POSITIONING APPARATUS FOR A ROTARY COMBINE HARVESTER

Abstract

The invention provides a positioning apparatus (17) for a rotary combine harvester (100) having a threshing concave (6a) and a separation grate (6b). The apparatus (17) has a concave adjustor mechanism for adjusting a threshing gap between the threshing concave (6a) and a rotor or rotors (5) of the harvester (100). The concave adjustor mechanism has a concave actuator (33) including a concave hydraulic cylinder having an adjustable hydraulic pressure to cause rotation of a concave control arm (31) so as to control a position of the threshing concave (6a). The apparatus (17) also has a grate adjustor mechanism for adjusting a separation gap between the separation grate (6b) and the rotor or rotors (5) of the harvester (100). The grate actuator mechanism has a grate actuator (330) including a grate hydraulic cylinder having an adjustable hydraulic pressure to cause rotation of the grate control arm (310) so as to control a position of the separation grate (6b). The concave hydraulic cylinder and the grate hydraulic cylinder both extend in a longitudinal direction (X) of the apparatus (17). Advantageously, the threshing and separation gaps may be adjusted independently and relatively quickly. Also advantageously, the invention provides a compact, space-saving layout for the apparatus (17).

Claims

1-20. (canceled)

21. A positioning apparatus for a rotary combine harvester having a threshing concave and a separation grate, the positioning apparatus comprising: an elongate member defining a longitudinal direction (X) of the positioning apparatus; a concave adjustor comprising: (i) a concave movable plate attachable to the threshing concave and being movable in a vertical direction (Y) perpendicular to the longitudinal direction (X); (ii) a concave control arm mounted on the elongate member and being pivotable relative to the elongate member about a pivot axis perpendicular to the longitudinal direction (X) and the vertical direction (Y), wherein rotation of the concave control arm causes movement of the concave movable plate; (iii) a concave control rod coupling the concave movable plate and the concave control arm; and, (iv) a concave actuator including a concave hydraulic cylinder having an adjustable hydraulic pressure to cause rotation of the concave control arm so as to control a position of the threshing concave; and a grate adjustor comprising: (i) a grate movable plate attachable to the separation grate and being movable in the vertical direction (Y); (ii) a grate control arm mounted on the elongate member and being pivotable relative to the elongate member about a pivot axis perpendicular to the longitudinal direction (X) and the vertical direction (Y), wherein rotation of the grate control arm causes movement of the grate movable plate; (iii) a grate control rod coupling the grate movable plate and the grate control arm; and, (iv) a grate actuator including a grate hydraulic cylinder having an adjustable hydraulic pressure to cause rotation of the grate control arm so as to control a position of the separation grate, wherein the concave hydraulic cylinder and the grate hydraulic cylinder both extend in the longitudinal direction (X).

22. The positioning apparatus according to claim 21, wherein the concave hydraulic cylinder and the grate hydraulic cylinder extend in a substantially common vertical plane of the positioning apparatus.

23. The positioning apparatus according to claim 21, wherein the concave hydraulic cylinder is positioned above the grate hydraulic cylinder in the vertical direction (Y).

24. The positioning apparatus according to claim 21, wherein the concave control rod is adjacent to the grate control rod.

25. The positioning apparatus according to claim 24, wherein the concave control rod extends substantially parallel to the grate control rod.

26. The positioning apparatus according to claim 25, wherein the concave control rod and the grate control rod extend in the longitudinal direction (X).

27. The positioning apparatus according to claim 21, wherein the concave actuator is configured to cause rotation of the concave control arm against a concave biasing force, and wherein the grate actuator is configured to cause rotation of the grate control arm against a grate biasing force.

28. The positioning apparatus according to claim 27, the concave adjustor comprising a concave spring and the grate adjustor comprising a grate spring, wherein the concave spring provides the concave biasing force against the concave actuator, and wherein the grate spring provides the grate biasing force against the grate actuator.

29. A rotary combine harvester comprising: first and second rotors; first and second threshing concaves extending under and about at least part of a threshing portion of the respective first and second rotors and defining a threshing gap there between; first and second separation grates extending under and about at least part of a separation portion of the respective first and second rotors and defining a separation gap therebetween; and, a positioning apparatus according to claim 21.

30. The rotary combine harvester according to claim 29, wherein the positioning apparatus is arranged centrally relative to the first and second rotors.

31. The rotary combine harvester according to claim 29, wherein the positioning apparatus is arranged above the first and second rotors in the vertical direction (Y).

32. The rotary combine harvester according to claim 29, wherein the first and second threshing concaves each comprise (i) a fixed outer concave edge at an outer side of the respective first and second rotors, and (ii) a movable inner concave edge at an inner side of the respective first and second rotors, wherein actuation of the concave actuator causes movement of the movable inner concave edges so as to adjust the threshing gap, and wherein the first and second separation grates each comprise (i) a fixed outer grate edge at an outer side of the respective first and second rotors, and (ii) a movable inner grate edge at an inner side of the respective first and second rotors, wherein actuation of the grate actuator causes movement of the movable inner grate edges so as to adjust the separation gap.

33. The rotary combine harvester according to claim 29, wherein: the concave actuator and the grate actuator each comprise a hydraulic cylinder; the concave actuator and the grate actuator each comprise pressure control means configured to control the hydraulic pressure in the respective hydraulic cylinders; and, the pressure control means is configured to set the hydraulic pressure in the respective hydraulic cylinders to a predetermined value so as to adjust the threshing and separation gaps to desired values.

34. The rotary combine harvester according to claim 33, wherein the pressure control means is configured to adaptively control the pressure in the hydraulic cylinders to return to the respective predetermined values so as to maintain the threshing and separation gaps at the desired values.

35. The rotary combine harvester according to claim 34, wherein the threshing concaves and the separation grates are configured to move relative to the first and second rotors to increase the respective threshing and separation gaps upon increased pressure being applied to the threshing concaves and separation grates by causing a change in the pressure in the hydraulic cylinders.

36. A rotary combine harvester comprising: first and second rotors; first and second threshing concaves extending under and about at least part of a threshing portion of the respective first and second rotors and defining a threshing gap therebetween; first and second separation grates extending under and about at least part of a separation portion of the respective first and second rotors and defining a separation gap therebetween; and, a positioning apparatus comprising a concave actuator and a grate actuator for respectively adjusting the threshing gap and the separation gap, wherein the positioning apparatus is arranged centrally relative to the first and second rotors.

37. The rotary combine harvester according to claim 36, wherein the positioning apparatus is arranged above the first and second rotors in a vertical direction (Y) of the rotary combine harvester.

38. The rotary combine harvester according to claim 36, wherein: the concave actuator and the grate actuator each comprise a hydraulic cylinder; the concave actuator and the grate actuator each comprise pressure control means configured to control the hydraulic pressure in the respective hydraulic cylinders; and, the pressure control means is configured to set the hydraulic pressure in the respective hydraulic cylinders to a predetermined value so as to adjust the threshing and separation gaps to desired values.

39. The rotary combine harvester according to claim 38, wherein the pressure control means is configured to adaptively control the pressure in the hydraulic cylinders to return to the respective predetermined values so as to maintain the threshing and separation gaps at the desired values.

40. The rotary combine harvester according to claim 39, wherein the threshing concaves and the separation grates are configured to move relative to the first and second rotors to increase the respective threshing and separation gaps upon increased pressure being applied to the threshing concaves and separation grates by causing a change in the pressure in the hydraulic cylinders.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0040] One or more embodiments of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:

[0041] FIG. 1 is a schematic side view of an axial flow combine harvester, showing the position of the rotors, threshing concaves and separation grates;

[0042] FIG. 2 is a schematic end view of a positional apparatus according to an aspect of the present invention, together with the rotors and threshing concaves of FIG. 1, the positional apparatus being for adjusting the position of the threshing concaves relative to the rotors;

[0043] FIGS. 3a and 3b show perspective views of the positional apparatus of FIG. 2;

[0044] FIG. 4 shows a schematic side view of the positional apparatus of FIG. 2;

[0045] FIG. 5 shows an end view of the rotors and the positioning apparatus of FIG. 2;

[0046] FIG. 6 shows a perspective view of the threshing concaves and separation grates of FIG. 1 and the positioning apparatus of FIG. 2; and,

[0047] FIG. 7 shows a cross-sectional side view of the threshing concaves and separation grates of FIG. 1 and the positional apparatus of FIG. 2.

DETAILED DESCRIPTION OF THE DRAWINGS

[0048] The present invention provides positional apparatus for a rotary combine harvester having both threshing concaves and separation grates located under rotors of the combine. In particular, the positional apparatus allows the positions of the threshing concaves and separation grates relative to the rotors to be set independent of each other. Furthermore, the positional apparatus allows the relative positions of the concaves and grates to adaptively adjust in dependence on a pressure applied thereto by crop that is being processed by the combine.

[0049] FIG. 1 shows the main components of an axial flow combine harvester 100, mounted on front and rear wheels 1, 2. Crops are cut from the field by the header assembly 3, and supplied by the feeder 4 to a twin set of rotors 5, arranged along a longitudinal axis of the harvester and tilted slightly upwards with respect to the horizontal. The rotors 5 are rotatably mounted with respect to threshing concaves 6a and separation grates 6b. In the present embodiment, the pair of rotors 5 includes one pair of threshing concaves 6a and one pair of separation grates 6b; however, any suitable number of pairs of threshing concaves and separation grates may be mounted along the length of the rotors.

[0050] The combine 100 includes a driver's cabin 7, as well as a cleaning arrangement comprising a grain pan 8, a set of sieves 9 and a blower 10 for blowing light residue material towards the back of the combine. Grains fall through the sieves and are transported by an assembly of augers and a grain elevator (not shown) to a grain tank 11.

[0051] As schematically illustrated in FIG. 2, for the twin-rotor arrangement of the described embodiment adjustment of the pair of concaves 6a is achieved by pivoting the concaves about their outer edges 15. In the area between the rotors 5, the inner edges of the concaves are suspended from a concave movable plate or divider 16, which is movable upwards or downwards along a vertical axis or direction Y as indicated by the arrows in FIG. 2. The concave movable plate 16 is part of a positioning apparatus 17, which controls movement of the concave movable plate 16. The positioning apparatus 17 is arranged above the rotors 5 centrally between them.

[0052] Note that adjustment of the separation grates 6b is achieved in a similar manner. In particular, the positioning apparatus 17 also includes, and controls movement of, a grate movable plate or divider (not shown in FIG. 2) which causes adjustment of the separation grates 6b by pivoting them about their outer edge.

[0053] FIGS. 3a and 3b show perspective views of the positioning apparatus 17. The apparatus 17 comprises an elongate gutter-shaped structure or member 20 which may be mounted to the chassis of the combine 100 such that it is fixed relative to the rotors 5. The elongate member 20 defines a longitudinal direction or axis X of positioning apparatus 17. The longitudinal direction X is perpendicular the vertical axis Y. As already shown in FIG. 2, the positioning apparatus 17 includes a concave movable plate 16 extending downwards from the elongate member 20, the concave movable plate 16 being attachable to the threshing concaves 6a and being movable relative to the elongate member 20. In particular, the elongate member 20 defines a longitudinal axis of the positioning apparatus 17 (and extends along a longitudinal axis of the combine), and the concave movable plate 16 is movable in a direction perpendicular to the longitudinal axis. At its lower end, the concave movable plate 16 is provided with recesses 21 where the inner edges of the threshing concaves 6a are to be slidably mounted thereon.

[0054] The concave movable plate 16 is itself suspended in two attachment points 22, from a pair of pivoting structures, each of the latter being provided with a rotatable axle 25 mounted between two fixed brackets 26. The axles 25 each have a first radially-oriented arm 27 connected to the attachment point 22 of the concave movable plate 16 via pivotable links 28. The axles 25 also each have a second radial arm pivotably connected to a concave control rod 30 extending along the length of the elongate member 20.

[0055] With additional reference to FIG. 4, which shows a schematic side view of the positional apparatus 17, the other end of the concave control rod 30 is attached or coupled to a concave control arm 31. In particular, the concave control arm 31 is attached to the concave control rod 30 at a first end 31a of the arm 31. At a second end 31b of the arm 31 opposite the first end 31a is attached a concave actuating mechanism 32. The concave control arm 31 is rotatable about a pivot point 31c between the first and second ends 31a, 31b. The pivot axis of the pivot point 31c is perpendicular to the longitudinal axis of the positioning apparatus 17, i.e. perpendicular to the axis along which the elongate member 20 extends. The concave actuating mechanism 32 includes a concave actuator 33. In the described embodiment, the concave actuator 33 is a hydraulic cylinder (containing hydraulic fluid) with an associated actuating piston which moves in dependence on the hydraulic pressure. That is, the pressure in the hydraulic cylinder dictates the level of force that the concave actuator 33 applies to the concave control arm 31.

[0056] With continuing reference to FIG. 4, there is also attached to the second end 31b of the concave control arm 31 a concave compression spring 34, which provides a biasing force against the actuating mechanism 32, i.e. in the opposite direction to the force applied by the actuating rod of the concave actuator 33 to the control arm 31. The concave spring 34 may be considered to act in the same direction as gravity and crops applying pressure to the concaves 6a. When the spring biasing force completely overcomes the force applied on the control arm 31 by the actuating mechanism 32 then the control arm 31 pivots about its pivot axis 31c. As viewed in FIG. 4, this causes the concave control rod 30 to move to the left which in turn causes the concave axles 25 to rotate. The attachment points 22 therefore move downwards which in turn causes the concave movable plate 16 to move downwards. When attached to the threshing concaves 6a, this means that the concaves 6a move downwards to increase the threshing gap between the concaves 6a and rotors 5 to attain the maximum possible value.

[0057] In contrast, when the force applied on the control arm 31 by the actuating mechanism 32 completely overcomes the biasing force of the concave spring 34 then the control arm 31 pivots such that the control rod 30 moves to the right. In turn, this causes the concave axles 25 to rotate such that concave movable plate 16 moves upwards. When attached to the threshing concaves 6a, this means that the concaves 6a move upwards to decrease the threshing gap to be the minimum possible value.

[0058] Therefore, it will be understood that the pressure in the hydraulic cylinder 33 dictates the size of the threshing gap in the combine. In particular, the hydraulic cylinder pressure is controlled by pressure control means 35. In the described embodiment the pressure control means is in the form of an accumulator.

[0059] When the pressure control means 35 controls the pressure in the hydraulic cylinder 33 to be a relatively low value, the actuating rod of the concave actuator is in a retracted position. As the pressure in the hydraulic cylinder 33 is increased, the actuating rod extends from the hydraulic cylinder 33 to increase the force it applies to the control arm 31 in opposition to the biasing force of the spring 34. This causes the control arm to rotate about the pivot axis 31c (in an anticlockwise direction as viewed in FIG. 4). In turn, this causes the control rod 30 to the right, or in the positive X direction, as viewed in FIG. 4. This causes the rotatable axles or linkages 25 to rotate about their axes (again anticlockwise as viewed in FIG. 4) and to move the first radially-oriented arms 27 and the pivotable links 28 generally upwards. In turn, this causes the concave divider 16 to move upwards in the vertical or Y direction as viewed in FIG. 4, which causes the concaves 6a to move upwards so as to reduce the threshing gap (see FIG. 2).

[0060] Returning to FIGS. 3a and 3b, the positioning apparatus 17 also includes a grate movable plate 160 extending downwards from the elongate member 20, the grate movable plate 160 being attachable to the separation grates 6b and being movable relative to the elongate member 20. In particular, the grate movable plate 160 is movable in a direction perpendicular to the longitudinal axis of the positioning apparatus 17. At its lower end, the grate movable plate 160 is provided with recesses 210 where the inner edges of the separation grates 6b are to be slidably mounted thereon.

[0061] The grate movable plate 160 is itself suspended in two attachment points 220, from a pair of pivoting structures, each of the latter being provided with a rotatable axle 250 mounted between two fixed brackets 260. The axle 250 has a first radially-oriented arm 270 connected to the attachment point 220 of the grate movable plate 160 via pivotable links 280. The axle 250 also has a second radial arm pivotably attached or coupled to a grate control rod 300 extending along the length of the elongate member 20.

[0062] With additional reference to FIG. 4, the other end of the concave control rod 300 is attached or coupled to a concave control arm 310. In particular, the concave control arm 310 is attached to the concave control rod 300 at a first end 310a of the arm 310. The concave control arm 310 is rotatable about a pivot point at a second end 310b of the control arm 310. The pivot axis of the pivot point 310b is perpendicular to the longitudinal axis of the positioning apparatus 17, i.e. perpendicular to the axis along which the elongate member 20 extends. Also attached to the first end 310a of the control arm 310 is a grate actuating mechanism 320. The grate actuating mechanism 320 includes a grate actuator 330. In the described embodiment, the grate actuator 330 is a hydraulic cylinder (containing hydraulic fluid) with an associated actuating piston which moves in dependence on the hydraulic pressure. That is, the pressure in the hydraulic cylinder dictates the level of force that the grate actuator 330 applies to the grate control arm 310.

[0063] With continuing reference to FIG. 4, there is also attached to the first end 310a of the grate control arm 310 a grate compression spring 340, which provides a biasing force against the actuating mechanism 320, i.e. in the opposite direction to the force applied by the actuating rod of the grate actuator 330 to the control arm 310. The grate spring 340 may be considered to act in the same direction as gravity and crops applying pressure to the grates 6b. When the spring biasing force completely overcomes the force applied on the control arm 310 by the actuating mechanism 320 then the control arm 310 pivots about its pivot axis 310b. As viewed in FIG. 4, this causes the grate control rod 300 to move to the right which in turn causes the grate axles 250 to rotate. The attachment points 220 therefore move downwards which in turn causes the grate movable plate 160 to move downwards. When attached to the separation grates 6b, this means that the grates 6b move downwards to increase the separation gap between the grates 6b and rotors 5 to attain the maximum possible value.

[0064] In contrast, when the force applied on the control arm 310 by the actuating mechanism 320 completely overcomes the biasing force of the grate spring 340 then the control arm 310 pivots such that the control rod 300 moves to the left. In turn, this causes the grate axles 250 to rotate such that grate movable plate 160 moves upwards. When attached to the separation grates 6b, grates 6b, this means that the grates 6b move upwards to decrease the separation gap to be the minimum possible value.

[0065] Therefore, it will be understood that the pressure in the hydraulic cylinder 330 dictates the size of the separation gap in the combine. In particular, the hydraulic cylinder pressure is controlled by pressure control means 350. In the described embodiment the pressure control means is in the form of an accumulator.

[0066] When the pressure control means 350 controls the pressure in the hydraulic cylinder 330 to be a relatively low value, the actuating rod of the grate actuator is in a retracted position. As the pressure in the hydraulic cylinder 330 is increased, the actuating rod extends from the hydraulic cylinder 330 to increase the force it applies to the control arm 310 in opposition to the biasing force of the spring 340. This causes the control arm to rotate about the pivot axis 310b (in an anticlockwise direction as viewed in FIG. 4). In turn, this causes the control rod 300 to the right, or in the positive X direction, as viewed in FIG. 4. This causes the rotatable axles or linkages 250 to rotate about their axes (again anticlockwise as viewed in FIG. 4) and to move the first radially-oriented arms 270 and the pivotable links 280 generally upwards. In turn, this causes the grate divider 160 to move upwards in the vertical or Y direction as viewed in FIG. 4, which causes the grates 6b to move upwards so as to reduce the separation gap.

[0067] The position of the concaves 6a and grates 6b, and therefore the size of the threshing and separation gaps, may be controlled from the driver's cabin 7. That is, the driver may set the pressure in the hydraulic cylinders 33, 330 so as to pre-set an initial position of the concaves 6a and grates 6b. Crucially, the position of the concaves 6a may be set independently of the position of the grates 6b.

[0068] Two different strategies may be followed: the positions of the concaves 6a and grates 6b, and therefore the threshing and separation gaps, may be kept constant during operation of the combine; or, the positions of the concaves 6a and grates 6b may be adaptively adjusted in dependence on the force applied on the concaves 6a and grates 6b by crops being processed by the combine. In the second of these strategies, a level of suspension is built into the combine so as to more effective process crops that pass therethrough. In particular, the combination of the hydraulic cylinders 33, 330 and the accumulators 35, 350 keeps the pressure in the arrangement quasi-constant. By this is meant that an increase in pressure applied by crops to the concaves 6a or grates 6b causes hydraulic fluid to be released from the cylinders 33, 330 to reduce the pressure applied on the control arms 31, 310 by the actuating mechanisms 32, 320, thereby causing the concaves 6a or grates 6b to move downwards to increase the threshing or separation gaps. However, when the pressure applied by crops to the concaves 6a or grates 6b reduces again there is an increase in the hydraulic cylinder pressure so as to return the concaves 6a or grates 6b to their initial or pre-set positions (as set from the driver's cabin 7, for example).

[0069] FIGS. 3a and 3b show that the concave hydraulic cylinder 33 is arranged generally above the grate hydraulic cylinder 330. In addition, the concave and grate hydraulic cylinders 33, 330 extend generally in the same plane, namely, a longitudinal direction of the positioning apparatus 17, i.e. the X direction indicated in the figures. That is, the cylinders 33, 330 are arranged generally in a vertical plane of the apparatus 17. The cylinders are, however, oriented in substantially opposing directions such that an increase in hydraulic pressure in the cylinders 33, 330 causes the respective pistons to move in opposing directions.

[0070] With further reference to FIG. 5, which shows an end view of the rotors 5, concaves 6a, and positional apparatus 17, the concave control rod 30 is arranged adjacent to the grate control rod 300, in particular substantially side-by-side. The control rods 30, 300 extend substantially parallel to one another, in particular along the longitudinal axis of the positional apparatus 17.

[0071] FIGS. 6 and 7 show additional views of the threshing concaves 6a and separation grates 6b together with the positional apparatus 17. In particular, these figures highlight that the available space between the pair of concaves 6a and between the pair of grates 6b is relatively narrow. The particular design of the positional apparatus 17 is such that the concaves 6a and grates 6b have independent adjustment mechanisms but the positional apparatus 17 remains narrow enough to fit in the limited available space between the concaves 6a and grates 6b (and also below a grain bin of the combine).

[0072] Many modifications may be made to the above-described embodiments without departing from the scope of the present invention as defined in the accompanying claims.

[0073] In the above described embodiment, the combine is a twin-rotor combine; however, in different embodiments the positional apparatus may be used in a combine having a single rotor, oriented either longitudinally or transversely.

[0074] In the above-described embodiment, both the initial positioning of the concaves and grates, and the suspension of the concaves and grates reacting to crop loading thereon, is controlled hydraulically. In different embodiments, only the suspension may be controlled hydraulically and the initial positioning may be controlled by an electric motor, for example.

[0075] In the above-described embodiment, the combine includes a single pair of threshing concaves 6a and a single pair of separation grates 6b; however, in different embodiments the combine may include any suitable number of pairs of concaves and any suitable number of pairs of grates.

[0076] In the above-described embodiment, the pressure control means is an accumulator; however, in different embodiments the pressure control means may be a dedicated pressure control valve which allows an increase or decrease in pressure in the hydraulic cylinders in dependence on the crop pressure applied to the threshing concaves and separation grates.