WO2015089574A1

WO2015089574A1 - A cutting apparatus

Info

Publication number: WO2015089574A1
Application number: PCT/AU2014/050350
Authority: WO
Inventors: Raymond Charles HICKLING
Original assignee: Hickling Raymond Charles
Priority date: 2013-12-17
Filing date: 2014-11-13
Publication date: 2015-06-25
Also published as: AU2014366826B2; BR112016013501B1; AU2014366826A1

Abstract

A cutting apparatus is disclosed which is operable to receive a moving feed of material, wherein the material is to be cut into pieces by the cutting apparatus. The cutting apparatus includes a fixed portion over which the material passes, and a rotating portion. The rotating portion includes at least one rolling cutting element that moves in an orbit around the rotating portion's axis of rotation when the rotating portion rotates. The orbit of each cutting element is at an angle to the direction in which the material passes over the fixed portion. For at least part of each revolution, each cutting element contacts the fixed portion and rolls along or relative to the fixed portion thereupon cutting the material passing over the fixed portion.

Description

A CUTTING APPARATUS

TECHNICAL FIELD

[0001] The present invention relates to cutting apparatus. For convenience, the invention will be described mainly with reference to apparatus and machines for cutting harvested crops, and particularly apparatus and machines for cutting harvested sugar cane. However, it is to be clearly understood that no limitation is necessarily to be implied from this, and the invention could potentially also be used in, or applied to, cutting other types of crops, or indeed for cutting products or things other than harvested crops. The invention might also be embodied in, or as part of, some other piece of equipment or machine (e.g. as part of a sugar cane harvester), or alternatively as a separate or standalone apparatus or machine.

BACKGROUND

[0002] Traditionally, sugar cane harvesters have fallen into two general types, namely whole stalk harvesters and chopper harvesters. Whole stalk harvesters, as the name suggests, retain the harvested cane stalks in their whole length form. In contrast, chopper harvesters cut the cane stalks into small pieces (called billets) which are then transported to the sugar mill in bin-type containers. Chopper harvesters have been more widely accepted, particularly in developed countries, due at least in part to their ability to better handle lodged crops and also unburnt crops. Providing harvested sugar cane in the form of billets rather than as whole stalks i also often preferable from the point of view of efficient transportation (e.g. in transporting the harvested crop to the mill), as this generally allows a greater mass of harvested cane to be transported in a given container/receptacle volume (because the smaller billets are generally able to more fully fill the container/receptacle than full stalks).

[0003] The cut and feed mechanism leading up to the billet cutting mechanism is generally similar in most chopper harvesters. In most cases, spiral crop dividers separate the row of crop/cane being cut from the next/adjacent standing row. As the harvester moves forward, knockdown rollers incline the stalks forward while the stalks are still attached to the ground. Twin counter-rotating base cutter discs then sever the stalks at (or just above) ground level. The butts of the stalks are then lifted by a butt- Sifter leading them into the roller feed train. Passage of the stalks into the feed train is also assisted by the rotating knockdown rollers. A continuous moving mat of cane Is fed into the billet chopping mechanism via the roller feed train.

[0004] One (perhaps the most) commonly used chopping mechanism is a rotary chopper. (The cutting method implemented by a rotary chopper is often termed the "rotary chop"). A rotar chopper system generall has two contra-rotating drums. Around the circumference of each drum are two or more vertically standing, equally spaced knives. The two contra-rotating drums are timed so that opposing knives on each respective drum overla and lightly touch at their bevelled/sharpened edges. This overlapping touch action provides a degree of self-sharpening. This is commonly called a pinch cut. One of the advantages of rotary choppers is that their rotary action is in general harmony with the continuous moving mat of cane. Another advantage of rotary choppers is that some biilets exiting the upper drum are flicked slightly upwards whilst some exiting the lower drum are flicked slightl downwards. This can help to open up the parcel (or the dispersal pattern) of the billets, which in turn assists with airflow removal of leaf material and other extraneous matter ("trash").

[0005] One problem associated with the use of airflow cleaning to separate the trash from the billets is that, if the airflow is created by sucking or extracting the air (as it often is), the trash exiting the billet flow stream can carry some billets with it. In other words, some biilets can become caught u or entangled with trash exiting the flow stream, and these billets then exit the flow stream with the trash as waste. It will be appreciated that this results in cane losses (i.e. loss of valuable cane billets which preferably would all be captured). For this reason, where airflow cleaning is used, the power of the extracting fan (or other airflow mechanism) and hence the strength of the airflow, is often regulated in order to achieve a compromise between acceptable cane losses and acceptable extraneous matter (trash) levels remaining in the harvested cane billets.

[0006] One of the disadvantages of rotary choppers is that, when the knives initially make contact with the moving cane mat, they are not perpendicular to each other. In other words, when two corresponding apposed knives initially make contact with the cane mat, the direction of movement of one knife relative to the other is not perpendicular at the point of contact therebetween on the knives' edges. This means that the two knives effectively come together initially at an angle. As the knives move together as the cut is performed, this angle diminishes. Nevertheless, the direction of relative movement between the knives generally only reaches perpendicular once the cut has been completed. Consequently (and due at least partly to the fact that the two knives engage each other at an angle through most of the cut), there is a squeezing action that occurs (i.e. squeezing of the cane) during the cut. This squeezing/compression of the cane can result in a degree of mutilation of the cane, and hence some juice loss from the cane, which is of course undesirable.

[0007] Another method of chopping which has been used, namely the so-called "swinging knife" system/method, consists of a shaft positioned roughly parallel with the feed train and having one or more knives protruding at right angles to the rotating shaft. An anvil is positioned either vertically or horizontally over which the mat of moving cane continuously passes. The rotating knife passes close to or lightly touches the anvil. It will be appreciated that the sharpened edge of the knife in this arrangement moves much faster at its outer (distal) end in comparison with its (inner/proximal) end closer to the shaft. This means that the cut is more effective at the outer (distal) end. Also the blade at the outer end moves out of the path of the moving cane mat more quickly than the inner end. Hence the inner end tends to obstruct free movement of the cane mat, at least more so than the outer end. With this general arrangement, the cut would be cleaner if the cane mat were stationary when the cut is performed (but of course the cane mat is moving, not stationary). There is also little self-sharpening effect with this system. Consequently, the blades must generally be sharpened frequently. This system has previously achieved some popularity, particularly in burnt crops, largely due to its simplicity. However, in unburnt crops, the rotary chop (discussed above) has proven superior and consequently is probably more commonly used.

[0008] As mentioned above, after the cane stalks have been chopped into billets, and after the billets exit the chopper, they are normally subject to airflow cleaning. The airflow is normally created by an extractor fan positioned above the billet flow. The airflow causes the miscellaneous leaf matter (trash) to be sucked upwards out of the billet flow stream. The billets, with most of the trash thus removed by the airflow, then fall into the boot of a conveyor elevator. The conveyor elevator, which normally consists of sprockets, chains and flights, conveys the billets upward and outward ultimately ejecting them into bin or receptacle which is "shadowing" the harvester. Often, the said bin/receptacle will take the form of a trailer being towed by a tractor or truck, or perhaps a cage-type receptacle on the back of a truck, etc. In any case, the tractor/truck "shadows" the harvester by moving along and keeping pace with the harvester such that billets ejected from the conveyor elevator of the moving harvester are caught in the contemporaneously moving receptacle. [0009] Another previously-proposed method of billet chopping is the so-called chop throw system. In a chop throw system, the chop (i.e. the method by which the cane is cut) is similar to that of the swinging knife system described above in that the knife passes over a horizontal anvil. However, in addition to this in a chop throw system, a paddle is positioned parallel to the driveshaft and travels behind and drives rotation of the knife. Early machines embodying the chop throw system consisted of two knives which, together with their respective correspondirig paddies, were positioned roughly diametrically opposite each other on a common shaft. A curved plate, with the curve having an inner shape corresponding to the outer radius of the arc swept by the paddles (such that the curved plate effectively partly surrounded the rotating paddles), ensured that the billets would be contained within the said radius and pushed around the curved plate to a point where the curved plate terminated, at which point the billets would be thrown upwards and/or outwards. Side plates attached on either side of the curved plate created a trough out of which the billets could not escape until they reached the said endpoint of the trough. The billets were generally thrown up a chute and Into a transport bin. A blower created airflow down the chute in a direction generally against the direction of travel of the billets. This provided quite effective cleaning as the light- weight/low-density leaf material (trash) would be rapidly decelerated and expelled by the airflow, whereas the heavier/denser cane billets (with their resultant much greater momentum) would continue to travel against through the flow of air and out of the harvester. Other chop throw systems have also been developed,

[0010] It has been demonstrated that, using a chop throw system, cleaning can be quite effective and can achieve relatively low cane losses. However, with previously- proposed chop throw systems, billet quality has generally been poor in comparison with rotary chop systems, Attempts to combin the rotary chop with a throw system have not proven successful. Tests have shown that billet damage can be attributed more to the cut than the throw. As mentioned above, the rotar chop can give rise to squeezing of the cane (and consequently juice loss), and the swinging knife would have better results if the cut were performed on a stationary mat rather than a moving mat. Also, with chop throw systems, the kinetic energy present in the rotating knife paddle assembly has proven to be difficult to tame/accommodate if the knife strikes a foreign object such as a stone, steel, timber or the like. Damage caused by foreign matter is also of concern in the rotary chop, but perhaps to a lesser extent than in a chop throw system. Another disadvantage of previous chop throw systems was the inability to deliver cane to the left or the right of the machine, which is considered highly desirable.

[001.1] Whilst harvester designs employing a rotary chop system have found wide acceptance, this type of chopper is also not without shortcomings. With most such harvester designs, it is a requirement to deliver cane into a transport bin which is "shadowing" the harvester. When the harvester incorporates rotary choppers, the rotary choppers are normally positioned relativefy high, often above the level of the rear wheels. This is so that the billets, as they are ejected from the choppers, have room to fall into the collection boot of the elevator which is positioned behind the rear wheels. It is also normally a requirement for the elevator to be able to rotate 180° about a vertical axis in order to allow left or right delivery (i.e. in order to allow billets to be ejected to either the left-hand side or the right-hand side of the moving harvester). The elevator is also quite heav in construction having (as mentioned above) shafts, sprockets, conveyor chains, flights, etc. In addition, a secondary extractor is usually attached on top of the elevator. This all causes the considerable weight of the elevator (including the secondary extractor) to be cantilevered relative to the harvester, and generally this weight becomes concentrated significantly over the rear wheel (s) on the discharge side of the harvester. The relatively high position of the rotary choppers (as mentioned above) further necessitates a fairly steep incline in the roller feed train. Considered together, these factors often result in the centre of gravity of the harvester being quite high. And this high centre of gravity combined with the heavy elevator (including the secondary extractor) which, as mentioned above is cantilevered to one side, can lead to stability problems for the harvester. In an attempt to counter such stability issues, it has been known to add water to the harvester's rear tyres and/or to use heavy ply tyres with high inflation pressures. However, this can in turn lead to poor flotation of the tyres over the soil, and consequently poor harvester mobility, especially in wet conditions. In some areas where rubber tyres are not suitable, harvesting machines are supplied on full tracks. This adds greatly to capital costs, maintenance costs and transport costs. Nevertheless, the considerable weight of harvesters, and the poor weight distribution issues discussed above, are increasingly preventing harvesters from being equipped with flotation agricultural tyres, and as a result the considerably more expensive full track alternative is becoming more widespread despite the cost.

[0012] It would appear to be desirable to overcome, or at least reduce the effect/impact of one or more of the problems or difficulties discussed above. [0013] It is to be clearly understood that mere reference herein to previous or existing apparatus, products, systems, methods, practices, publications or othe information, or to any problems or issues, does not constitute an acknowledgement or admission that any of those things individually or in any combination formed part of the common general knowledge of those skilled in the field, or that they are admissible prior art.

SUMMARY OF THE INVENTION

[0014] The present invention, in one form, relates broadly to a cutting apparatus operable to receive a flow (or a moving feed) of material, wherein the material is to be cut into pieces by the cutting apparatus, the cutting apparatus including:

a fixed portion over which the (flow or feed of) material passes, and

a rotating portion,

wherein

the rotating portion includes at least one rolling cutting element that moves (or is swept) in an orbit around the rotating portion's axis of rotation when the rotating portion rotates,

the orbit of each cutting element is (in a plane which is) at an angle to the direction in which the material passes over the fixed portion, and

for at least part of each revolution, each cutting element contacts the fixed portion and rolls along or relative to the fixed portion thereupon cutting the material passing over the fixed portion.

[0015] The cutting apparatus in the form of the invention mentioned above could be embodied in, or as part of, some larger or other piece of equipment or machine (e.g. as part of a sugar cane harvester, if the material is sugar cane to be cut into billets). Alternatively, it could be embodied as some other form of separate or standalone apparatus or machine.

[0016] As mentioned above, embodiments of the present cutting apparatus are operable to receive a flow of a material which is to be cut into pieces, in this regard, the word "flow" does not mean that the material must liquid or "fiowable". Rather, it is intended to convey that the cutting apparatus is operable to receive a moving feed of the material, which may often be (or be made up of) a form of solid material (e.g. sugarcane). The moving flow or feed of materia! need not be a perfectly continuous feed (i.e. it need not necessarily move at a constant flow/feed rate, although of course it could do), In some cases, the flow may be delivered in such a way that it is received by the cutting apparatus in a staggered or "stop start" manner, or the speed or rate of the flow may vary. Those skilled in the art will recognise that the speed at which the material passes over the fixed portion of the cutting apparatus, in combination with the rotational speed of the cutting apparatus's rotating portion, will affect the size of the pieces into which material is cut. Generally, increasing the speed at which the material passes over the fixed portion will increase the size of the pieces into which material is cut, but on the other hand increasing the rotational speed of the cutting apparatus's rotating portion will decrease the size of the pieces into which material is cut.

[0017] In relation to the material itself, this could be e.g. a harvested crop such as full stalks of sugarcane which are to be cut into pieces {billets). However, no limitation whatsoever is to be implied from this particular example, and the material could indeed be any kind of material which is to be cut or chopped into pieces.

[0018] The cutting apparatus includes a fixed portion over which the material passes, and a rotating portion. In relation to the fixed portion, the term "fixed" does not mean that this part of the apparatus must remain absolutely stationary. For example, if the cutting apparatus is provided as part of a moving cro harvesting machine, the fixed portion may well move when the harvester moves (i.e. it may move with the harvester). Therefore, "fixed" in the present context means that this portion of the cutting apparatus remains (at least generally) stationar relative to the cutting apparatus as a whole, and the moving flow/feed of material moves/passes over/across this portion as it is received by end enters the cutting apparatus.

[0019] In relation to the rotating portion of the cutting apparatus, as mentioned above, this includes at least one rolling cutting element that moves in an orbit around the rotating portion's axis of rotation. The orbit of each cutting element is at an angle to the direction in which the material passes over the fixed portion, and for at least part of each revolution each cutting element contacts the fixed portion and rolls along or relative to the fixed portion cutting the material which is then passing over the fixed portion. Such a configuration may be embodied in range of different ways, all of which are considered to fall within the scope of the present invention.

[0020] In some embodiments, the fixed portion of the cutting apparatus may comprise an anvil. Also, in some embodiments, the rotating portion of the cutting apparatus may include multiple roiling cutting elements. The multiple rolling cutting elements may be similar or identical to each other (such that their respective weights and moments of inertia about the rotating portion's axis of rotation are similar or the same), and they may be equally spaced around the rotating portion's axis of rotation (such that the rotating portion is balanced when it rotates).

[0021] In some particular embodiments, each of the roiling cutting elements may be, or may include, a substantially (or generally) disc shaped cutting coulter, In this regard, by way of background, a coulter is generally a round disc (often a flat disc, although some coulters have a zigzag or other shape out of the plane of the main disc shape) with a sharpened edge (or edges) around its perimeter. A coulter is generally free rolling, often around an axel (or the like) at its centre. Coulters have bee used in agricultural industries for decades, and are commonly used to cut a path through surface crop residue or other vegetation to allow a non-residue gathering passage by a plough shear or tyne. Coulters have been used extensively in the sugar industry to cut a path through the thick mat of cane trash often left behind during green cane harvesting to allow the passage of a ripper tyne or a tyne to place fertiliser or chemicals below the surface. Coulters have stood the test of time, and they are fairly forgiving of obstacles in their path, even stones. This is because of their roiling cut action. More specifically, a coulter generally has the ability to roil up and over an obstacle without sustaining damage (or only little/minimal damage).

[0022] In embodiments of the invention where each of the rolling cutting elements is, or includes, a coulter, each coulter may be mounted on or relative to a respective radiall oriented radial member (e.g. a radial spindle). Each radial member (spindle) may be part of the cutting apparatus's rotating portion, and each coulter may be able to rotate relative to its associated radial member (spindle). Each coulter may also be able to move radially inward and outward relative to its associated radial member (i.e. each coulter may be able to move radially inward toward, and outward away from, the rotating portion's axis of rotation) when the rotating portion is rotating at or above a predetermined (or a certain minimum) rotational speed. However, when the rotating portion is stationary or rotating below the predetermined/minimum rotational speed, each coulter may be held in position toward the radially outer end of its associated radial member (this may prevent the coulter from moving radially inward relative to its associated radial member). The means by which each coulter is held in position toward the radially outer end of its associated radial member when the rotating portion is stationary or rotating below the predetermined/minimum rotational speed may include a component which is biased (by a spring or any other biasing means) towards a position which causes the coulter to be held toward the radially outer end of its associated radial member, but when the rotating portion is rotating at or above the predetermined/minimum rotational speed the bias on the said component is overcome by centrifugal forces causing the said component to move in such a way that the component does not cause the coulter to be held towards the radially outer end of its associated radial member. Means may also be provided for adjusting the axial and/or radial position of each coulter (e.g. so that the coulters, as they wear, can be adjusted to still ensure cutting contact with the anvil during the relevant portion of each revolution).

[0023] As has been described, the rotating portion of the cutting apparatus includes at least one roiling cutting element (which may be a coulter) that is moved/swept in an orbit around the rotating portion's axis of rotation when the rotating portion rotates. Also, the orbit of each cutting element (coulter) is at an angle (or in a plane which is at an angle) to the direction in which the material passes over the fixed portion (anvil). In some embodiments, the orbit of each coulter may be (at least approximately) perpendicular to the direction in which the material passes over the fixed portio (anvil), but each coulter may also be oriented at an angle relative to the plane of the orbit such that each coulter cuts through the materia! at an angle which is not precisely perpendicular to the direction in which the material passes over the fixed portion (anvil). Preferably, each coulter may cut through the material at an angle which at least slightly accelerates the material in the material's direction of travel. This may help to maintain the flow/feed of the material, and to prevent blockage/disruption (even temporary) of the flow/feed of material. Means may be provided for adjusting the angle of orientation of each coulter relative to the plane of the coulter orbit. Any suitable means or mechanism or configuration may be used for this.

[0024] In some embodiments, the cutting apparatus may further include at least one sweeping component that is moved or swept in an orbit around the rotating portion's axis of rotation when the rotating portion rotates. Each sweeping component may contact with material that has been cut by the cutting eiement(s) and convey the cut material away from the fixed portion (anvil). Preferably, the cutting apparatus may include a sweeping component associated with each coulter, wherein each sweeping component is moved or swept in an orbit around the rotating portion's axis of rotation when the rotating portion rotates, and each sweeping component contacts with material that has been cut by one or more of the coulters and conveys the cut material away from the anvil. In these embodiments, each sweeping component may comprise a paddle component with at least one contact surface, and when the paddle component is moved/swept in an orbit around the rotating portion's axis of rotation, it's contact surface may collide with material that has been cut by one or more of the coulters and convey the cut material away from the anvil. In certain particular embodiments, at least one of the paddle components may be operable to pivot such that, in the event of a foreign object passing over the anvil, the paddle component pivots upon contact with the foreign object (and hence moves over or past the foreign object) rather than sustaining damage (or more significant damage) upon collision with the foreign object.

[0025] In embodiments of the cutting apparatus which include one or more sweeping components, as described above, the apparatus may further include a trough and a chute. Material cut by one or more of the coulters may fail into and/or collect temporarily in the trough. The trough may be curved with radius corresponding to the outer radius of the orbit swept by one or more paddies. One or more of the paddles may sweep through the trough whereupon the contact surface(s) thereof may collide with cut material and convey the cut material around the trough until the trough opens into the chute whereupon the cut material may separate from the paddle(s) and travel into the chute, exiting the cutting apparatus through the chute. The chute may include one or more of the following: means for allowing or causing the cut material to exit the chute at different points on or along the chute; means for altering the trajector or direction with which cut material exits the chute; and means for enabling a small amount of material to be temporarily retained in (o collected or stored in) the chute.

[0026] As mentioned above, in some embodiments, the fixed portion of the cutting apparatus may comprise (i.e. it may be or it may include) an anvil. The anvil ma have a contact edge or surface along or relative to which each cutting element (coulter) roils or rotates when in contact with the anvil. The said contact edge or surface may be curved with a radius substantially corresponding to the outer radius of the coulter orbit. Where this is the case, the cutting apparatus may also include a profile converter operable to shape the flow (or feed) of material to conform (at least generally/approximately) to the shape of the contact edge or surface of the anvil before or as the material passes oyer the contact edge or surface. The profile converter may have an inlet which is shaped to receive the flow (feed) of material and an outlet which is shaped to conform (at least generally/approximately) to the shape of the contact edge or surface of the anvil, and when the flo (or feed) of material passes through the profile converter it may be squeezed into the shape (or at ieast the general shape) of the outlet such that it exits the profile converter in a shape conforming generally to the shape of the contact edge or surface of the anvil.

[0027] It is envisaged that, in many possible embodiments, the materia! to be cut into pieces by the cutting apparatus will be a harvested crop material, in which case the feed of material entering the cutting apparatus will contain the harvested crop and also leaf matter and/or other unwanted matter. Both the harvested crop and also the unwanted leaf/other matter will be cut into pieces by the cutting apparatus and conveyed around the trough and into the chute, as described above. In such embodiments, the apparatus may further include a blower associated with the chute. The blower may be operable to blow air into and/or through the chute in a directio at !east partly transverse to the trajectory of the pieces of harvested cro and unwanted leaf/other matter in the chute, and this flow of air may cause the pieces of unwanted ieaf/other matter to separate from the pieces of harvested crop such that the pieces of harvested crop exit the chute separately from the pieces of unwanted leaf/other matter.

[0028] An of the features described herein can be combined in any combination with any one or more of the other features described herein within the scope of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Preferred features, embodiments and variations of the invention may be discerned from the following Detailed Description which provides sufficient information for those skilled in the art to perform the invention. The Detaiied Description is not to be regarded as limiting the scope of the preceding Summary of the Invention in any way. The Detailed Description will make reference to a number of drawings as follows:

[0030] Figure 1 is a side-on view of a sugarcane harvester in which one possible embodiment of the invention is utilised.

[0031] Figure 2 shows the forward portion of the harvester in Figure 1 partially disassembled and with certain parts hidden to reveal other parts.

[0032] Figure 3 is a perspective illustration of the harvester, shown from behind and to the right-hand side. Figure 3 illustrates, inter alia, the harvester's chute configured to deliver billets to the right-hand side of the harvester. Some parts of the harvester are hidden in Figure 3 to reveal other parts.

[0033] Figure 4 is a close-up view of certain important components of the chop throw mechanism.

[0034] Figure 5 illustrates the cane mat profile converter and anvil.

[0035] Figure 6 shows the chop throw mechanism and chute.

[0036] Figures 7 and 8 are (approximately) side-on views of the chop throw mechanism.

[0037] Figure 9 is an exploded view of three groups of components (or subassemblies) which together make up the chop throw mechanism.

[0038] Figures 10 and 1 1 are side-on views of the chop throw mechanism.

[0039] Figure 2 also shows the chop throw mechanism, but from a slightly behind and to one side.

[0040] Figure 13 illustrates the coulter hub and the spindles to which the respective coulters (and other related components) are mounted.

[0041 ] Figure 14 is an exploded view of one of the coulter assemblies. Nqtabiy, Figure 14 shows the keeper arm in the orientation it adopts when the coulter assembly is (assembled and) stationary or at low rpm.

[0042] Figure 1 5 shows the coulter assembly of Figure 14 assembled. Figure 15 also shows the keeper arm in the configuration it adopts when stationary or at low rpm.

[0043] Figure 16 is a view of the harvester from one side, with a number of parts hidden to reveal other parts, and showing components which allow the trough (etc) to be converted for either left-hand side or right-hand side delivery.

[0044] Figure 17 is similar to Figure 15 in that it shows an assembled coulter assembly. However, unlike Figure 15, Figure 17 shows the keeper arm in the configuration it adopts when the chap throw mechanism is rotating at high rpm, such as at operating speed.

[0045] Figure 18 is similar to Figure 14 in that it shows an exploded view of a coulter assembly. In Figure 18, the keeper arm of the coulter assembly is shown in the open position which it adopts when the chop throw mechanism is rotating at high rpm such as at operating speed.

[0046] Figure 19 is a cutaway and pictorial illustration of the operation of the chop throw mechanism, chute and blower.

DETAILED DESCRIPTION

[0047] As mentioned above, Figure 1 is a side-on view of a sugarcane harvester 10 in which one possible embodiment of the presently-proposed chop throw system/mechanism is utilised. This harvester 10, which is also shown in various ways and views in other Figures, is a harvester which has been custom-designed to accommodate and operate with the particular embodiment of th chop throw mechanism discussed below and shown in other Figures. However, it is to be clearly understood that the scope and application of the invention is in no way limited to use or implementation in such (or similar) custom-designed harvesters. On the contrary, the proposed chop throw system/mechanism, whether in accordance with the particular embodiment shown and discussed below or another embodiment of the invention, may be incorporated in any suitable harvester design. It should also be recalled that whilst the invention is described herein mainly with reference to the harvesting of sugarcane, nevertheless the invention could potentially also be used in, or applied to, harvesting machines or apparatus for other crops or cutting apparatus of other types.

[0048] Referring to the Figures, it can be seen from Figures 1 -3 in particular that the harvester 10 has a crop divider mechanism 12 on the front. The operation of the crop divider mechanism 12 in gathering standing cane stalks, and also the way in which the standing stalks are severed at ground level and then conveyed as a continuously moving mat of stalks to the chopper via the roller feed train, is mostly similar to the wa this is done in other harvesters. However, the wa in which the cane is cut into billets, and the way in which the billets are conveyed into a shadowing transport unit, are not conventional and will be discussed further below. Nevertheless, before discussing the proposed chop throw mechanism in detail, it is useful to provide an overview of the crop divider mechanism 2 and the feed train.

[0049] The cro divider mechanism 1 includes four spiral crop dividers. More specifically, there are two inner spiral crop dividers 14 and two outer spiral crop dividers 16. The spiral crop dividers separate the row of standing cane being cut from the next adjacent standing row. As the harvester moves forward, knockdown rollers 1 7 incline the stalks forward while the stalks are still attached to the ground. Counter- rotating discs associated with a respective pair of basecutters 19 then sever the stalks at (or just above) ground level. The butts of the stalks are then Sifted by a butt-lifter roller 21 leading them into the roller feed train. Passage of the stalks into the feed train is also assisted by the rotating knockdown rollers 17. As a result, a continuous moving mat of cane stalks is fed into the chopper by the roller feed train as the harvester progresses down a row.

[0050] The spiral crop dividers are mounted o a crop divider frame 18. The undersides of the lowermost members of the crop divider frame 18 function as skids. These skids carry the weight of the front end of the feed train assembly. The rear of the feed train assembly is supported at pivots 20 (one on either side). The cutting height of the basecutters 19 can be adjusted by hydraulic cylinders 22 which move the basecutters 19 via the connecting linkages 23. The crop dividers 14, 16 and basecutters 19 can be raised clear of the ground by hydraulic cylinders 26 which move rockers 28. Again, there is a hydraulic cylinder 26, rocker 28, and an associated linkage, on either side. The linkage between rocker 28 and the feed train on one side can be seen in Figure 1 . The weight on the skids (recall that the skids are formed by the undersides of the divider frame 18) can be reduced by providing hydraulic accumulators associated with the hydraulic cylinders 26.

[0051] As mentioned above, after the basecutters 19 sever the standing cane stalks at their base, the butts of the stalks are lifted by butt-lifter roller 21 into the roller feed train. The driven (rotating) rollers of the roller feed train (i.e. the feed train rollers) are indicated by reference numeral 30 (see Figure 2). The feed train rollers 30 convey the continuous moving mat of cane rearward into the chopper. There is also a series of upper feed train rollers 32. As can be seen in Figure 2, each upper feed train roller 32 is mounted (and rotates within) in a hinged cradle. More specifically, the cradle supporting each upper feed train roller 32 is hinged so that the roller can raise and fall (i.e. move vertically up and down) according to the thickness of the mat of cane passing there-beneath. Hence, if the thickness of the cane mat increases, the upper feed train rollers 32 will be pushed upward by the increased mat thickness, and conversely if the cane mat thins the upper feed train rollers 32 will drop/lower back down, [0052] It should be noted, at this point, that the angle of inclination of the feed train in the depicted arrangement is comparatively gentle (i.e. not steep), This is possible due to the configuration of the chop throw mechanism (discussed below). More specifically, because the chop throw mechanism has no need for an elevator to convey the cut billets, there is therefore no need to provide a vertical gap/distance to allow cut billets to fall into a boot at the base of the elevator. Accordingly, the anvil used in the presently-proposed chop throw mechanism can be (and is) located relatively low (i.e. relatively close to the ground), thus allowing the angle of inclination of the feed train to remain comparatively gentle. This, in turn, allows for more efficient feeding of the cane stalks as well as helping to lower the overall centre of gravity of the harvester.

[0053] Adjacent the last of the lower and upper feed train rollers (30 and 32 respectively) is a cane mat profile converter 34. The profile converter 34 is the last component which the mat of cane passes ove before being cut into billets. In order to understand the configuration and function of the profile converter 34, it should first be appreciated that the profile of the cane mat as it passes through the feed train is generally rectangular. This is due, at least in part, to the fact that the mat is pressed from below by the lower feed train rollers 30 and from above the upper feed train rollers 32. Hence, the cross-sectional profile of the cane mat passing through the feed train is a generally flat rectangle, similar to the profile of a belt. However, as discussed in further detail below, the anvil 40 over which the cane mat passes as it enters the chopper is curved (the anvil 40 is curved in order to operate with the rotating coulters which, together with the anvil, cut the cane into billets).

[0054] Because the anvil 40 over which the cane mat passes as it enters the chopper is curved, the profile of the cane mat needs to change from flat to curved. This is achieved by the profile converter 34 which is clearly illustrated (together with the anvil) in Figure 5. For the avoidance of doubt, in Figure 5, the moving mat of cane moves "into the page" as it leaves the last of the feed train rollers and passes through the profile converter 34.

[0035] As shown in Figure 5, the profile converter 34 is essentially a funnel for funnelling the moving mat of cane from the feed train rollers into the chopper. At the intake end of the profile converter 34 (i.e. where the mat of cane first enters the profile converter 34 after leaving the feed train), the cross-sectional shape of the opening in the converter 34 is rectangular. This can be seen in Figure 5. However, moving through the profile converter 34 towards the outlet end, the cross-sectional shape of the space inside the profile converter transitions to become curved such that, at the outlet end (i.e. where the mat of cane exits the profile converter 34 to pass over the anvil 40), the cross-sectional shape of the converter's outlet opening is curved into a similar shape to the concave curve of the anvil 40.

[0056] Referring now to the construction of the profile converter 34, the profile converter 34 includes a lower portion 36 and an upper portion 38. The lower portion 36 has a pair of flat vertical box sides 35, and the floor of the lower portion (which extends between the vertical sides 35) is flat at its intake edge and transitions to become curved at its outlet edge (thus helping to create the transitioning "flat-to-curved" shape discussed above). A curved flange 37 depends below the curved outlet edge of the profile converter's iower portion 36, and the flange 37 is bolted directly to the anvil 40 thus connecting the profile converter 34 to the anvil 40.

[0057] The configuration of the upper portion 38 is similar to that of the Iower portion 36 in that the upper portion 38 has a pair of vertical sides, and a portion which extends between the said sides (which forms the roof of the funnelling space inside the profile converter) is flat at its intake edge and transitions to become curved at its outlet edge (thus again helping to create the transitioning "flat-to-curved" shape discussed above).

[0058] The upper portion 38 of the profile converter is hingedly connected to the lower portion 36 by a rod 39. The rod 39 extends between the upper comers of the respective sides 35 of the lower portion 36, near the intake edges of the sides 35. The upper portion 38 is therefore hinged relative to the lower portion 36. The upper portion 38 can to pivot relative to the lower portion 36 about an axis corresponding to the axis of rod .39. More specifically, the upper portion 38 can pivot from the position shown in Figure 5 in the direction indicated by arrows "A" and then back again in the opposite direction, back into the position shown in Figure 5.

[0059] A pair of springs 42 is provided, one on either side of the profile converter 34. The springs 42 are mounted in tension. The purpose/function of the springs 42 can be visualised from Figure 5 by considering that a mat of full sugarcane stalks is entering and passing through the profile converter 34 (i.e. the mat is travelling through the converter 34 in the direction "into the page" in Figure 5}. Due to the vertical thickness of the mat, the mat will generally press upward against the underside of upper portion 38 as the mat passes through the profile converter 34, This in turn causes the upper portion 38 to pivot (about the axis of rod 39) in the direction indicated by arrows "A" in Figure 5. When the upper portion 38 pivots in this way, this causes the profile converte to "open up" such that the cross-sectional area of the profile converter's outlet opening increases. In other words, when the upper portion 38 is caused to pivot du to upward pressure from the mat of cane moving there-beneath, the outlet edge of the upper portion 38 moves/pivots upwards, thus increasing the distance between the outlet edge of the upper portion 38 and the outlet edge of the lower portion 36. Hence, the cross- sectionai size of the outlet in the profile converter increases.

[0060] However, it will also be appreciated that when the upper portion 38 pivots in this way (Le. in the direction indicated by arrows "A" in Figure 5), this also causes the springs 42 to be stretched further against their natural tensile bias. Accordingly, the springs 42 simultaneously pull against the upper portion 38 attempting to pivot it back the other way (i.e. attempting to pivot the uppe portion 38 back in the direction opposite to arrows "A"). Thus, the springs 42 function to try to force the profile converter 34 "dosed". Consequently, the springs apply pressure such that the roof of the profile converter presses down on the mat of cane which is passing through the profile converter, thus helping to press the mat of cane into the ultimately curved cross- sectionai shape of the converter as the cane exits the converter to pass over the anvii 40.

[0061] The proposed chop throw mechanism will next be introduced, initially with reference to Figure 6. From Figure 6, it will first be noted that the lower portion 36 and upper portion 38 of the profile converter 34 are shown in a similar orientation to in Figure 5 (although Figure 6 is comparatively more "zoomed out" than Figure 5). The chop throw mechanism illustrated in Figure 6 can be understood by (again) considering that a moving mat of full sugarcane stalks is continuously entering and passing through the profile converter 34 (i.e. the mat is travelling in the direction "into the page" in Figure 6). The operation of the profile converter 34 is described above and need not be repeated. As the moving mat of cane exits the profile converter 34, it immediately passes over the anvil 40. More accurately, the cane mat exits the profile converter 34 and passes over a curved wear plate 44 which is attached to the concave upper edge of the anvil 40. (It will be readily appreciated that the wear plate 44 is a sacrificial part which prevents damage/wear to the anvii 40 itself, and which can be replaced periodically or as it becomes worn.) The stalks of cane which make up the moving cane mat are then cut into billets as they pass over the downstream edge of the anvil wear plate 44. In summary, the cutting is performed by a series of cutting coulters 50. The construction and operation of the coulters 50, and the chop throw mechanism generally, will initially be discussed briefly, but then described in more detail further below.

[0062] In the particular embodiment illustrated in the Figures, the chop throw mechanism includes three cutting coulters 50. Of course, in other embodiments a different number of coulters (or other cutting components/members) could be used. In any case, in the present embodiment, each coulter 50 is mounted to a radially-oriented spindle 70. The coulters 50 are able to rotate/spin relative to the respective spindles 70 to which they are mounted. In other words, the connection between each coulter 50 and its corresponding spindle 70 allows free rotation of the coulter 50. The spindles 70, at their respective radially inner proximal ends, all attach to a common coulter hub 90 which is configured to be rotated by rotation delivered from a mai drive shaft 100. (The manner in which rotation of the coulter hub 90 is caused by rotation of the drive shaft 100 is discussed further below. The d iveshaft 100 is the main drive shaft of the chop throw mechanism and is itself driven by the harvester's engine.)

[0063] In any case, it will be appreciated that when the coulter hub 90 rotates (in Figure 6 the mechanism is configured so the coulters 50 etc rotate anticlockwise as indicated by arrow "B", although the mechanism can also rotate in the opposite direction), this rotation in turn causes the respective spind!es 70, and hence the coulters 50 which are mounted on the distal ends of the respective spindles 70, to also rotate in the same direction and at the same speed. Thus, the coulters 50 rotate in a circular arc about the driveshaft 100. As the coulters 50 rotate, the respective coulters 50 pass, one after the other, along the curved edge of anvil wear plate 44. In fact, the coulters 50 contact and roll along the edge of the wear plate 44 as they pass (this is discussed further below}. It should be recalled that, as the moving mat of cane exits the profile converter, it immediately passes over this curved edge of the wear plate 44. Hence, as the cane mat moves over the edge of the anvil wear plate 44, it is chopped into small billets by the rapidly successive passes of the respective rotating cutting coulters 50. Typically, the billets are 150 mm - 200 mm long.

[0064] Importantly, there is more to the operation of the coulters and the associated mechanisms than has just been described. However, this detail will b explained further below, and the above introduction provides an overview of how the mat of cane is chopped into billets by the rotating coulters 50. [0065] Next, the paddle mechanism which performs the "throw" function in the proposed chop throw mechanism will be briefly introduced, again with reference to Figure 6, As explained above, the mat of cane stalks passes over the anvil wear plate 44 and is chopped into billets by the passing coulters 50. After being cut, the billets collect (temporarily) below the anvil in the bottom of the trough component 46. From Figure 6, it will be seen that the trough 46 extends approximately ¾ of the way around the outside circumference of the cutting mechanism, and on one side the trough 46 extends all the way up to the chute 130. The chute 130 itself, which is clearly visible in Figure 6, continues vertically up and also horizontally out from the cutting mechanism. Further explanations relating to the trough 48, the chute 130, and also to the way the overall mechanism can switch to deliver cane billets to the other side of the harvester (i.e. to the left-hand side as shown in Figures 1 , 2, 16 and 19, rather than the right-hand side as shown in Figures 3 and 6) will be given below. Nevertheless, for present purposes, it will be appreciated that, immediately after the cane billets are cut, they collect (temporarily) in the bottom of the trough 46. After collecting in the trough 46, the billets are then thrown up and out though the chute 130 by the paddle mechanism.

[0066] The paddle mechanism includes, firstly, a paddle rotor 1 10. The paddle rotor 1 10 is a large circular disc-like component at the rear of the chop throw mechanism. At its centre, the paddle rotor 1 0 is keyed directly into the main driveshaft 100. Consequently, the main driveshaft 100 and the paddle rotor 1 10 are effectively fixed together, and they both also share a common central axis of rotation. Hence, rotation of the main driveshaft 100 always directly causes rotation of the paddle rotor 1 10 in the same direction and at the same rotational speed.

[0067] The paddle mechanism also includes a number of fixed and hinged paddles which are connected to the paddle rotor 110. The fixed paddles are indicated by reference numeral 1 12, and the hinged paddies are indicated by reference numeral 1_. 14. The fixed paddles 1 12 and hinged paddles 1 14 are mounted to the paddle rotor 1 10 in pairs, with each pair comprising one fixed paddle 1 12 and one adjacent hinged paddle 1 14. In this particular embodiment, there are three such pairs located at equally spaced positions around the paddle rotor 1 0 (meaning that there is one pair of paddles per coulter). In other embodiments, and particularly embodiments having a different number of cutting coulters, a different number of paddle pairs may also be provided. In any case, only one of the pairs of paddles is clearly visible in Figure 6 (the other two pairs are at least partly hidden from view in Figure 6 by the coulters 50 etc). [0068] Nevertheless., from Figure 6 it will be seen that, in each paddle pair, both the fixed paddle 1 12 and the hinged paddle 1 14 comp ise a flat substantially rectangular plate. In each pair, the fixed paddle 112 is mounted on the outside, and the hinged paddle 1 14 is mounted on the radially inward side of the fixed paddle 112, Each fixed paddle 1 12 is mounted such that its outer-most straight edge is approximately flush with (and perpendicular to) the perimeter edge of the paddle rotor 1 10. Also, each fixed paddle 1 12 is mounted such that its flat shape is oriented in a plane which contains the axis of the driveshaft 100 (and hence each fixed paddle 1 12 is perpendicular to the paddle rotor 1 10).

[0069] Normally, the hinged paddle 1 14 in each pair will be aligned with the fixed paddle 1 12 (i.e. the hinged paddle 1 14 in each pair will normally be oriented in the same plane as the fixed paddle 1 12}, and the hinged paddle 1 14 in each pair will normally be positioned such that its outermost straight edge touches (or almost touches) the innermost straight edge of the fixed paddle 11 . Each fixed paddle 1 1 is fixedly bolted to the paddle rotor 110. Each of the hinged paddles 1 14, however, is designed to be able to pivot (and specifically pivot out of the plane of the corresponding fixed paddle 1 12) for reasons discussed further below.

[0070] The length of each of the fixed paddles 1 12 (i.e. the dimension of each fixed paddle 112 in the direction perpendicular to the padd!e rotor 1 10 and parallel to the d iveshaft 100) is such that the fixed paddles 1 12 along with the paddle rotor 1 10 (to which the fixed paddles 112 are bolted) together fit snugl in and rotate within the confines of the curved, rectangular cross-sectioned channel on the inside of trough 46. In other words, the length of the fixed paddle 1 1 , plus the thickness of the portion of the paddle rotor 1 10 which inserts into the said channel inside the trough 46, is approximately the same as (or slightly less than) the width of the said channel. Consequently, when the chop throw mechanism is assembled and rotating, the paddle rotor 1 10 rotates causing, inter alia, the fixed paddles 1 12 to move around in a circular path. This rotation causes the fixed paddies 1 12 to sweep through the rectangula channel inside the trough 46. More specifically, the paddle rotor 1 10 and the fixed paddles 1 12 together sweep around and through the channel inside trough 46 with only a small clearance between them and the internal surfaces of the trough 46.

[0071] At this point it should be recalled that, after being cut by the coulters 50, the cut cane billets collect (temporarily) in the bottom of the trough 46. It will now be appreciated that, cut billets actually only cofiect in the trough 46 during the time after one of the fixed paddles 1 12 has swept through, and before the next paddle 1 12 sweeps through. Also, any billets which collect in the bottom of the trough 46 before the next fixed paddle 1 12 sweeps through will then be pushed along ahead of that next fixed paddle 1 12 as it sweeps through. The fixed paddle 1 12 then sweeps those billets ail the way around the curved trough 46 until the billets are "thrown" up into the chute 130. This is how the paddle mechanism throws the cut billets into the chute 130.

[0072] In general, the hinged paddles 1 14 perform the same function as the fixed paddies 112 described above, and they normally operate in generally the same way. However, there are also some important differences between the fixed and hinged paddles. Firstly, the hinged paddles 114 are mounted radially inward on the paddle rotor 1 10 relative to the fixed paddles 1 12. This means that, when the paddle rotor 110 rotates, the circular path swept out by eac of the hinged paddles 1 14 is smaller and located inside the circular path swept out by the corresponding fixed paddle 1 12. In other words, the hinged paddles 1 14 sweep through a space which is radially inside the space through which the fixed paddies 1 12 sweep.

[0073] Accordingly, whereas the fixed paddles 1 12 sweep up any billets which temporarily collect within the space in the trough through which the fixed paddles 1 12 sweep (this space being within but radially towards the outside of the trough 46), in contrast the hinged paddles 1 14 swee up billets which temporarily collect in the more radially inward space in the trough through which the hinged paddles 1 14 sweep. Of course, billets swept by the hinged paddles 1 14 are swept around and up into the chute 130, just like the biilets swept by the fixed paddles 1 12.

[0074] There are aiso certain important design differences between the fixed paddies 112 and the hinged paddles 1 14. To begin to understand these differences, it should first be noted that the width of the fixed paddles 1 12 (i.e. the dimension of the fixed paddies 1 12 in the radial direction) is slightly less than the depth of the channel inside the trough 46. Consequently, as the fixed paddles 112 swee around and through the channel in the trough 46, the fixed paddles 112 all pass beneath (i.e. radially to the outside of) the anvil wear plate 44. In other words, even though the distal ends of the respective fixed paddies 1 12 (i.e. the ends opposite the paddle rotor 1 10) pass quite ciqse to the anvil wear plate 44, nevertheless at all times ail parts of the fixed paddies 1 12 remain radially to the outside of the anvii wear plate 44. The fixed paddles 1 12 therefore cannot collide with portions of the un-cut cane mat (or foreign objects which are carried by the cane mat) as these pass over the edge of the anvil wear plate 44.

[0075] In contrast to this, as mentioned above, the hinged paddles 1 14 are located radially inward of the fixed paddles 112, although the outside edges of the respective hinged paddles 114 are close to (or touch) the radially inside edges of the fixed paddles 1 12. As a result, and due to the width of the hinged paddles 1 14 (i.e. their dimension in the radial direction), there are portions of each hinged paddle 14 which are located at the same radius as the anvil wear plate 44, and parts which are located radially inward relative to the anvil wear plate 44. Consequently, to prevent the hinged paddles 114 from coiliding with the anvil 40 and the anvil wear plate 44 as they rotate, the ends of the hinged paddles 114 opposite the paddle rotor 1 10 are shaped to ensure that the hinged paddles 114 "clear" the anvil 40 and the anvil wear plate 44. In other words, the edges of the hinged paddles 1 14 which are on the opposite side thereof from the paddle rotor 1 10 are shaped to ensure that the hinged paddles 1 14 do not collide with the anvil or its wear plate as the hinged paddles 1 14 pass by.

[0076] In the particular embodiment illustrated in the Figures, on each hinged paddle 1 14, the end of the paddle opposite the paddle rotor 1 10 is tapered to prevent the paddle from colliding with the anvil etc. The tapered ends of the hinged paddles 114 are clearly visible in Figures 7-9. Note that the anvil 40 and anvil wear plate 44 are not illustrated in Figures 7-9, although Figures 7 and 8 do illustrate that the tapering on the ends of the respective hinged paddles 1 14 also allows the hinged paddles to "clear" (i.e. avoid colliding with) the respective cutting coulters 50.

[0077] Figures 7 and 8 also illustrate the fact that the hinged paddles 1 14 are attached to the paddle rotor 1 10 in a different way to the fixed paddles 1 12. As mentioned above, the fixed paddles 1 12 are fixedly attached (bolted to) the paddle rotor 1 10. This can also be seen from Figure 6. In contrast, each of the hinged paddies 1 14 is connected to the paddle rotor 1 10 by a hinged connection. More specifically, it can be seen from Figures 7 and 8 that, on each of the hinged paddles 114, a radially inside edge portion 1 16 of the paddle is rounded. This rounded edge portion 1 16 on each hinged paddl 1 14 contains a hinge rod (not visible), and each hinge rod also inserts into a corresponding rounded portion 1 18 on the paddle rotor 1 10. Hence, the respective hinged paddles 1 14 are hingedly connected to the paddle rotor 1 10 by the said hinge rods. However, whilst the hinged paddles 1 14 are hingedly connected to the paddle rotor 1 10, nevertheless they are normally prevented from pivoting about the resulting hinge by a connecting member 1 0. Each connecting member 120 is, at one end thereof, connected to (or formed as part of) the rounded portion 116 of the corresponding paddle 114, and at the other end the connecting member 120 is fixedly bolted to the paddle rotor 110 by a shear bolt 122. Hence, each connecting member 120 is attached to its corresponding hinged paddle 114, and each connecting member 120 is also normally fixedly attached to the paddle rotor 1 10 by its shear bolt 122. in this way (i,e, due to the attachment of the connecting member 120 to the paddle rotor 1 10 by the shear bolt 122) each of the hinged paddles 1 14 is normally prevented from pivoting about its hinge rod.

[0078] The purpose of this hinged connection between the respective hinged paddles 1 14 and the paddle rotor 110 will now be explained. As mentioned above, there are portions of each hinged paddle 1 14 which are located at the same radius as the anvil wear plate 44, and also portions of each hinged paddle 114 which are located radially inward relative to the anvil wear plate 44. As a result, when the hinged paddies 1 14 rotate, they each sweep through the space into which the movin mat of cane enters as the cane mat passes out of the profile converter 34 and over the edge of the anvil wear plate 44. Of course, at this point the rotating coulters 50 normally cut the cane into billets, as described above, and therefore the hinged paddles 1 14 normally simply sweep up any billets which remain in this space when th paddle 1 14 sweeps through.

[0079] However, occasionally a foreign object, such as a large rock or a length of steel (e.g. a steel post or star picket) or the like, may become caught up in the moving mat of cane. Such a foreign object may therefore travel or be carried with the cane mat through the feed train, through the profile converter 34 and out over the edge of the anvil wear plate 44. Thus, the foreign object may become positioned in the space through which the hinged paddles 114 pass as the rotate. (This may also cause the foreign object to move into the path of the rotating cutting coulters 50, however the way in which the cutting coulters 50 are designed to prevent or minimise damage in this situation is discussed further below.) In any case, in this situation, if the paddles 1 14 were simply bolted to the paddle rotor 110 (i.e. in the same way as the fixed paddles 1 12 are), then the paddles 1 14 might be severely damaged or destroyed upon colliding with such a heavy hard foreign object. However, the hinged paddles 1 14 are not simply immovably bolted to the paddle rotor. Rather, there is a hinged connection between the hinged paddles 1 14 and the paddle rotor 1 10, as described above, which operates to help prevent or minimise damage in these situations.

[0080] More specifically, if a foreign object such as a rock or the like enters the space through which the paddles 1 14 sweep (i.e. as explained above), then at least one (and possibly multiple or all) of the hinged paddles 1 14 wiii likely collide with that foreign object. However, rather than bending, snapping or otherwise severely damaging the paddie(s) 1 14, this collision between the paddle (s) 1 14 and the foreign object will instead impact the side of the (or each successive) paddle 114 creating a lateral/sideways force on the (or each successive) paddle 114 (i.e. a force approximately perpendicular to the plane of the paddle 1 14). This lateral force, due at !east in part to the high speed at which the paddies are rotating, will be sufficiently large (and/or will create a sufficiently great impact loading), and it will be transmitted through the connecting member 1 0, so that the shear bolt 122 will shear/break. Shearing the shear bolt 122 disconnects/disengages the connecting member 120 from the paddle rotor 1 10, Therefore, when the shear bolt 122 shears, the hinged paddle 1 14 will become free to pivot about its hinge and will therefore immediately be pushed by the lateral force and pivot about the hinge. This therefore causes the hinged paddle 1 14 to pivot and move over the top of the rock or other foreign object. In other words, the paddle 114 will pivot and "clear" the foreign object, rather than bending or snapping upon collision with the foreign object

[0081] Of course, in this situation, the mechanism would need to be stopped to remove the foreign object and also to replace the shear bolt(s) 122 in order to reestablish the connection between the paddle(s) 1 14 and the paddle rotor 1 10 via the connecting member 120 (which prevents the paddle 114 from pivoting). This is necessary for the paddles 114 to again operate normally to perform the sweeping function described above. Nevertheless, it will be appreciated that this design (and in particular the sacrificial shear bolts 122 which can be severed to thereby allow the hinged paddles to pivot) at least helps to prevent significant damage to the hinged paddles 1 14 in the event of impact with a foreign object exiting the feed train.

[0082] Next, the chute 130 which extends above and out from the chop throw mechanism will be explained. As has been mentioned previously, and for the avoidance of doubt, Ftgures 3 and 6 show the chute 130 extending up and out to the right-hand side relative to the harvester's forward direction. On the other hand, Figures 1 , 2, 16 and 19 show the chute extending up and out to the left-hand side relative to the harvester's forward direction. Both configurations are possible (although only one configuration is possible at a time). The way in which the mechanism can be switched to dispense billets to the left-hand side rather than the right-hand side, or vice versa, wit! be discussed further below.

[0083] From the explanations above, it will be recalled that the moving mat of cane enters the chopper mechanism through the profile converter 34. As the moving mat of cane exits the profile converter 34 over the anvil wear plate 44, it is cut into billets by the cutting coulters 50 which rotate past the wear plate 44 at high speed (the coulters 50 contact and roll along the wear plate 44 as they pass). The cut billets are then swept up by the respective sets of paddles 1 12, 1 14 which are also rotating. (Each pair of rotating paddies 1 12, 1 14 rotates closely behind and hence "follows" a respective coulter 50). The paddles 1 12, 1 1 convey the cut biliets around the channel instde the trough 46 until the billets reach the end of the said channel in the trough 46 immediately below the chute 130, whereupon the billets are thrown upwards into the chute 1 30 as depicted in Figure 19.

[0084] The operation of the chute 130 and its various associated components can be understood from Figures 2, 3, 6 and 19. From these Figures, it can be seen that the chute 130 begins above the chop throw mechanism and it extends vertically upwards and laterall to one side (left or right) from there. Importantly, the upper surface of the chute 130 is mostly solid. That is. there are no openings or gaps therein through which cut billets etc might otherwise escape. The one exception to this is the opening in the upper surface of the chute which allows entry of air flow from the blower 140. Nevertheless, aside from the opening which allows air flow from the blower 140, the chute's upper surface otherwise forms a solid curved roof along the length of the chute 130. The horizontal side walls of the chute 130 are also solid (to prevent billets escaping out the sides), and this is visible in Figure 2, 3 and 6 (for example). (Note that the cut billets and trash etc appear to be visible through the side of the chute in Figure 19, However, for the avoidance of doubt, this is not intended to show or suggest that the sides of the chute 130 are open. Rather, in Figure 19, one side of the chute 130 is removed in order to reveal and illustrate the passage of billets and trash inside the chute (i.e. moving through and out of the chute).) [0085] In contrast to the upper surface and sides of the chute 130 whic are mostly closed/solid as described above, much of the underside of the chute 30 is open. This ca be see in Figures 2 and 3, and can also be appreciated from Figure 19.

[0086] As mentioned above, the chute 130 has a blower 140 mounted thereon. The blower 140 is positioned above the upper surface of the chute 130 and is cantilevered relative to the chute 130 in such a way that the blower 140 extends out in generally the opposite lateral direction compared to the chute 1 30 itself. This helps to (at least partially) balance the weight of the chute 130 which is cantilevered to one side of the harvester. The blower 140 includes a cylindrical portion 142 at its outer end. The blower's fan {or other air-flow creating mechanism) is housed inside the cylindrical end portion 142. Details of the blower's internal fan (or other air-fiow creating mechanism) are not critical to the invention and therefore need not be described. The cylindrical portion 142 containing the blower mechanism is connected to the upper surface of the chute 130 via a duct 144. Hence, air is blown by the blower mechanism down through the duct 144 and into the chute 130.

[0087] More specifically, as illustrated in Figure 19, the blower 140 creates a curtain of comparatively high speed airflow passing diagonally down and through the chute 130. In other words, the high speed airflow entering through the upper surface of the chute 130 from the duct 144 create a curtain of moving air which passes diagonally down through the chute 1 30 and out through the chute's open underside. The airflow curtain created by the blower 140 is indicated by arrow "C" in Figure 19,

[0088] As explained above, after being cut by the coulters 50, the cut cane billets are swept (b the rotating paddles 1 12, 1 14) around the channel inside of the trough 46 until the billets are thrown upwards into the chute 130. It should also be recognised that, before being cut into billets, the moving mat of cane contains and carries with it a large amount of leaf matter and other low-density debris (collectively referred to as "trash"). Hence, this trash is also chopped up into small pieces and swept up into the chute 130 in the same way as, and together with, the cut cane billets.

[0089] The purpose of the airflow curtain created by the blower 140 is to help separate the cane billets from the unwanted pieces of chopped u trash. The way this is achieved is discussed below. Firstly, it should be appreciated that the cut billets and the cut trash are both thrown up info the chute 130 by the paddles at roughly the same velocity. However, it should also be appreciated that the cane billets are much denser than the cut pieces of trash. As a result, whilst the billets and the trash both enter the bottom of the chute 130 with approximately the same velocity, nevertheless the cane billets (due to their greater mass/density) continue info the chute 130 with much greater momentum than the trash. This is significant because the greater momentum of the cane billets carries the billets up through the chute and it allows them to pass through the curtain of airflow C created by the blower 140. In contrast, the cut pieces of trash have far lower momentum (due to their lower density/mass) and therefore they decelerate much more rapidly than the cane billets upon entering the chute 130. The momentum of the cut trash is generally also insufficient to carry much (or any) of the trash through the air curtain C. As a result, most (if not all) of the cut trash is diverted (blown) out through the open bottom of the chute 130 by airflow curtain C, whereas the cane billets continue through the air curtain, up along and out of the chute 130, as depicted in Figure 1 9,

[0090] In addition to the above, those skilled in the art will appreciate that the motion of the rotating paddles as they move up towards the chute (i.e. as they rotate vertically upward carrying the cut billets and trash and just before the billets and trash are thrown up into the chute) also creates airflow which travels upward into the chute. Importantly, however, this airflow (which at least partially carries with it the less dense trash) is blocked by and cannot pass through the curtain of air C created by the blower 140. Basically, the airflow in the airflow curtain O is much stronger.

[0091] Furthermore, those skilled in the art will appreciate that, at the point of throw, the denser/heavier cane billets will often follow a more direct trajector up the chute (i.e. they will travel up and along the underside of the chute's upper surface), whereas the lower density trash will often tend to separate due to its more rapid deceleration and will move towards the open underside of the chute. Movement of air transverse to (rather than along the chute which is created by the paddles as they sweep horizontally past the open base of the chute may also assist the trash to move laterally toward the open underside of the chute, thus further assisting separation of billets from trash. Accordingly, even before reaching the airflow curtain, much of the trash may already be located (or moving) more towards the open underside of the chute whereas much of the cane billets may already be located (or moving) more towards the chute's upper inside surface. This may assist further in reducing cane losses while maximising trash removal. [0092] Widely used rotary choppers, as discussed in the Background section above, have a primary extractor fan above and behind the choppers. The fan draws air through the billet and trash mix that is exiting the choppers. The billet and trash mix in this mechanism is generally relativel compact. A strong suction is required from the fan to draw the leaf material from this rather dense mix. if this suction is too strong, billets will eject along with the trash (as discussed in the Background section above}. Consequently the power of the fan is adjusted to achieve an acceptable compromise between extraneous matter levels and billet losses. In an attempt to reduce extraneous matter levels whilst minimising losses, a second (or secondary) extractor is usually also mounted at the ejection point at the top of the elevator. This extra extractor, mounted at the top end of the elevator creates an additional weight which exasperates the cantilevering action which already exists in the relatively heavy elevator.

[0093] In contrast, whilst the chute 30 in the chop throw mechanism described herein also creates a degree of undesirable cantilevering action, nevertheless it weighs substantially less not having an elevator with chains, sprockets, shafts, flights etc. It also does not have a (secondary) extractor at the outer end. Furthermore, the blower 140 is positioned on the opposite side of the centre line of the harvester, thereby providing some relief in relation to the cantilevering action of the chute 130.

[0094] In addition, extractors (including primary and secondary extractors) such as those used in rotary choppers operate in dirty air. Indeed, all material extracted from the cane flow passes through the extractor blades. This creates substantial wear and tear, not only to the extractor fan, but also to the wear shroud, the chute that surrounds it, etc. In contrast the blower 140 operates in clean air meaning that wear and tear issues are significantly reduced,

[0095] The chute 130 also includes a diversion plate 150, a sloping floor 160 and a spreader flap 170. These components can be seen in several of the Figures. From Figures 3 and 19, it can be seen that one edge of the diversion plate 150 is pivotally attached to the underside of the chute 130, at a location somewhat inward from the chute's outer distal end. The diversion plate 150 can be pivoted upward from the orientation shown in the Figures. It is pivoted upward in this way by a hydraulic cylinder 152 (the hydraulic cylinder 1 52 is shown in Figure 3). Pivoting the diversion plate 150 upward causes its free end edge (i.e. the edge opposite the hinged edge) to move up into contact with the underside of the chute's upper surface. The effect of this is to change the path (trajectory) along which the billets travel as they travel (fly) along the underside of the chute's upper surface. More specifically, it causes the billets to be directed downward as soon as they contact the diversion plate 150 such that the billets are discharged through the open underside of the chute below the diversion plate 150 (and hence closer to the harvester), rather than out through the end of the chute 130 as is shown Figure 19, This (i.e. discharging the billets closer to the harvester) may be useful in situations where there is a need to allow the truck or other vehicle carrying the receptacle into which the billets are dispensed to travel closer to the harvester, for instance in confined areas or when opening up through the centre of a field.

[0096] As mentioned above, the chute 130 also has a sloping floor portion 160 and a spreader flap 170. The sloping floor 160 has a solid planar base 162 which is attached, by a pair of solid vertical planar sides 164, to the sides of the chute 130. The configuration of the sloping floor 160 is such that the planar base 162 effectively hangs by the sides 164 in an outwardly-sloping diagonal orientation beneath the outer end of the chute 130.

[0097] The spreader flap 170 is hingedly attached to the outermost edge of the chute's upper surface. In the Figures, the spreader flap 170 is shown hanging approximately vertically down from its hinge. In this orientation (assuming the diversion plate 150 is lowered out of the path of the billets as shown in the Figures) the trajectory of the billets through the chute 130 will extend all the way along and out of the chute, whereupon the billets will strike the approximately vertical spreader flap 170 and drop down vertically therefrom (as illustrated in Figure 19).

[0098] However, the spreader flap 170 can be pivoted about its hinge. The spreader flap 170 is pivoted by operation of hydraulic cylinders 172 (visible in Figures 3 and 6). If the spreade flap 170 is pivoted outward relative to its orientation as shown in the Figures (i.e. if it is pivoted so as to "open up" more relative to the chute 130) the billets, rather than striking the spreader flap 1 0 quite square on and dropping vertically downward (as they do in the Figures), will instead strike the spreader flap 170 at a more glancing angle (depending on how much the spreader flap is opened up) and the billets will therefore be deflected in a trajectory that continues at least somewhat more outwardly from the harvester. As such, varying the angle of the spreader flap 170 allows a degree of control over how far away from the harvester the billets are ultimatel delivered, thus providing a degree of flexibility to allow for, for example, different sizes or widths of the shadowing truck/trailer/receptacle, etc,

[0099] The hydraulic cylinders 1 72 ca also be used to pivot the spreader fla 170 inward relative to its orientation shown in Figures, in fact, the spreader flap 1 0 can be pivoted inward such that it's side flanges 1 4 overla on the outside of the respective sides 164 of the sloping floor 160, and the spreader flap itself closes against the lower outside edge of the sloping floor's base 162. Thus, the spreader flap 170 can be pivoted inward so as to fully close the opening that is formed between the sloping floor 60 and the upper surface of the chute 130 (i.e. the opening through which billets would otherwise normall pass as they are ejected). When the spreader flap 170 is closed in this way, the sloping floor 160 (including the base 62 and the sides 164 of the sloping floor) together with the spreader flap 1 0 create a containment receptacle in the end of the chute 130 which is capable of temporarily storing a small volume of billets which are received and collect therein, while the harvester is proceeding with the spreader fla 170 closed. This ability to temporarily "catch" and retain a small volume of cut billets may be useful in a number of circumstances. For example, when the harvester first commences down a new crop row, there may not be room (or it may not otherwise be possible) for the shadowing truck trailer to be positioned appropriately behind and to the side of the harvester as the harvester commences down the row. Rather, the harvester may need to move down the row a certain distance before the shadowing truck trailer can move correctly into position. In these or similar circumstances, the spreader flap 170 can be closed such that billets which are harvested as the harvester initially commences down a new row can be caught, rather than being dispensed out onto the ground and lost/wasted before the shadowing truck/trailer can move into position.

[00100] As mentioned above, Figure 9 is an exploded view of three groups of components (or subassemblies) which together make up the chop throw mechanism. The group of components on the left in Figure 9 includes the paddle rotor 1 10 which is keyed to the main driveshaft 100, and also the sets of paddies 1 12, 114 which are attached to the paddle rotor 110 and operate in the manner described in detail above. The left-hand group of components in Figure 9 might therefore be thought of as the paddle subassembly, although this subassembly also includes certai additiona! components the purpose of which will be discussed further below. The group of components on the right in Figure 9 includes the cutting coulters 50, the spindles 70 which connect the respective coulters 50 to the coulter hu 90, etc. The right-hand group of components in Figure 9 might therefore be thought of as the coulter subassembly, although again this subassembly also includes certain additional components the purpose of which will be discussed further below, The group of components shown in the centre in Figure 9, which may be thought of as the set hub subassembly, interacts with both the paddle subassembly and the coulter subassembly. Figures 7, 8, 10, 1 1 and 12 variously show the three above-mentioned groups of components/subassemblies assembled together. It can be seen that all three subassemblies are mounted so as to rotate about an axis corresponding to the longitudinal axis of the main driveshaft 100.

[001.01^']_. As just mentioned, the coulter subassembly (on the right in Figure 9) includes the cutting coulters 50 and the spindles 70 which connect the respective coulters 50 to the coulter hub 90. The way in which the respective spindles 70 connect to the coulter hub 90 is more clearly illustrated in Figure 13. From Figure 13, it can be seen that on the radially inner end of each spindle 70 there is a plate portion 72. Each plate 72 is bolted directly to the coulter hub 90 by four bolts 71 , thus connecting the said spindle 70 to the coulter hub 90. The holes in each plate 72 through which the bolts 71 pass to attach that spindle 70 to the coulter hub 90 are elongated/slotted. This allows for adjustment (in a direction parallel to the axis of the main driveshaft 100} of the position at which the spindie is secured relative to the coulter hub. One reason such adjustment may be needed is because, as the coulters 50 wear with use, the edge of each coulter 50 may wear down, thus reducing the width (i.e. the thickness in the direction parallel to the driveshaft) of at least portions of the coulters 50 which contact the anvil wear plate 44, Accordingly, the position of the spindles 70 may need to be adjusted to, in effect, move the coulters 50 axially closer to the anvil to ensure that the coulters continue to contact the anvil wear plate 44 to maintain cutting performance. In fact, this also allows the spindles 70 to be positioned such that the coulters 50 are "preloaded" against the anvil wear plate 44 (i.e. so that the coulters 50 contact with some pressure against the anvil wear piate 44) as they pass along the anvil wear plate 44 one after the other. The adjustment allows this pre-load to be maintained even as the coulters 50 wear.

[00102] In relation to this preloading of the coulters 50 against the anvii wear plate 44, it should also be noted that the anvil 40 and the wear plate 44 are wider (i.e. they extend in a larger arc) than the profile converter 34. This is so that, as the coulters 50 rotate, they contact the anvil wear plate 44, and hence begin rolling along the anvil wear plate, before coming into contact with the cane mat exiting the profile converter 34. Thus, the coulters 50 are already rolling before they begin cutting into (and through) the cane mat. Also, the ends of the anvil wear plate 44 are tapered slightly. This helps to guide the rotating coulters 50 into their preload against the anvil wear plate 44 without a drastic impact against the wear p!ate (which might otherwise cause damage). The preload between the coulters 50 and the anvil wear plate 44 may also have a self- sharpening effect on the coulters 50.

[00103] Importantly, the dise!ike portion 92 visible in Figure 13 is part of the coulter hub 90. That is, the disclike portion 92 is integral with (or fixed to) the part of the coulter hub 90 to which the spindles 70 are bolted. Furthermore, it can be seen that there is an adjustment screw 74 associated with each spindle plate 72. In each case, one end (the head end) of the adjustment scre 74 is secured to the plate portion 72 of the spindle, and the threaded adjustment screw 74 extends from the head end through a hole in the disclike portion 92 of the coulter hub. A nut is screwed onto the adjustment screw 74 on either side of the disclike portion 92 from the head end. It will therefore be understood that the adjustment screw 74, by adjusting the nuts thereon, can affect fine adjustment of the positioning of the associated spindle plate 72 relative to the coulter hub 90. Hence, in practice, the spindle plate 72 for a given spindle can first be approximately positioned on the coulter hub 90 and the bolts 71 lightly tightened. Then the adjustment screw 74 can be used (by adjusting the nuts) to finely position that spindle 70 relative to the coulter hub 90 before the bolts 71 are fully tightened to secure the spindle 70 in position. Figure 13 illustrates that there are a number of other features of (on) the disclike portion 92, and a number of additional components attached thereto. These will be discussed further below.

[00104] Figure 13 also illustrates that, on the distal end (i.e. the radially outward end) of each spindle 70 there is a portion of slightly reduced diameter. This portion with reduced diameter, on each spindle 70, forms a boss 76 for mounting boot 1 80 (see further below). The outer end of each boss 76 is threaded, and in Figure 13 a retaining nut 77 and a washer 78 are shown on the threaded end of each boss 78. The retaining nuts 77 operate to secure the respective boots 180 on the respective bosses 76 (again, see below).

[00105] Figure 14 is an exploded view of one individual coulter assembly. The spindle 70 is shown at the top in Figure 14, and as explained above, bolts 71 are inserted through spindle's plate-like portion 72 to attach the spindle to the coulter hub 90 (the bolts 71 and the coulter hub 90 are not shown in Figure 14). The boss 76 on the opposite (radially outer) end of the spindle 70 is also illustrated in Figure 14, as are the boot retaining nut 77 and washer 78. However, in Figure 14, the nut 77 and washer 78 are illustrated below all the other components. This is intended to help visualise the way in which the nut 77 and washer 78 operate to secure the boot 180 on the spindle. It will be appreciated that when all of the components illustrated are assembled together onto the spindle 70, the nut 77 in particular is screwed onto the threaded end of the spindle boss 76 last to thereby secure the components thereon.

[00106] The other components illustrated in Figure 14 are the circular disc-like cutting coulter 50, coulter carrier 60, an adjustment sleave 80, the boot 180, a keeper 190 and a tiller arm 200. The interconneetedness and function of these components is explained below.

[00107] Referring first to the coulter carrier 60, it can be seen that this component has a cylindrical stub axle 62. The disc-like coulter 50 is mounted on the stub axle 62, The coulter 50 is mounted in such a way that it can freely rotate relative to the coulter carrier 60 when mounted on the stub axle 62. In other words, the coulter 50 can rotate freely on the stub axle 62. To facilitate this, the coulter 50 is provided with bearings. The bearings are visible in several Figures but are not specifically identified by reference numerals.

[00108] Referring next to the coulter carrier 60 and the adjustment sleave 80, whilst these two components are shown separate from one another in the exploded views in Figures 14 and 18, when the coulter assembly is assembled (as shown in Figures 15 and 17) these two components are attached together. More specifically, the adjustment sleave 80 has a back and a pair of parallel sides. The coulter carrier 60 includes a main block-like portion. When the coulter carrier 60 and adjustment sieave 80 are assembled together, the block-like portion of the coulter carrier 60 inserts between the sides of the adjustment sleave 80. Four threaded holes 64 on the block-like portion of the coulter carrier 60 then become aligned with four corresponding vertically elongate slots 82 in the back of the adjustment sleave 80. Bolts 81 (see Figure 18) are inserted through the vertical slots 82 and into the threaded holes 64 to thereby secure the coulter carrier 60 and the adjustment sleave 80 together.

[00109] The vertically elongate shape of the slots 82 also allows a degree of radial adjustment of the position at which the coulter carrier 60 is secured relative to the adjustment sleave 80. An adjustment rod 84 is also provided to help facilitate fine adjustment of the radial position of the coulter carrier 60 relative to the adjustment sleave 80. The radially inner end of the adjustment rod 84 is threaded and inserts through a flange attached to the cylindrical portion 66 of the coulter carrier, and nuts 85 threaded onto the threaded portion of the rod 84, above and below the said flange, facilitate the fine adjustment. See Figure 17. One reason why such radial adjustment may be needed is because, as the coulters 50 wear with use, the edge of each coulter 50 may wear down thus reducing the overall diameter of each coulter 50. Accordingly, the radial position at which each coulter carrier 60 is attached relative to the associated adjustment sleave SO may need to be adjusted to thereby move the coulter 50 (which is mounted to the coulter carrier 60) radially outwards to ensure that the coulter continues to contact the anvil wear plate 44 (including with the required preload as discussed above) to maintain cutting performance.

[00110] The coulter carrier 60 and the adjustment sleave 80 are connected together as just described. As has also been described, the disc-like coulter 50 is mounted on the stub axle 62 of the coulter carrier. Accordingly, these three components of each individual coulter assembly (i.e. the coulter carrier 60, adjustment sleave 80 and coulter 50) are ail connected together when the individual coulter assembly is assembled. Figure 14 also shows the cylindrical portion 66 of the coulter carrier mentioned above. The cylindrical portion 66 extends radially inward from the block-like portion of the coulter carrier 60. The tiller arm 200 is pivotally connected to cylindrical portion 66. The tiller arm 200 will be discussed further below. For present purposes it should be noted that there is a cylindrical bore 68 extending through the cylindrical portion 66. In fact, the cylindrical bore 68 extends through the cylindrical portion 66, and also through the block-like portion, of the coulter carrier 60. Hence, the bore 68 extends radially all the way through the coulter carrier 60. Accordingly, when the individual coulter assembly (illustrated in exploded view in Figure 14) is assembled as shown e.g. in Figure 15, the coulter carrier 60 slides onto the spindle 70 such that the spindle inserts into and through the cylindrical bore 68. Furthermore, because the adjustment sleave 80 is attached to the coulter carrier 60, as is the coulter 50 and the tiller arm 200, it follows that when the individual coulter assembly is assembled, all of these components (which are connected together) become mounted on the spindle 70.

[0011 1] Importantly, the coulter carrier 60 (with the other components attached thereto as described above) is not always secured relative to the spindle 70. Therefore, in some circumstances the coulter carrier 60 (together with the other components attached thereto) will be unconstrained from sliding (and hence able to slide) radially inward and outward along the spindle 70. The reason for this will be explained below. The exception to this is when the chopper mechanism is stationary or operating at low speeds (e.g. at start-up). At such times (e.g. at start-up or during low RPM operation) the Goulter carrier 60 is secured/locked toward the outside (in fact it is locked to the outside in engagement with the boot 180) and thus prevented from moving radially inward along the spindle. The reason for this too, and the way in which it is achieved, will be discussed further below. The coulter carrier 60 is also able to pivot relative to the spindle 70. And again, the reason for this, and the wa in which it is achieved, will be discussed below.

[00112] As mentioned above, the boot 180 is secured on the end of the spindle 70, More specifically, there is a hole extending radially through the centre of the boot 180, and the boss 76 on the radially outward end of the spindle 70 inserts through this hole before the nut 77 (along with washer 78) is screwed onto the threaded end of the boss 76 to thereby secure the boot 180 on the boss 76. The hole in the boot 180, and the way the nut 77 secures the boot 180 on the end of the spindle 70 is evident from Figures 4, 7, 8, 9 and others. Of course, th boot 180 is only installed and secured on the end of the spindle 70 after the coulter carrier 60 (together with the other components which are attached to the coulter carrier) has been installed on the spindle 70. The boot 80 thus prevents the coulter carrier 60 (and other components) from sliding off the end of the spindle 70.

[0011 ] When the boot 80 is mounted on the spindle 70, specifically on the boss 76 on the end of the spindle, the step change in the diameter of the spindle between the boss 76 and the main body section of the spindle 70 prevents the boot 180 from sliding axial!y along the spindle 70. Also, the radial length of the boss 76 is slightly larger than the bore through the boot 180. Therefore, when the boot 180 is mounted on the boss 76, the boot is able to pivot on the boss 76 (i.e. the boot 180 can pivot relative to the spindle 70) even after the nut 77 has been screwed on and tightened. Of course, the nut 77 and washer 78 prevent the boot from falling off the spindle boss 76. Specifically, when the nut 77 is tightened, this secures (clamps) the washer 78 on the end of the boss 76 which in turn ensures that the boot 180 is held on the boss 76 (albeit the boot 180 is able to pivot thereon). The pivotal movement/orientation of the boot 180 (amongst other components) is affected/controlled by the operation of the tiller arms 200, etc, as discussed below.. [00114] Referring now to the boot 180, it can be seen that the boot's radially outer surface 182 is curved. This curved outer surface 182 effectively functions as a funnel like lead-in to help ensure that the mat and cut billets are kept within the confines of the approaching paddles. For instance, the rotating coulters 50 might deflect some billets upwards causing the paddles to pass below them. However, because the hinged paddles 1 14 are positioned almost touching the trailing edge of a respective boot 180, this ensures that all billets (whether they are in suspension or at the base of the trough) remain somewhere in the path of the approaching paddies.

[00115] The boot 180 also includes a pair of upstanding walls 184. The walls 184 are parallel to one another, and they are separated by a distance equal to (or slightly greater than) th distance between the parallel sides of the adjustment sleave 80. The reason for this will be explained below.

[00116] The keeper 190 (mentioned above) is also pivotally mounted to the boot 180. The pivotal connection between the keeper 190 and the boot 180, which is formed by a pin 186 that connects the keeper 190 to the boot 180 and also functions as a hinge between the boot 180 and keeper 190, is located between and to one side of the upstanding walls 184. The orientation of the pin 186 (which forms the keeper's pivotal hinge) is such that the keeper 190 is able to pivot relative to the boot 180 in the direction of arrow "D" (see Figure 14), and back in the opposite direction to arrow "D". There is also a rod 192, which extends through the keeper 190 from one side to the other. The rod 192 is located part-way along the keepe 190, slightly up the keeper from the pin 186, and is parallel to the pin 186. Two springs 194 each extend between the rod 192 and respective fixed points (flanges) on the boot 180. The springs 194 are mounted in tension and are oriented such that the springs' natural bias tends to try and pivot the keeper 190 in the direction opposite to arrow "D".

[00117] The purpose and function of the keeper 190 in particular will now be explained. Figures 15 and 17 both illustrate a single coulter assembly fully assembled. Figures 15 and 17, however, differ from one another in that Figure 15 illustrates the said assembly when it is stationary or rotating about the drive shaft 100 at low rpm (e.g. as it would at start-up), whereas Figure 17 illustrates the same assembly operating at high rpm such as operating speed. In other words, Figure 17 is effectively a "snapshot" of the individual coulter assembly as it whirls around the drive shaft 100 at high rpm, (The tiller arm 200 is shown in Figure 15 but not in Figure 17, but this is immaterial insofar as the function of the keeper 190 is concerned.)

[001 18] From Figure 14, it can be seen that there is a keeper hook 86 formed as part of the adjustment sleave 80. The keeper hook 86 extends out from the back of the adjustment sleave 80. The keeper hook 86 is perpendicular to the back of the adjustment sleave 80 and extends in the opposite direction to the parallel sides of the adjustment sleave. The upper (radially inward) distal corner of the keeper hook 86 is cut away to form a notch. It can also be seen from Figure 14 that there is a pin 196 which extends between the two sides of the keeper 190. The pin 196 is on the distal end of the keeper 190 (i.e. the opposite end of the keeper from the pin 186 which pivotally connects the keeper to the boot 180).

[00119] Referring to Figure 15, as mentioned above this Figure illustrates the configuration of one of the individual coulter assemblies when the chop throw mechanism is stationary or moving at low rpm (e.g. at start-up). When the chop throw mechanism is stationary or moving at low rpm, the various parts of the coulter assembly adopt the configuration shown in Figure 15. In particular, the keeper 190 is pivoted by the springs 194 such that the pin 196 in the distal end thereof engages in the notch in the keeper hook 86. The engagement of the keeper's pin 196 in the keeper hook notch causes the adjustment sleave 80 to be retained in position relative to the boot 180. Effectively, the adjustment sleave 80 is locked to the boot 180 by the keepe 190. When the adjustment sleave 80 is locked to the boot 180_s the adjustment sleave 80 resides in between the upstanding walls 184 of the boot. Furthermore., because the coulter carrier 60 is attached to the adjustment sleave 80, it follows that the coulte carrier 60 (along with the other components which are attached to the coulter carrier) are also locked to the boot 180, Because the coulter carrier 60, adjustment sleave 80, etc, are thus locked to the boot 180 by the keeper 190 when the chop throw mechanism is stationary or at low rpm, therefore these components (including the coulter carrier 60 and the coulter 50) are prevented from sliding radially inward along the spindle 70 when the chop throw mechanism is stationary or operating at low rpm. in other words, when the chop throw mechanism is stationary or moving at low rpm, the coulter carrier 60 and coulter 50 etc are locked radially to the outside in engagement with the boot 180.

[00120] This is important is because, if it were otherwise, then when the mechanism is stationary or moving slowly, at which time at least one of the individual coulter assemblies will be oriented somewhat upward (i.e. with its coulter carrier 60, coulter 50, etc, located at least somewhat vertically above the drive shaft 100), gravity would cause the said coulter carrier 60, coulter 50, etc, to slide down/inward along the spindle 70 toward the drive shaft 100. If this were to happen, the coulters 50, coulter carriers 60, etc, on the respective different spindles 70 would be located at different relative radii, and this would cause imbalance during start-up rotation. Also, if the coulter carrier 60, coulter 50, etc, were not locked to the outside (to the boot) when the chop throw mechanism is stationary or moving at low rpm, and could hence slide inward along the spindle, then when the mechanism subsequently starts up (i.e. begins rotating with rapidly increasing angular velocity) centrifugal forces would cause the said coulter carrier 60, coulter 50, etc, to slide rapidly outward along the spindle 70 towards the outside where it would collide with the boot 180, potentially causing damage due to severe impact loading. Accordingly, the coulter carrier 60, coulter 50, etc, are locked radially to the outside in engagement with the boot 180 when the chop throw mechanism is stationary or moving at low rpm, in order to prevent the undesirable effects above.

[00121] Whilst the coulter carrier 60, couiter 50, etc, are locked to the boot 180 in the manner (and for the reasons) explained above, the keeper 190 should also allow a small amount of radial movement (or play) of the coulter carrier 60, coulter 50, etc, relative to the boot 130, when these are locked to the boot. This is in order to allow the coulter carrier 60, coulter 50, etc, to rise slightl if necessary to accommodate the preload of the coulter 50 against the anvil wear plate 34 (of course this is only necessary if one of the coulters is in (or comes into) contact with the anvil wear plate 34 when the machine is stationary (or operating at lo rpm)).

[00122] However, as mentioned above, Figure 1 is effectively a "snapshot" of an individual coulter assembly as it whirls around the drive shaft 100 at high rpm. When the chop throw mechanism is operating at high rpm, the various parts of the coulter assembly adopt the configuration shown in Figure 17. At this point it should be noted that, i both Figure 15 (stationary/low rpm) and Figure 17 (high-speed/high rpm), the keeper 190 is oriented slightly at an angle relative to the radial direction. (For example, the keeper 190 is oriented at angle compared to the spindle 70 which extends directly in the radial direction.) As a consequence of this, the centre of mass of the keeper 190 is located slightly out to one side of the pin 186. (Recall that the pin 186 forms the hinge by which the keeper 190 is pivotally connected to the boot 180.) As a result, when the chop throw mechanism is operating at high rpm, centrifugal forces acting on the keeper 190 cause the keeper to pivot about pin 186 in the direction of arrow D, overcoming the tensile bias of the springs 194. In other words, the said centrifugal forces cause the keeper 190 to pivot, against and overcoming the bias of springs 194, from the orientation shown in Figure 15 into the orientation shown in Figure 17.

[00123] When the keeper 190 pivots from the orientation in Figure 15 into the orientation Figure 17, as described above, the pin 196 in the distal end of the keeper 190 moves out of engagement with the notch in the keeper hook 86. Once the pin 196 moves free of the notch in the keeper hook 86, the keeper 190 no longer operates to Sock the adjustment sleave 80 to the boot 180. Accordingly, when the chop throw mechanism is operating at high rpm, the keeper 190 disengages meaning that the coulter carrier 60 (to which the adjustment sleave 80, coulter 50, etc, are attached} is able to move radially inward along the spindle 70 away from the boot 180. Of course, normally when the chop throw mechanism is rotating at high rpm, centrifugal forces acting on the coulter carrier 60, coulter 50, adjustment sleave 80, etc, will push radially outwards on these components, fn other words, when the chop thro mechanism is rotating at high rpm, centrifugal forces will normally cause the coulter carrier 60, adjustment sleeve 80, etc, to be pushed into (and remain in) engagement with the boot 180, even though the keeper 190 is disengaged.

[00124] However, as mentioned above, occasionally a foreign object, such as a large rock or a length of steel (e.g. a steel post or star picket) or the like, may become caught up in the moving mat of cane. Such a foreign object may therefore travel or be carried with the cane mat through the feed train, through the profile converter 34 and out ove the edge of the anvil wear plate 44. Thus, the foreign object may become positioned in the path the coulters 50 as they rotate and contact the anvil wear plate 44 to cut the cane into billets. In light of this, if the coulters 50 (and the components to which they are attached) were permanently fixed to the boot 180 (or otherwise permanently fixed in radial position) then the coulters 50 (and possibly other connected components as well) might be severel damaged or destroyed upon coulter 50 colliding with such a heavy/hard foreign object. However, the coulters 50 are not simply fixed in radial position when the chop throw mechanism is operating at high rpm. Rather, when the chop throw mechanism is operating at high rpm, the respective coulter carriers 60 (along with the other components attached thereto) are able to move radiall inward along the spindle 70. This helps to allow the coulters 50 (and other connected components) to avoid or minimise damage in such situations. [00125] More specifically, if a foreign object such as a rock or the like moves over the anvil wear plate 44 into the path of the rotating coulters 50, then at least one (and possibly multiple or all) of the rotating coulters 50 will collide with that foreign object. However, rather than damaging the coulters, in this situation each coulter will instead simply roll along the anvil wear plate 44 as per the normal cutting action until it collides with the foreign object, at which point the collision will cause the coulter 50 to be pushed radially inwards (i.e. pushed inward against the centrifugal forces). When this occurs, the coulter carrier 60 (along with the other components) will slide radially inward along the spindle 70 a sufficient distance to allow the coulter 50 to effectively roll "up and over" the rock/foreign object. After the coulter 50 has moved/rolled over the foreign object, the centrifugal forces will again cause the coulter carrier 60 (and the coulter 50 and other components) to move radially back outward along the spindle 70, back into engagement with the boot 180. In other words, in the event of a collision between a coulter 50 and a foreign object passing over the anvil wear plate 44, the coulter 50 will roll up and over the foreign object, rather than attempting to force its way through the foreign object, which could otherwise cause severe damage.

[00126] There is also anothe consequence of the rolling action of the coulters 50 that should be appreciated. Because the coulters 50 contact with, and roll along, the anvil wear plate 44, at ail times while a coulter is passing (cutting) through the mat of cane, the angle at which each coulter 50 contacts the wear plate 44 at the point of contact their between is vertical/perpendicular to the wear plate 44. This largely eliminates the detrimental squeezing effect (which damages the billets and leads to juice loss) which is often associated with rotary choppers.

[00127] The function of the respective tiller arms 200 associated with each coulter subassembly will now be explained. However, before referring to the tiller arms 200 specifically, an aspect of the chop throw mechanism concerning the orientation of the coulters 50 should first be appreciated. From a number of the Figures including Figures 4 and 6, it can be seen that each of the coulters 50 comprises a generally flat circular disc, and that the plane of each coulter disc is approximately perpendicular to the direction that the moving mat of cane moves in as it passes out of the profile converter 34 and over the anvil wear plate 44. In other words, the coulters are approximately parallel to the anvil 40. However, importantly, the respective coulters 50 preferably should not be oriented exactly perpendicular to the direction of the moving cane (i.e. they should not be exactly parallel to the anvil). If they were, they could potentially block at least some of the moving cane from moving out over the edge of the anvil wear plate 44. Therefore, it is to be clearly understood that in the particular embodiment illustrated the respective coulters 50 are oriented such that their discs define planes which are slightly at an angle (rather than perfectly perpendicuiar) to the direction that the moving mat of cane moves in as it passes out over the anvil wear plate 44. in other words, each of the coulters 50 is oriented at an angle relative to the plane of the anvil 40. This slight angle between the orientation of the respective coulters 50 and the plane of the anvil is visible in Figure 4 (it can also be appreciated in other Figures).

[00128] One significant consequence of the angle at which the coulters 50 are oriented relative to the plane of the anvil 40 is that, when the cho throw mechanism is rotating at speed to cut the cane into billets, the angle of the coulters as they engage the cane creates a slight impeller-like (or auger-like) action. In other words, because of the angle of the coulters 50, and hence the angle at which the coulters 50 contact the moving cane mat to chop the cane into billets, each passing coulter 50 slightly accelerates the cane in the cane's direction of travel as the coulter 50 passes and cuts the cane. This, in turn, helps to ensure that the speed of the moving cane mat is maintained approximately constant. Put another way, due to the said impeller-like (or auger-like) action of the coulters 50, the moving mat of cane is not temporarily stopped or stalled when a coulter 50 cuts into and through the cane to chop it into billets. The coulters' impeller-like action therefore helps to maintain a generally continuous and steady flow-rate of cane.

[00129] At this point it should be recalled that the cho throw mechanism (and also other components such as the chute, etc) can switch to deliver cut cane billets to the left-hand side of the harvester rather than the right-hand side, or vice versa. In order to enable this, the direction of rotation of the chop throw mechanism must be reversed. For instance, referring to Figure 6 as an example, the direction of rotation of the chop throw mechanism would need to be changed so that instead of rotating in the direction of arrow "B", the chop throw mechanism would instead rotate in the direction opposite to arrow "B". Furthermore, and importantly, if the direction of rotation of the chop throw mechanism is reversed, the angle of the coulters 50 relative to the plane of the anvil 40 must also be switched to ensure that the impeller-like action of the coulters still helps to propel the cane in the correct direction after the reversal (i.e. when the mechanism is rotating in the opposite direction). The orientation of the each individual coulter 50 is controlled by its associated tiller arm 200. [00130] As shown in Figures 14 and 15, each tilier arm 200 includes a centra! portion 210, and on each central portion 210 the end which points towards the spindle 70 comprises a U-shaped portion. The U-shaped portion forms two legs 214, and when the mechanism is assembled the respective legs 214 are positioned on either side of the cylindrical portion 66 of the associated coulter carrier 60. There is a hole in the distal end of each leg 214, and a bolt 216 is inserted through eac said hole to thereby pivotally connect the respective legs 214 to the cylindrical portion 66 of the coulter carrier 60. Hence, when the legs 214 of the tiller arm are connected by bolts 216 to the coulter carrier 60, the tiller arm 200 can pivot relative to the coulter carrier 60 about an axis corresponding to the common axis of the bolts 216.

[00131] The opposite end of each tiller arm's central portion 210 contains a hollow cylindrical bore 218. The cylindrical bore 218 in each tilier arm is operable to receive a cylindrical rod portion 220 of the tiller arm. The rod portions 220 associated with each respective tiller arm 200 are visible in the exploded view in Figure 9. As shown in Figure 9, each of the rods 220 is attached to the set hub 250. Hence, the respective rod portions 220 are shown as part of the set hu subassembly (the set hub subassembly is the subassembly which is illustrated in the centre in Figure 9). When the set hub subassembly and the coulter subassembly (the subassembly on the right in Figure 9) are connected together, the respective rod portions 220 insert into the cylindrical bores 218 in the respective central portions 210 to form the respective tilier arms 200. In other words, in each case, the tiller arm 200 is formed by the insertion of a rod portion 220 into the central portion 210. In each tiller arm, the rod portion 220 is telescopic within the central portion 210. That is, the rod portion 220 is able to slide in and out relative to the bore 218 in the central portion 210. The reason for this will be explained below.

[00132] As mentioned above, one end of each rod 220 inserts into the bore 218 in the corresponding central portion 210 of the tiller arm. On the other end, each rod 220 has both a hinged connection 222 and a swivel connection 224 connectin it to the set hub 250. Each hinged connection 222 comprises a yoke. The hinged connections 222 are therefore generall similar to the hinged connections on the other end of the respective tiller arms 200 (i.e. between the U-shaped portion of the tiller arm and the associated coulter carrier 60). Thus, the hinged connection 222 on each tiller arm 200 allows the tiller arm to pivot about an axis defined by the pin of the hinge. In contrast, each of the swivel connections 224 is formed by the connecting end portion of the tiller arm which slots over and becomes pivotable on a boss extending through a respective flange on the set hub 250. (Two of these swivel connections 224 are clearly illustrated in Figure 9). Hence, tfie swivel connection 224 of each tiller arm 200 allows for angula movement of the tiller arm about the axis of the said boss, or in other words, each tiller arm is capable of angular movement about an axis which is perpendicular to the axis of the hinged connection 222 and also perpendicular to the drive shaft 100.

[00133 j The hinged connections on both ends of each tiller arm 200 (that is the hinged connection 222, and the hinged connection to the associated coulter carrier 60, for each tiller arm) allow the coulter 50 (etc) to deflect in the manner described above, for example to prevent damage in the event of a rock o other foreign object entering the chop throw mechanism through the feed train. Indeed, as explained above, in the event that a coulter 50 strikes a rock, this will cause the coulter carrier 60 to which that coulter 50 is attached to slide radially inward along the associated spindle 70 (to allow the coulter to move/roll up and over the rock). It will now be appreciated that, because the U-shaped portion 212 of the associated tiller arm 200 is connected to the coulter carrier 60, the point of connection between the coulter carrier 60 and the U-shaped portion 212 of the tiller arm will also move inward along the spindle 70 in this situation. (Of course, centrifugal forces will cause the coulter carrier 60 and coulter 50, etc, to move radially back outward along the spindle 70 once the coulter 50 has cleared the rock. The connection between the coulter carrier 60 and the U-shaped portion of the tiller arm 212 will also then move back outward.) As the coulter carrier 60 moves along spindle 70 (in or out), this will cause the tiller arm 200 to pivot at its hinged connections on both ends (i.e. to accommodate the changing orientation of the tiller arm). Those skilled in the art will also appreciate that the movement of the coulter carrier 60 along the spindle 70 will generally also cause the distance between the hinged connection 222 (on one end of the tiller arm) and the hinged connection to the coulter carrier 60 (on the other end of the tiller arm) to change. This means that the length of the tiller arm 200 must be able to change. The length of the tiller arm may increase or decrease depending on the relative positions of the components at the instant in question. In any case, the way the rod portion 220 is telescopically movable (in and out) relative to the bore 218 in the central portion 210 in each tiller arm is what enables the length of the tiller arm to dynamically change to accommodate the deflection of the coulter 50 described above.

[00134] Next, the purpose of the swivel connection 224 between each tiller arm and the set hub 250 will be explained. From above, it will be recalled that if the chop throw mechanism is to be switched to deliver cut cane billets to the left-hand side rather than the right-hand side, or vice versa, the direction of rotation of the chop throw mechanism must be reversed, and the angle of the coulters 50 relative to the plane of the anvil 40 must also change to ensure that the impeller-like action of the coulters still helps to propel the cane in the correct direction. It is the swivel connection 224 between each tiller arm and the set hub assembly that enables the angle of each coulter 50 to change appropriately relative to the plane of the anvil 40. In this regard, it should be understood that the tiller arms 200 are able to swivel freely on or about their respective swivel connections 224. Furthermore, when the direction of the chop throw mechanism's rotation is switched/reversed, the tiller arms 200 each automaticall pivot to become reoriented relative to the anvil 40 at the correct angle to ensure that the impeller-like (or auger-like) action occurs when the mechanism is rotating in the new direction. (Note that the swivel joints 224 could instead be bail joints or tie rod ends or the like).

[00135] Next, the way in which rotation is transmitted into the different parts of the chop throw mechanism will be explained. Referring again to Figure 9, it will be recalled that the chop throw mechanism may be thought of as being made up (notionally) of three subassemblies, namely the paddle subassembly (shown on the left in Figure 9}, a set hub subassembly (shown in the middle in Figure 9) and the coulter subassembly (shown on the right in Figure 9). When all three subassemblies are assembled together and the chop throw mechanism is operating, ail three subassemblies rotate about a common rotational axis (the axis of the main driveshaft 100). However, the way in which rotation is transmitted into each of these subassemblies is explained below.

[00136] Firstly, the harvester's engine (which is mounted towards the rear of the harvester) delivers rotation to the main driveshaft 100. Also, it has already been explained that the paddle subassembly includes the paddle rotor 1 10, and that the paddle rotor 110 is keyed directly into the main driveshaft 100. Consequently, the main driveshaft 100 and the paddle rotor 1 10 are effectivel fixed together. Hence, the rotation of the main driveshaft 100 directly causes rotation of the paddle rotor 1 10 in the same direction and at the same rotational speed. However, neither the set hub subassembly nor the coulter subassembly are keyed or otherwise directly connected to the main driveshaft 100. On the contrary, both are abie to rotate (at least to some extent) relative to the main driveshaft 100.

[00137] Referring to the set hub subassembly, this subassembly includes as its main/central component the set hub 250 mentioned above. When the cho throw mechanism is assembled, the set hub 250 is mounted in a freewheeling manner on the driveshaft 100. That is, the set hub 250 is not connected directly to the drive shaft 100, meaning that the set hub 250 is able to pivot (at least to some extent) about/relative to the driveshaft. The set hub 250 includes a central cylindrical portion 252 the length of which extends parallel to the driveshaft 100. In fact, the central cylindrical portion 252 of the set hub 250 has a hollow bore extending therethrough, and when the mechanism is assembled the driveshaft 100 extends through the bore in the cylindrical portion 252. However, as just noted, the driveshaft 100 and the set hub 250 are not directly connected and the set hub 250 is able to pivot (at least to some extent) about/relative to the driveshaft. The set hub 250 also includes a disc portion 254 which is the larger diameter portion located on the end of the cylindrical portion 252 nearer the paddle rotor 1 10. On the other end of the central cylindrical portion 252, the set hub 250 includes a straight sided plate portion 256. The straight sides of the plate portion 256 are visible in certain other Figures, including Figures 7 and 8. The flanges through which bosses are inserted to form the swivel connections 224 (for the respective tiller arms 200) extend from the disc portion 254 of the set hub. Two of the said flanges are sized so as to be large enough only to accommodate the boss in order to form the swivel connection 224. However, the third of the said flanges, identified by reference numeral 258, is wider and extends circumferentiaily a short distance to either side of its swivel connection 224. The extending portions 258 on either side of this particular swivel joint 224 each form a "stop", the purpose of which will be discussed further below.

[00138] There is also a first twin drive dog component 260 connected to the set hub. More specifically, the first twin drive dog component 260 includes a plate portion which is attached to the surface of the disc portion 254 of the set hub on the side of the disc portion 254 that faces the paddle rotor 1 10. The first twin drive dog component 260 also includes a pair of flanges or "dogs" which project out perpendicular to the disc portion 254. Hence, the two "dogs" of the first twin drive dog component form flanges which extend towards the paddle rotor. The two "dogs" and the plate portion of the first twin drive dog component 260 (i.e. these individual parts of the first twin drive dog component 260) are not individually identified by reference numerals. However, the two "dogs" at least are visible in several of the Figures.

[00139] In operation, the first twin drive dog component 260 interacts with a first single drive dog component 270 which is connected to the padd!e rotor 1 10. The first single drive dog component 270 includes a portion which is attached to the surface of the paddle rotor 110 on the side of the paddle rotor 110 that faces the set hub 250, The first single drive dog component 270 also includes a single flange or "dog" which projects out perpendicular to the paddle rotor 110. Hence, the single "dog" of the first single drive dog component forms a flange which extends towards the set hub 250. Also, and importantly* the first single drive dog component 270 is mounted on the paddle rotor 110 at a position such that, when the chop throw mechanism is assembled, the "dog" of the first single drive dog component 270 is always positioned in between the two "dogs" of the first twin drive dog component 260.

[00140] The chop throw mechanism also includes a second twin drive dog component 280 connected to the set hub. More specifically, the second twin drive dog component 280 includes a plate portion which is attached to the plate portion 256 of the set hu on the side of the set hub's plate portion 258 that faces the coulter hub 90. The second twin drive dog component 280 also includes a pair of flanges or "dogs" which project out perpendicular to the set hub's plate portion 256. Hence, the two "dogs" of the second twin drive dog component form flanges which extend towards the coulter hub 90. The two "dogs" and the plate portion of the second twin drive dog component 280 (i.e. these individual parts of the second twin drive dog component 260} are not individually identified by reference numerals. However, the two "dogs" at least are visible in several of the Figures.

[00141] In operation, the second twin drive dog component 280 interacts with a second single drive dog component 290 which is connected to the coulter hub 90, More specifically, the second single drive dog component 290 is connected to the disc-like part 92 of the coulter hub. In fact, the second single drive dog component 290 includes a portion which is attached to the disc-like part 92 of the coulter hub 90 on the side thereof that faces the set hub 250. The second single drive dog component 290 also includes a single flange or "dog" which projects out perpendicular to the disc-like part 92. Hence, the single "dog" of the second single drive dog component forms a flange which extends towards the set hub 250. Also, and importantly, the second single drive dog component 290 is mounted on the disc-like part 92 of the coulter hub at a position such that, when the chop throw mechanism is assembled, the "dog" of the second single drive dog component 290 is always positioned in between the two "dogs" of the second twin drive dag component 280.

[00142] To understand the interaction between the first single drive dog component 270 and the first twin drive dog component 260, it is useful to refer to Figure 7. in Figure 7, the chop throw mechanism is assembled and rotating. More specifically, the dnveshaft 100 is rotating (driven by the harvester's engine) in the direction of arrow Έ". Therefore, because the paddle rotor 1 10 is fixedly connected to the dnveshaft 100, it follows that the paddle rotor 1 10 is also rotating in the direction of arrow "E" at the same rotational speed. Furthermore, because the first single drive dog component 270 is fixedly mounted to the paddle rotor 1 10, it follows that the first single drive dog component is also rotating wit the paddie rotor. As shown in Figure 7, when the first single drive dog component 270 rotates with the paddie rotor in the direction shown, this causes the "dog" of the first single drive dog component 270 to engage with, and press against, one of the "dogs" of the first twin drive dog component 260. Hence, the first single drive dog component 270 presses against one of the dogs of the first twin drive dog component 260, and the rotation of the paddle rotor 1 10 is thereby transferred to cause rotation of the set hub 250 (to which the first twin drive dog component 260 is attached). This is therefore how rotation is transferred into the set hub 250.

[00143] At this point, it should again be recalled that if cut cane billets are to be delivered to the left-hand side of the harvester rather than the right-hand side, or vice versa, this requires (among other things) reversing the direction of rotation of the chop throw mechanism. The fact that the coulters, etc. can be reoriented to allow this was mentioned above. In any case, it will be understood that reversing the direction of rotation of the chop throw mechanism means (among other things) that the driveshaft 100 must rotate in the opposite direction. This in turn means that the paddle rotor 110 will also rotate in the opposite direction, because the paddle rotor 1 10 is fixedly connected to the driveshaft 1 0. it will now also be understood that, if the direction of rotation of the driveshaft and paddle rotor is reversed, this means the first single drive dog component 270 (which is attached to the paddle rotor) will instead engage with the other of the "dogs" of the first twin drive dog component 260. For instance, referring to Figure 7, if the direction of rotation were to be reversed compared to the direction shown (i.e. if the direction of rotation were to be opposite to arrow "E"), the single drive dog component 270 would not engage with the particular "dog" of the first twin drive dog component 260 as shown, but would instead contact and push against the other of the "dogs" of the first twin drive dog component 260. Hence, if the direction of rotation is reversed, the first single drive dog component 270 will engage with the othe of the "dogs" on the first twin drive dog component 260 so that the opposite-direction rotation is thereby transmitted into the set hub 250 (i.e. so that the set hub rotates in the said opposite direction).

[00144] The spacing in between the respective "dogs" on the first twin drive dog component 260 is important. This is because, if the mechanism is switched to rotate in the opposite direction, as part of this the paddle rotor 1 10 must be rotated relative to the set hub 250 such that the first single drive dog component 270 disengages from one of the "dogs" on the first twin drive dog component 260 and engages with the other of the "dogs" on the first twin drive dog component 260. The arc-shaped spacing in between the respective "dogs" on the first twin drive dog component 260 (i.e. the arced spacing between these "twin dogs", which is 50° in the particular embodiment illustrated) therefore defines the distance which the paddle rotor 1 10 must rotate relative to the set hub 250 for the first single drive dog 270 to disengage one of the twin dogs and engage the other of the twin dogs.

[00145] At this point, it should be recalled that the paddles 112 and 1 14 are connected to the paddle rotor 1 10 and therefore move with the paddle rotor 1 10. It should also be recalled that, when the chop throw mechanism is operating, each pair of rotating paddles 1 12, 114 rotates closely behind (i.e. "follows") a respective coulter 50 in order to sweep up billets cut by that coulter. It will therefore be understood that, if the mechanism is switched to rotate in the opposite direction, each pair of paddles 1 12, 114 must be repositioned so that, instead of being adjacent one particular coulter (as it would be for the original direction of rotation), that pair of paddles 1 12, 1 14 becomes positioned adjacent another coulter such that those paddles will then "follow" that other coulter when the mechanism rotates in the opposite direction. Therefore, the arced spacing in between the respective "dogs" on the first twin drive dog component 260 (which defines the extent of the relative rotation possible between the paddle rotor 1 1 0 and the set hub 250) is specifically set so that, when the paddle rotor 1 10 rotates to disengage the dog 270 from one of the twin dogs and engage it with the other of the twin dogs, the distance which the paddle rotor rotates relative to the set hub 250 is the distance required to correctly position the paddles relative to the alternative coulter.

[00146] To understand the interaction between the second single drive dog component 290 and the second twin drive dog component 280, it is useful to refer to Figure 8. In Figure 8, the chop throw mechanism is again assembled and rotating. More specifically, the driveshaft 100 is rotating (driven by the harvester's engine) in the direction of arrow "F". Because the paddle rotor 1 10 is fixedly connected to the driveshaft 100. it follows that the paddle rotor 1 10 is also rotating in the direction of arrow "F" at the same rotational speed. Furthermore, because the rotation from the paddle rotor 1 10 is transmitted to cause rotation of the set hub 250 by interaction of the first single drive dog component 270 with the first twin drive dog component 260 (as explained above), it follows that the set hub 250 is also rotating at the same speed in the direction of arrow "F". Next, because the second twin drive dog component 280 is fixedly mounted to the plate portion 256 of the set hub, it follows that the second twin drive dog component 280 is also rotating with the set hub. As shown in Figure 8, when the second twin drive dog component 280 rotates with the set hub, this causes one of the "dogs" of the second twin drive dog component 280 to engage with, and press against, the "dog" of the second single drive dog component 290. Hence, one of the dogs of the second twin drive dog component 280 presses against the dog of the second single drive dog component 290, and the rotation of the set hub 250 (which is the same as the rotation of the paddle rotor and driveshaft) is thereby transferred into the coulter hub 90 (to which the second single drive dog component 290 is attached). This is therefore ho rotation is transmitted into the coulter hub 90, and from above it will be understood that rotation of the coulter hub 90 is what ultimately causes the coulters 50, etc, to move in a circular path to perform the cutting action.

[00147] It will be understood that, if the direction of rotation of the driveshaft and paddle rotor is reversed, this means the second single drive dog component 290 (which is attached to the coulter hub 90) will instead engage with the other of the "dogs" on the second twin drive dog component 280. For instance, referring to Figure 8, if th direction of rotation were to be reversed compared to the direction shown (i.e. if the direction of rotation were to be opposite to arrow "P the single drive dog component 290 would not engage with the particular "dog" of the second twin drive dog component 280 shown, but it would instead be contacted and pushed b the other of the "dogs" on the second twin drive dog component 280. Hence, if the direction of rotation is reversed, the second single drive dog component 290 will engage with and be pushed by the other of the "dogs" on the second twin drive dog component 280 so that the opposite-direction rotation is thereby transmitted from the set hub 250 into the coulter hub (i.e. so that the coulter hub rotates in the said opposite direction).

[00148] The spacing in between the respective "dogs" on the second twin drive dog component 280 is important. This is because, if the mechanism is switched to rotate in the opposite direction, as part of this the angle of the coulters 50 relative to the plane of the anvil 40 must adjust to ensure that the impeller-like action of the coulters still helps to propel the cane in th correct direction (even when the mechanism is rotating the other way). The arc-shaped spacing in between the respective "dogs" on the second twin drive dog component 280 (i.e. the arced spacing between these "twin dogs", which is 20° in the particular embodiment illustrated) defines the distance which the coulter hub 90 can rotate relative to the set hub 250 when the second single drive dog 290 disengages one of the twin dogs and engages the other of the twin dogs. At this point, it should be recalled that each of the tiller arms 200 is free to pivot at the swivel joint 224 that connects that tiller arm 200 to the set hub 250. Hence, when the direction of rotation is reversed and the second single drive dog component 290 disengages from one "dog" of the second twin drive dog component 280 and moves toward engagement with the other "dog" of the second twin drive dog component 280, at the same time, this rotation of the coulter hub 90 relative to the set hub 250 automatically causes the orientation of each of the tiller arms 200 to change (each by pivoting about its swivel joint 224). Furthermore, by the time the second single drive dog component 290 engages with the other "dog" of the second twin drive dog component 280, the tiller arms 200 will have reoriented themselves so as to precisely angle the respective coulters 50 at the correct angle relative to the anvil 40 to create the required in impellerlike action on the cane mat when the mechanism begins rotating in the new direction. Hence, the arced spacing between the two dogs of the second twin drive dog component 280 is sized specifically such that, when the direction of rotation of the mechanism is reversed, the tiller arms 200 automatically swivel/reorient to correctly angle the coulters 50 relative to the anvil 40 to ensure the required impeller-like action occurs when the mechanism rotates in the new direction.

[00149] From the discussion above, it will be understood that when the chop throw mechanism is being switched to the rotate in one direction rather than the other, the ability of the set hub 250 to rotate somewhat relative to the paddle rotor 1 10, and the ability of the coulte hub 90 to rotate somewhat relative to th set hub 250, allows the necessary reorientation of components. However, as will now be explained, the chop throw mechanism also incorporates means for preventing relative rotation between the paddle rotor 1 10 and the set hub 250, and between the set hub 250 and the coulter hub 90, when the chop throw assembly is operating at high rpm. This is achieved by pivotable locking arms, as discussed below. [00150] Before referring to the pivotable locking arms specifically, it should be recalled that the disc-like portion 254 of the set hub 250 has a number of flanges each of which accommodates the boss of one of the swivel joints 224, and one of these flanges is wider than the others. The portions of this wider flange 258, on either side of the boss forming this particular swivel joint 224, each form a "stop", it should also be noted that there is a "stop" flange 259 formed as part of the plate portion 256 on the set hub 250. The pivotable locking arms interact with these "stops" in the manner discussed below.

[0015!] One of the pivotable locking arms 300 is mounted to the paddle rotor 1 10, as shown in Figure 1 1 for instance. From Figure 11 , it can be seen that there is a pair of mounting flanges projecting out from the paddle rotor 1 10, and the locking arm 300 is pivotally mounted on a pin extending between these mounting flanges. A spring 302 is also provided. The spring 302 is mounted in tension. One end of the spring 302 is attached to the locking arm 300 near where the locking arm 300 pivotally connects to the mounting flanges. The other end of the spring 302 is attached to a further mounting flange located on the paddle rotor a short distance away. The spring 302 imposes a bias on the locking arm 300. More specifically, the bias created by the spring 302 tends to cause the locking arm 300 to pivot about its pivotal connection such that the distal free end of the locking arm 300 moves towards (and rests against) the surface of paddle rotor 1 10 (as shown in Figure 1 1 ).

[00152] The other of the pivotable locking arms 310 is mounted to the disc portio 92 of the coulter hub 90. This can be seen in Figure 1 1 , and also in Figure 10 (although it should be noted that the orientation of the locking arms 300 and 310 in Figure 10 is different to in Figure 1 1 for reasons discussed below). If can be seen that there is a pair of mounting flanges projecting out from the disc portion 92, and the locking arm 310 is pivotally mounted on a pin extending between these mounting flanges. A spring 312 is also provided. The spring 312 is mounted in tension. One end of the spring 312 is attached to the locking arm 310 near where the locking arm pivotally connects between the mounting flanges. The spring 312 then extends through an opening in the disc-like portion 92 and the other end of the spring 312 attaches between a pair of mounting flanges on the opposite side of the disc-like portion 92. The spring 312 imposes a bias on the locking arm 310. More specifically, the bias created by the spring 312 tends to cause the locking arm 310 pivot about its pivotal connection such that the distal free end of the locking arm 310 moves towards (and rests against) the surface of the disc-like portion 92 of the coulter hub 90, as illustrated in Figure 1 1 ,

[00153] Thus, when the chop throw mechanism is stationary (e.g. as it is when it is being switched for opposite-direction rotation} the bias created by spring 302 causes the locking arm 300 to rest with its distal free end against the surface of the paddle rotor 1 10, and the bias created by spring 312 causes the locking arm 310 to rest with its distal free end against the surface of the disc-like portion 92 of the coulter hub 90. These are the positions in which the respective locking arms 300 and 310 are shown in Figure 1 1 . When in these positions, the respective locking arms 300 and 310 are pivoted "out of the way" of their associated "stops". That is, the locking arm 300 is pivoted out of the wa such that it does not engage with either of the stops 258. The locking arm 300 therefore does not prevent the stops 258 from moving past the locking arm 300, meaning that rotation of the set hub 250 relative to the paddle rotor 1 10 is possible. Similarly, when in the position shown in Figure 1 1 , the locking arm 310 is pivoted out of the way such that it does not engage with either side of stop flange 259. The locking arm 310 therefore does not prevent the stop flange 259 from moving past the locking arm 310, meaning that rotation of the coulter hub 90 relative to the set hub 250 is possible. Thus, when pivoted as shown in Figure 1 1 , the locking arms 300 and 310 do not impede the relative rotation between subassemblies necessary for the various components to reorient themselves for opposite direction rotation, as discussed above.

[00154] However, when the chop throw mechanism is operating at high rpm, centrifugal forces cause the respective locking arms 300 and 310 to pivot against the bias is of their respective springs. That is, the respective locking arms 300 and 310 pivot from the orientations shown in Figure 1 1 into the orientations shown in Figure 10. (Figure 10 therefore shows the chop throw mechanism operating at high rpm.) In Figure 10 it can be seen that centrifugal forces have caused the locking arm 300 to pivot out so the locking arm 300 is approximately parallel to the paddle rotor 110 (perpendicular to the drive shaft) and such that the locking arm 300 engages against the edge of one of the stops 258. Importantly, when the locking arm 300 engages against one of the stops 258 as shown, this effectively locks the set hub 250 relative to the paddle rotor 1 10 (i.e. it prevents relative rotation between the set hub 250 and the paddle rotor 1 10). It does so by preventing the first single drive dog component 270 from disengaging from the relevant "dog" of the first twin drive dog component 260. By preventing relative rotation between the set hub 250 and the paddle rotor 1 10 when the chop throw mechanism is rotating at high rpm, damage or imbalance that might occur if such relative rotation (or rattling) were possible is prevented.

[00155] Likewise, Figur 10 also shows how centrifugal forces cause the locking arm 310 to pivot out so that the locking arm 310 is approximately perpendicular to the drive shaft, and so that the locking arm 310 engages against one side of the stop flange 259, Importantly, when the locking arm 310 engages one side of the stop flange 259 as shown, this effectively locks the set hub 250 relative to the coulter hub 90 (Le, it prevents relative rotation between the set hub 250 and the coulter hub 90). It does so by preventing the second single drive dog component 290 from disengaging from the relevant "dog" of the second twin drive dog component 280. By preventing relative rotation between the set hub 250 and the coulter hub 90 when the chop throw mechanism is rotating at high rpm, damage or imbalance that might occur if such relative rotation (or rattling) were possible is prevented.

[00156] If the chop throw mechanism were rotating at high rpm but in the opposite direction compared to Figure 10, the locking arm 300 would operate in exactly the same way, but it would instead engage on the opposite side of stop 258, and this would thereby lock the first single drive dog 270 in engagement with the other of the "dogs" of the first twi drive dog component 260. Likewise, if the mechanism were rotating at high rpm but in the opposite direction compared to Figure 10, the locking arm 310 would also operate in exactly the same way, but it would instead engage on the opposite side of stop 259, and this would thereby lock the second single drive dog 290 in engagement with the other of the "dogs" of the second twin drive dog component 280.

[00157] As has previously been mentioned, if the harvester is to be switched so as to deliver cut cane billets to one side rather than the other, the chute 130 must be reoriented so that, instead of extending out to one side of the harvester, it extends out to the other side. For instance, Figures 1 and 2 illustrate the chute extending out to the left-hand side of the harvester. In contrast, Figure 3 illustrates the chute 130 extending out to the right hand side of the harvester. The particular mechanism by which the chute 130 is re-oriented in this way (and the components involved) is not critical to the invention. Indeed, any suitable means for enabling the chute to be rotated or otherwise re-oriented may be used. For example, the chute 130 (and the various other components mounted thereon) might be disconnected/detached from the rest of the harvester and rotated 180° before being reattached/connected facing the other way. Alternatively, some form of rotational mechanism might be provided to enable the chute 130 to be re-oriented without being detached/disconnected from the rest of the harvester.

[00158] It should also be recalled that, in operation, the mat of cane stalks passes over the anvil wear plate 44 and is chopped into billets by the passing coulters 50. After being cut, the billets collect (temporarily) below the anvil in the bottom of the trough component 46. The trough 46 extends approximately ¥4 of the way around the outside circumference of the cutting mechanism, and on one end the trough 46 extends all the way up to and joins with the chute 130. The chute 130 then extends up and out from the cutting mechanism. This is clearly shown in Figure 6.

[00159] As will now be appreciated, if the chute 130 is reoriented to face in the opposite direction, the trough 46 must be rotated so that when the chute 130 is facing in the opposite direction the trough 46 (again) effectively joins up with the base of the chute 130 thereby ensuring that cut cane billets which are conveyed along and up within the trough 46 by the paddles then continue up into, and then out through, the chute 130.

[00160] This may be visualised with reference to Figure 6. In Figure 6, the chute 130 is shown oriented in one direction. (Figure 6 actually shows the chute and cho throw mechanism from the front looking back, and therefor in Figure 6 the chute 130 is actually oriented to deliver cut cane billets to the right hand side.) In any ease, as can be seen in Figure 6, on one side, the trough 46 extends around and joins up with the base of the chute 130. This is to ensure that cut cane billets which are conveyed through the trough 46 are thrown up into the chute 130 as discussed above. However, if the chute 130 in Figure 6 were instead oriented to face the other way (i.e. opposite to the direction shown), the trough 46 would need to be rotated approximately 90° in the direction indicated by arrow "L" to thereby cause the other end of the trough 46 (which is indicated by reference numeral 46'} to join up with the base of the chute,

[00161] The mechanism used for rotating the trough 46 as just described is best visible in Figures 2. 3, 4 and 16. From these Figures it can b seen that there is a hydraulic cylinder 48 positioned just behind the trough 46. From Figures 3, 4 and 16 it can also be seen that the upper end of the hydraulic cylinder 48 is connected to an eccentric counter arm 49 which is in turn connected to the rear of the trough 46. The bottom end of the hydraulic cylinde 48 is connected to a rigid frame point on the harvester as shown in Figure 2. Note that Figures 3 and 6 both show the chute 130 in the same orientation (i.e. both show the chute 130 oriented to deliver cane billets to the right-hand side of the harvester). Note also that in Figures 3 (and the same would be true Figure 6 although the hydraulic cylinder 48 is not visible in Figure 6) the hydraulic cylinder 48 is unextended. The trough 46 can be rotated by pressurisation and extension of the hydraulic cylinder 48. More specifically, if the hydraulic cylinder 48 is extended, the upper end of the hydraulic cylinder 48 will move upwards thereby causing the counter arm 49 to also move in an arc about the chop throw mechanism's axis of rotation. This causes the trough 46 to rotate in the direction indicated b arro "L" in Figure 6, and this is therefore how the trough 46 is rotated as required when the mechanism is reconfigured for opposite direction delivery. By way of further illustration, Figures 2, 4 and 16 illustrate the chop throw mechanism (including the chute 130 and the trough 46) configured for left-hand side delivery. As can be seen in these Figures, the hydraulic cylinder 48 has been extended causing the trough 46 to be in the appropriate orientation for this configuration.

[001.62] To understand the significance of being able to switch the delivery direction (i.e. the ability to switch between the delivering cut cane billets to the left-hand side, or right-hand side, of the harvester), it should be appreciated that a sugarcane harvester will generally travel in one linear direction while harvesting a given row of sugarcane before then turning around to travel back in the opposite linear direction to harvest the next row. Hence, the harvester will generally travel in one direction, then the other, and then back in the first direction, etc, repeatedly and frequently. For example, the harvester may change travel direction 10-15 times per our (depending on the length of the rows of sugarcane to be cut). It should also be understood that, whichever direction the harvester is travelling in at a given time, the shadowing truck/trailer which is carrying the receptacle (which receives the cut cane billets) will need to be on the opposite side of the harvester from the standing rows of unharvested cane. Hence, when the harvester changes direction, the delivery direction wi!l also need to be switched so that cut cane billets continue to be delivered into the receptacle as the harvester travels back in the opposite direction to harvest the next row.

[001.63] In order to allow the particular harvester described above (including the chop throw mechanism described above) to be switched from left-handed delivery to right- handed delivery, or vice versa, after the harvester completes a given row and before it commences back the other way, the rotation of the chop throw mechanism will be stopped. The chute 130 would then be rotated to temporarily face towards the rear (which may be the chute's transport position). The harvester would be driven/turned 180° (i.e. to face the other way) and aligned with the next row to be cut. The chute would be rotated to the opposite side compared to its previous position. The trough 46 would then be rotated to its appropriate position. Rotation of the chop throw mechanism in the appropriate direction would then be engaged/commenced. Re-orientation of the coulters and paddles etc, and the subsequent locking of the various components in their respective positions as the mechanism approaches operational speed, all occurs automatically and simply as a result of changing the rotational direction. Ail of this can be achieved in a matter of seconds, meaning that harvesting time can be maximised (because very little time is lost in switching the harvester's delivery direction).

[00164] In the present specification and claims (if any), the word 'comprising' and its derivatives including 'comprises' and comprise' include each of the stated integers but does not exclude the inclusion of one or more further integers.

[00165] Reference throughout this specification to One embodiment' or ^!an embodiment' means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the present invention. Thus, the appearance of the phrases 'in one embodiment' or 'in an embodiment' in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more combinations.

[00166} In compliance with the statute, the invention has been described in language more or less specific to structural or methodical features. It is to be understood that the invention is not limited to specific features shown or described since the means herein described comprises preferred forms of putting the invention into effect. The invention is, therefore, claimed in any of its forms or modifications within the proper scope of the appended claims (if any) appropriately interpreted by those skilled in the art. INDEX TO FIGURES

upper portion of the profile converter 34 rod which creates the hinged connection between the upper and lower portions of profile converter 34 anvil profile converter springs anvil wear plate trough end of the trough which joins up with the base of the chute 130 if the trough is rotated relative to the position shown in Figure 6 hydraulic cylinder that rotates the trough counter arm on the back of the trough coulter coulter carrier (the part which the coulter 50 directl mounts to) stub axle on the coulter carrier 60 to which the coulter 50 mounts t readed holes i the coulter carrier 60 cylindrical portion of the coulter carrier 60 (to which the tiller arm 200 is attached) cylindrical bore through the coulter carrier 60 coulter spindle bolt which bolts the spindle 70 to the coulter hub 90 plate on the radially inner end of the spindle 70 spindle adjustment scre (for fine adjustment relative to the coulte hub 90) 76 boss where the boot 180 attaches on the end of the spindle 70

77 boot retaining nut

78 boot retaining washer

80 coulter adjustment sleave

81 bolts for attaching the coulter carrier to the sleave

82 bolt slot in the coulter adjustment sleave

84 adjustment rod (for fine adjustment relative to the coulter carrier 60)

85 nuts on adjustment rod 84

86 keeper hook

90 coulter hub

92 disc-like part of the coulter hub 90 oo main drive shaft of the chop throw mechanism

1 10 paddle rotor (i.e. the large disc-like component to which the paddles etc are attached)

1 12 fixed paddle

1 14 hinged paddle

1 16 rounded portion on the inside of the hinged paddle 1 14 which contains the hinge rod

1 18 rounded portion on the paddle rotor 1 1 0 which receives the hinge rod

1 20 connecting member which connects the hinged paddle 1 14 to the sheer

bolt 122

1 22 sheer bolt

130 chute

212 U-shaped portion of the tiller arm 200

214 individual legs defined by the U-shaped portion 21

216 bolts which bolt the legs 214 of the tiller arm to the coulter carrier 60

218 bore in the central portton 210 of the tiller arm 200 which receives a telescopic rod portion 220

220 rod portion which is telescopic in the bore 218 of the tiller arm 200

222 hinged connection between the rod 220 and the set hub assembly

224 swivel joint between the rod 220 and the set hub assembly

250 set hub

252 central cylindrical portion of the set hub 250

254 disc-like portion of the set hub 250

256 straight sided plate portion of the set hub 250

258 stops formed on either side of the flange of one of the swivel joints 224

259 stop on the plate portion 256 of the set hub 250

280 first twin drive dog component (mounted to the disc portion 254 of the set hub)

270 first single drive dog component (mounted to the paddle rotor 1 10)

280 second twin drive dog component (mounted to the plate portion 256 of the set hub)

290 second single drive dog component (mounted to the disc-like part 92 of the coulter hub 90)

300 first locking arm (the one attached to the paddle rotor 1 10)

302 spring associated with first locking arm 300

Claims

1 . A cutting apparatus operable to reeerve a moving feed of material, wherein the material is to be cut into pieces by the cutting apparatus, the cutting apparatus including: a fixed portion over which the material passes, and a rotating portion, wherein the rotating portion includes at least one rolling cutting element that moves in an orbit around the rotating portion's axis of rotation when the rotating portion rotates, the orbit of each cutting element is at an angle to the direction in which the material passes over the fixed portion, and for at least part of each revolution, each cutting element contacts the fixed portion and rolls along or relative to the fixed portion thereupon cutting the material passing over the fixed portion.

2. The cutting apparatus as claimed in claim 1 , wherein the fixed portion comprises an anvil.

3. The cutting apparatus as claimed in claim 1 or 2, wherein the rotating portion includes multiple rolling cutting elements equally spaced around the rotating portion's axis of rotation.

4. The cutting apparatus as claimed in an one of the preceding claims, wherein each of the rolling cutting elements is or includes a substantially (or generally) disc shaped cutting coulter.

5. The cutting apparatus as claimed in claim 4, wherein each coulter is mounted on or relative to a respective radially oriented radial member, each radial member being part of the cutting apparatus's rotating portion, and each coulter is able to rotate relative to its associated radial member.

8. The cutting apparatus as claimed in claim 5, wherein each coulter is able to move radially inward and outward relative to its associated radial member when the rotating portion is rotating at or above a predetermined rotational speed.

7. The cutting apparatus as claimed in claim 6 wherein, when the rotating portion is stationary or rotating below the predetermined rotational speed, each coulter is held in position toward the radially outer end of its associated radial member.

8. The cutting apparatus as claimed in claim 7, wherein the means by which each coulter is held in position toward the radially outer end of its associated radial member when the rotating portion is stationary or rotating below the predetermined rotational speed includes a component which is biased towards a position which causes the coulter to be held toward the radially outer end of its associated radial member, but when the rotating portion is rotating at o above the predetermined rotational speed the bias on the said component is overcome by centrifugal forces causing the said component to move in such a way that the component does not cause the coulter to be held towards the radially outer end of its associated radial member.

9. The cutting apparatus as claimed in any one of claims 4-8, wherein means are provided for adjusting the axial and/or radial position of each coulter.

10. The cutting apparatus as claimed in any one of claims 4-9, wherein the orbit of each coulter is approximately perpendicula to the direction in which the material passes over the fixed portion, but each coulter is oriented at an angle relative to the plane of the orbit such that each coulter cuts through the material at an angle which is not perpendicular to the direction in which the materia! passes over the fixed portion.

1 1 . The cutting apparatus as claimed in claim 10, wherein each coulter cuts through the material at an angle which at least slightly accelerates the materia! in the material's direction of travel.

12. The cutting apparatus as claimed in claim 10 or 1 1 , wherein means are provided for adjusting the angle of orientation of each coulter relative to the plane of the coulter orbit

13. The cutting apparatus as claimed in any one of the preceding claims further including at least one sweeping component that is swept in an orbit around the rotating portion's axis of rotation when the rotating portion rotates, whereby each sweeping component contacts with materia! that has been cut by the cutting element(s) and conveys the cut material away from the fixed portion,

14. The cutting apparatus as claimed in any one of ciaims 4-1 further including a sweeping component associated with each coulter, wherein each sweeping component is swept in an orbit around the rotating portion's axis of rotation when the rotating portion rotates, whereby each sweeping component contacts with material that has been cut by one or more of the coulters and conveys the cut material away from the anvil.

15. The cutting apparatus as claimed in claim 14, wherein each sweeping component comprises a paddie component with at least one contact surface, and when the paddle component is swept in a orbit around the rotating portion's axis of rotation, it's contact surface collides with material that has been cut by one or more of the coulters and conveys the cut material away from the anvil.

16. The cutting apparatus as claimed in claim 15, wherein at least one of the paddle components is operable to pivot such that, in the event of a foreign object passing over the anvil, the paddle component pivots upon contact with the foreign object.

17. The cutting apparatus as claimed in claim 15 or 16 further including a trough and a chute, wherein material cut by one or more of the coulters falls into and/or collects temporarily in the trough, the trough is curved with a radius corresponding to the outer radius of the orbit swept by one or more paddles, one or more of the paddles sweep through the trough whereupon the contact surface(s) thereof collide with cut material and convey the cut material around the trough until the trough opens into the chute whereupon the cut materia! separates from the paddle(s) and travels into the chute exiting the cutting apparatus through the chute.

18. The cutting apparatus as claimed in claim 7, wherein the chute includes one or more of the following: means for allowing or causing the cut material to exit the chute at different points on or along the chute; means for altering the trajectory or direction with which cut material exits the chute; and means for enabling a small amount of material to be temporarily retained in (or collected or stored in) the chute.

19, The cutting apparatus as claimed in any one of claims 2-18, wherein the anvil has a contact edge or surface along or relative to which each cutting element rolls or rotates when in contact with the anvii, the said contact edge or surface being curved with radius substantially corresponding to the outer radius of the coulter orbit.

20, The cutting apparatus as claimed in claim 19 further including a profile converter operable to shape the feed of material to conform (at least generally/approximately) to the shape of the contact edge or surface of the anvi! before or as the material passes over the contact edge or surface.

21. The cutting apparatus as ciaimed in claim 20, wherein the profile converter has an inlet which is shaped to receive the feed of materia! and an outlet which is shaped to conform at least approximately to the shape of the contact edge or surface of the anvii, and when the feed of material passes through the profile converter it is squeezed into the shape of the outlet and therefore exits the profile converter in a shape conforming generally to the shape of the contact edge or surface of the anvil.

22. The cutting apparatus as ciaimed in claim 17 or 18, wherein the material to be cut into pieces by the cutting apparatus is a harvested crop material and the feed of material entering the cutting apparatus contains the harvested crop and also leaf matter and/or other unwanted matter, both the harvested crop and also the unwanted leaf/other matter are cut into pieces by the cutting apparatus and conveyed around the trough and into the chute, wherein the apparatus further includes a blower associated with the chute, the blower is operable to blow air into and/or through the chute in a direction at least partly transverse to the trajectory of the pieces of harvested crop and unwanted leaf/other matter in the chute, whereby the flow of air causes the pieces of unwanted leaf/other matter to separate from the pieces of harvested crop such that the pieces of harvested crop exit the chute separately from the pieces of unwanted leaf/other matter.

3. The cutting apparatus as claimed in any one ol the preceding claims, wherein the apparatus can be configured to operate with the rotating portion rotating in etther one rotational direction or the other about its axis of rotation.