30 may be different. For example, as shown in figure 8 for a harvester front of the Case/New Holland (CNH) type, the overall diameter of the feeder drum 26 is 650 mm and the flight depth is about 130 mm.

Further, the diameter of the shaft 30 is about 300 mm and the flight depth is about 130 mm. Thus, the ratio between the diameter of the shaft and the flight depth is about 2.3. In accordance with alternative arrangements, the shaft diameter and the flight depth may have values different from those mentioned above; thus, the ratio between the shaft diameter and the flight depth may be different; for example, for a harvester of the type CNH, a ratio of 3 may be suitable.

In accordance with the present embodiment of the invention, the overall diameter E of the feeder drum 26 is configured depending on the particular type of harvester front onto which the feeder drum 26 will be installed. Figure 8 shows the particular values of overall diameters E of feeder drums 26 to be mounted in different types of harvester front.

The flight depth can vary depending on the specific diameter that a shaft 30 of the feeder drum 26 needs to have in order to operate on a particular front attached to a particular harvester 10.

The feeder drum 26 shown in the Figures can have an overall diameter (referred herein as 'overall diameter' of the feeder drum 26) of about 560 mm, which is particularly appropriate for MacDon D60 and D65 models, older MacDon models and some Honeybee models. Alternatively, the overall diameter can be about 650 mm, which is particularly appropriate for CNH harvester fronts.

Further, in the feeder drum 26, the diameter of the shaft 30 is relatively small compared with that in conventional feeder drums, and flight depth and degree of finger extension ("effective length" of the fingers) are relatively large compared with those in conventional feeder drums, promoting comparatively effective engagement and movement of crop material as described previously. A further benefit is that there is a taller gap between the shaft 30 and the floor or platform under the feeder drum, allowing more bulk of crop material to flow unimpeded under the shaft and through to the feeder house opening.

It is important to note that in conventional feeder drums, the ratio between the overall diameter of the feeder drum 26 and the diameter of the shaft 30 is typically around 1.57 - i.e. (550)/(350). In contrast, as mentioned above, that ratio in feeder drums 26 in accordance with particular embodiments of the invention ratio is 1.67 to 1.87, as shown in figure 8.

Further, in conventional draper front feeder drums, the ratio between the shaft diameter and the flight depth is typically about 3.5 (for example, 350mm/100mm). In contrast, as mentioned above, that ratio in feeder drums 26 in accordance with particular embodiments is 2.3 to 3.

As shown in, for example, figure 6, in accordance with the present embodiment of the invention, the feeder drum 26 comprises four rows 34 of fingers 28, which can reciprocate relative to the surface of the shaft between extended and retracted conditions, though the number of rows may, without departure from the invention, vary according to factors such as the rotational speed of the feeder drum 26 during operation of the feeder drum 26, and the desired finger spacing within each row.

The rows 34 are equally spaced around the circumference of the shaft 30, neighbouring rows of fingers 34 in the present embodiment being spaced apart by an azimuthal angle of 90 degrees around the shaft 30.

Furthermore, as shown in figure 6, the fingers of neighbouring rows are offset with respect to each other along the length of the shaft 30. Further, each row 34 extends from a location in one of the opposed end sections 41 of the shaft 30 to a location in the other of those end sections.

The fact that the rows 34 extend between locations in the end sections 41 results in rows 34 being are intersected by the flights 32 as can be seen, for example, in Figure 6.

In each row 34, the fingers are arranged in a straight line which extends parallel to the shaft axis. That the rows are parallel to the axis is advantageous because the engagement of crop material by the fingers acts to move that material rearwardly, rather than in a direction having a lateral component, as is consistent with fingers arranged, for example, in one or more helices extending around and along the shaft (in an auger-like configuration).

Further, the number of fingers 28 in feeder drum 26 is relatively large when compared to the number of fingers in conventional draper front feeder drums which comprise such fingers.

In a particular arrangement, there are 25 fingers in the shaft 30. Each row of fingers 28 extends along a particular section of the shaft 30. This particular section has a length of about 1.3 meters with a finger density of about 20 fingers per metre and neighbouring fingers in each row are spaced apart about 200 mm. In accordance with the present embodiment of the invention, the finger density will not vary depending on the length that each row of fingers 28 has.

The length of the particular sections having fingers 28 extending along the shaft 30 may vary. For example, in the particular arrangement shown in the figures 2 to 6, the flights 32 intersect the rows 34 at particular locations as depicted in Figure 6. Alternatively, the rows 34 may extend from the first end 33a of the shaft 30 to the second end 33b of the shaft 30. In the feeder drum 26, in which the flights 32 define a sectional threaded-like formation around the feeder drum 26 by extending substantially along the entire length of the feeder drum 26, the flights 32 may intersect the rows 34 at more locations when compared to the feeder drum 26 shown in Figures 2 to 6. In a particular arrangement, the finger density (number of fingers/length) is of the order as mentioned in the previous paragraph: about 20 fingers per metre.

Furthermore, as mentioned before, the fingers 28 are adapted to reciprocate between extended and retracted conditions, the reciprocation being effected by at least one mechanism, e.g. crankshaft mechanism, operable by rotation of the shaft 30. To this end, the shaft 30 is hollow, defining a barrel or tube, containing the mechanism(s).

Crankshaft mechanisms for driving retractable fingers in feeder drums and their manner of operation are well known to persons skilled in the art. Any suitable crank shaft mechanism may be incorporated in the feeder drum 26 in accordance with the present embodiment of the invention. Broadly speaking, in particular crankshaft mechanisms, the fingers 28 are rotatably journaled by cylindrical bearings to a finger shaft. The finger shaft is eccentrically disposed within the shaft 30 and its ends connected via crank arms to shafts rotatably attached to walls within the shaft 30. One of the shafts is operatively connected to a locking mechanism to prevent rotation of the finger shaft in relation to a frame to which the shaft 30 is attached.

Rotation of the feeder drum 26 is synchronised with the operation of the crankshaft mechanism. Synchronisation, is necessary to ensure that for varying climatic, field and crop conditions. The synchronisation can be adjusted, so as to vary the "timing" of the mechanism, i.e. the rotational position that each row assumes, in its circular trajectory around the axis of the shaft during rotation thereof, when the fingers in that row are fully extended, in order to suit such conditions. The feeder drum 26, to this end, includes a suitable timing adjustment provision/mechanism known to persons skilled in the art, such provision/mechanism typically permitting rotation of the crankshaft to a particular angle wherein the crankshaft and the feeder drum 26 are synchronised to ensure that the fingers reach maximum extension at an optimal point of rotation in order to engage with the crop material in front of the feeder drum and/or are fully retracted at a suitable point of rotation in order to release the crop material for delivery into the rear opening. Upon completion of synchronisation, the timing mechanism/provision may be secured or locked to preclude rotation of the crankshaft and thus keep the fingers 28 correctly timed.

Advantageously, the pulling action of the fingers on the crop material, owing to their being arranged in rows, is considerable, particularly as compared with that of fingers arranged in a spiral or screw pattern in conventional feeder drums, which can act as an auger which shifts the crop material sideways, rather than to drag the crop material under the shaft. The relatively large number of fingers, as compared with that in conventional drums, also, advantageously, contributes to their pulling action. In addition, the relatively large ratio of the length of the fingers when extended to the shaft diameter, as compared with that in conventional drums, also, advantageously, contributes to their pulling action. Also, the regular distribution of the fingers over the area of the shaft which they occupy, advantageously, renders their grabbing action relatively consistent, particularly as compared with conventional feeder drums in which the fingers are arranged in spiral or screw patterns or irregularly distributed generally.

The relatively small shaft diameter as compared with that in conventional draper front feeder drums, advantageously, reduces impedance to the flow of bulky crop material through the gap between the shaft and the floor on which the crop material rests.

In addition, the relatively large ratio of the depth of the paddles and flighting to the shaft diameter, as compared with that in conventional draper front feeder drums, advantageously, contributes to the grabbing action of the feeder drum.

In a particular arrangement, the timing mechanism/provision is arranged to permit rotation of the crankshaft to any one of plural locations within a 360-degree range such that the crankshaft mechanism is properly timed.

Modifications and variations as would be apparent to a skilled addressee are deemed to be within the scope of the present invention.

Further, it should be appreciated that the scope of the invention is not limited to the scope of the embodiments disclosed. By way of example, in alternative arrangements of the present embodiment of the invention the screw flights 32 may extend a shorter length than is shown in the Figures, and the rows of fingers may also extend a shorter length than is shown or up to the full length of the shaft 30.

Throughout this specification, unless the context requires otherwise, the word "comprise" or variations such as "comprises" or "comprising", will be understood to imply the inclusion of a stated integer or group of integers but not the exclusion of any other integer or group of integers.

Claims

CLAIMS:

1. A feeder drum, for use in a harvester draper front for cutting and collecting crop material, the front including a rear opening arranged such that crop material cut by the front is transferred therethrough so as to be delivered to a feeder house of the harvester, the feeder drum comprising: a shaft which has a central axis and is mountable in the draper front so as to be rotatable about the central axis, the shaft having opposed end sections and a centre section located between the end sections, and being dimensioned such that the centre section is arranged in front of said opening when the shaft is mounted; flighting on the end sections to direct crop material received into the draper front laterally inwardly towards a position below the centre section as the shaft rotates; paddles on the centre section and projecting therefrom, the paddles extending diagonal to the central axis and being arranged to either side of a plane which is perpendicular to said axis and which, when the shaft is mounted in the draper front, passes substantially centrally through said opening, such that surfaces thereof are arranged to contact cut crop material lying below the centre section so as to urge it towards said opening as the shaft rotates; fingers mounted at distributed positions along and around the shaft; and a mechanism which is configured to reciprocate the fingers, as the shaft rotates, such that each finger assumes an extended condition during downward movement thereof, so as to penetrate crop material received into the draper front and urge that material under the shaft, and assumes a retracted condition during rearward movement thereof, so as to separate from that material, wherein the fingers are dimensioned such that each projects from the shaft a distance equal to at least a third of a diameter of the shaft when in its extended condition.
2. A feeder drum according to claim 1, wherein each paddle is a flight and a leading edge thereof is curved and/or inclined whereby a degree of engagement between the paddle and crop material in front of and/or below the centre section increases progressively as the shaft rotates. 3. A feeder drum for a draper front to be attached to a harvester, the feeder drum comprising: a rotatable drum; flights extending along the length of said rotatable drum, the flights being arranged in a spaced apart relationship with respect to each other and comprising: outer flights located adjacent ends of said rotatable drum; and a plurality of inner flights, which is located between said outer flights, the inner flights comprising paddle flights to increase crop material grabbing and feeding action in the area located between the outer flights, and to prevent build-up of accumulated stationary crop material under a centre of said rotatable drum by an effect of wiping the floor under the rotatable drum with every revolution of the rotatable drum; and a plurality of rows of fingers, the rows being arranged in a spaced apart relationship with respect to each other and surrounding said rotatable drum, the fingers being movable from a retracted condition to an extended condition to grab and pull the crop material for delivery into a feeder house of the harvester.
4. A draper front comprising: a rear opening; and a feeder drum according to claim 3, wherein the feeder drum is located adjacent the rear opening such that said delivery is through the rear opening.
5. A draper front comprising a feeder drum according to claim 1 or 2, wherein the shaft is mounted so as to be rotatable about said central axis and such that the centre section is arranged in front of said opening and said plane passes substantially centrally through said opening.