WO2014191804A1

WO2014191804A1 - Combine having cam-operated concave adjustment

Info

Publication number: WO2014191804A1
Application number: PCT/IB2014/000791
Authority: WO
Inventors: Robert Figger
Original assignee: Agco Corporation
Priority date: 2013-05-31
Filing date: 2014-05-16
Publication date: 2014-12-04

Abstract

A crop harvester (20) is operable to process severed crop material and includes a harvester frame (22), crop-processing rotor (28), concave (32), and cam element (82). The concave (32) is shiftably supported relative to the harvester frame to be moved generally toward or away from the rotor along a direction transverse to the rotor axis (R) to control processing of severed crop material. The cam element is shiftably mounted relative to the harvester frame and is operably coupled to the concave so that shifting of the cam element relative to the harvester frame causes shifting of the concave relative to the rotor along the transverse direction.

Description

DESCRIPTION

COMBINE HAVING CAM-OPERATED CONCAVE ADJUSTMENT

BACKGROUND

[0001] 1. Field

[0002] The present invention relates generally to crop harvesting equipment. More specifically, embodiments of the present invention concern a harvester with a cam- operated concave adjustment device.

[0003] 2. Discussion of Prior Art

[0004] Conventional combine harvesters have long used a rotor and concave system to thresh and separate grain from severed crop material. The rotor is typically rotatably mounted to spin relative to concaves located below the rotor. The concaves are adjustably positioned so that the gap between the rotor and concaves can be adjusted. In this manner, the rotor and concave system can be adjusted to accommodate various types of crops for threshing and separating of grain and to otherwise optimize the threshing and separating process. Some prior art harvesters employ a powered motor to shift concaves relative to the rotor.

[0005] However, conventional harvesters and concave adjustment mechanisms suffer from various deficiencies. For instance, prior art concaves and concave adjustment devices are generally bulky and heavy. Also, known concave adjustment devices generally have a complex mechanical structure with numerous moving components. These deficiencies result in concave adjustment mechanisms that are expensive to design, build, and maintain.

SUMMARY

[0006] The following brief summary is provided to indicate the nature of the subject matter disclosed herein. While certain aspects of the present invention are described below, the summary is not intended to limit the scope of the present invention.

[0007] Embodiments of the present invention provide a harvester that does not suffer from the problems and limitations of the prior art harvesters set forth above. [0008] A first aspect of the present invention concerns a crop harvester operable to process severed crop material. The crop harvester broadly includes a harvester frame, crop- processing rotor, a concave, and a cam element. The crop-processing rotor is rotatably supported by the harvester frame to define a rotor axis. The concave extends axially along the rotor and is generally positioned below the rotor, with the crop-processing rotor being rotatable relative to the concave so that the concave and rotor cooperatively receive and process severed crop material. The concave is shiftably supported relative to the harvester frame to be moved generally toward or away from the rotor along a direction substantially transverse to the rotor axis to control processing of severed crop material. The cam element is shiftably mounted relative to the harvester frame and is operably coupled to the concave so that shifting of the cam element relative to the harvester frame causes shifting of the concave relative to the rotor along the transverse direction.

[0009] This summary is provided to introduce a selection of concepts in a simplified form that are further described below in the detailed description. This summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used to limit the scope of the claimed subject matter. Other aspects and advantages of the present invention will be apparent from the following detailed description of the embodiments and the accompanying drawing figures.

BRIEF DESCRIPTION OF THE DRAWING FIGURES

[0010] Preferred embodiments of the invention are described in detail below with reference to the attached drawing figures, wherein:

[0011] FIG. 1 is a side elevation of a harvester constructed in accordance with a preferred embodiment of the present invention, and depicting, among other things, a rolling chassis with a harvester frame, a rotor, concaves, grates, and a concave adjustment device;

[0012] FIG.2 is a fragmentary front perspective the harvester shown in FIG. 1 , showing rotor bulkheads of the harvester frame and the concave adjustment device in a lowermost position, with the concave adjustment device including an axial support, fore and aft cam housings, fore and aft cam wheels, a linear motor, and a linkage;

[0013] FIG. 3 is a fragmentary front perspective of the harvester similar to FIG. 2, but showing the concave adjustment device in an uppermost position;

[0014] FIG. 4 is an enlarged upper fragmentary perspective of the concaves and concave adjustment device shown in FIGS. 1 -3, showing the concaves and concave adjustment device in the uppermost position;

[0015] FIG. 5 is an enlarged lower fragmentary perspective of the concaves and concave adjustment device shown in FIGS. 1 -4, showing the concaves and concave adjustment device in the uppermost position;

[0016] FIG. 6 is a fragmentary front elevation of the harvester shown in FIGS. 1 -5, showing the rotor mounted relative to the harvester frame and concaves, with the rotor and concaves cooperatively defining a gap therebetween, and showing the concaves and concave adjustment device in the lowermost position;

[0017] FIG. 7 is an enlarged fragmentary front elevation of the harvester frame, concaves, and concave adjustment device shown in FIGS. 1 -6, showing the concaves and concave adjustment device in the lowermost position;

[0018] FIG. 8 is an enlarged fragmentary front elevation of the harvester frame, concaves, and concave adjustment device similar to FIG. 7, but showing the concaves and concave adjustment device in an intermediate position; and

[0019] FIG. 9 is an enlarged fragmentary front elevation of the harvester frame, concaves, and concave adjustment device similar to FIG. 7, but showing the concaves and concave adjustment device in the uppermost position.

[0020] The drawing figures do not limit the present invention to the specific embodiments disclosed and described herein. The drawings are not necessarily to scale, emphasis instead being placed upon clearly illustrating the principles of the preferred embodiment.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0021] Turning initially to FIG. 1 , a crop harvester 20 is constructed in accordance with a preferred embodiment of the present invention. The crop harvester 20 is preferably operable to travel through a field to sever crop (not shown) and separate grain from the severed crop material (not shown). The crop harvester 20 is preferably configured to harvest a variety of crops, such as wheat, soybeans, milo, oats, or corn.

[0022] In the usual manner, the crop harvester 20 is a self-propelled machine that collects the separated grain and generally discharges material other than grain (MOG) onto the field. Thus, the illustrated harvester 20 includes a rolling chassis that includes a harvester frame 22, wheels 24, operator enclosure 26, and an engine (not shown) to drive the wheels 24. The crop harvester 20 also includes a rotor threshing and separating system to process the severed crop material. In particular, the crop harvester 20 broadly includes a rotor 28, separating grates 30, concaves 32, concave guides 34, and a concave adjustment device 36.

[0023] The rotor threshing and separating system receives severed crop material from a header (not shown) that severs the crop and collects the severed crop material. The material is transported from the header by a feederhouse 38, which sends the material into a beater 40 and then to the rotor 28.

[0024] After passing through the rotor threshing and separating system, separated grain and MOG are further processed by sieve assembly 42 located generally below the concaves 32. [0025] Turning to FIGS. 1 -4, the harvester frame 22 preferably includes, among other things, fore and aft rotor bulkheads 44,46 spaced apart from one another. Each of the bulkheads 44,46 is preferably rigid and presents an opening 48 that rotatably receives the rotor 28. Preferably, each of the bulkheads 44,46 also presents an upright slot 50 that receives the concave adjustment device 36. As will be discussed, the bulkheads 44,46 cooperatively support concaves 32 for shifting movement relative to the rotor 28. However, the harvester frame 22 could be alternatively configured without departing from the scope of the present invention.

[0026] The rotor 28 preferably comprises a conventional axial rotor that cooperates with the grates 30 and concaves 32 to thresh severed crop material and separate grain from MOG. The rotor 28 includes multiple rasp-like elements (not shown) to thresh and separate the grain. The illustrated rotor 28 preferably extends axially along the length of the crop harvester 20 and rotates about a rotor axis R (see FIG. 6). However, it is within the scope of the present invention where the rotor 28 has an alternative construction and/or orientation relative to the harvester frame 22. Additional features of one preferred rotor are disclosed in U.S. Patent No. 7,393,274, which is incorporated in its entirety by reference herein.

[0027] Turning to FIGS. 2-6, the concaves 32 each have a conventional construction and include a plurality of curved side members 52, multiple bars 54 that extend transversely to the side members 52, and a series of curved rods 56. The side members preferably include lowermost mounting lugs 58. The side members 52, bars 54, and rods 56 cooperatively form a plurality of apertures 60 that permit threshed grain (and small pieces of MOG) to fall through the concave 32 (see FIG. 4). The apertures 60 cooperatively define inner and outer faces 62,64 of the concaves 32. Preferably, the concave adjustment device 36 of the present invention does not extend across the outer face 64. [0028] In the usual manner, the concaves 32 are preferably positioned alongside one another so that the inner faces 62 extend along and adjacent to the rotor 28, with the rotor 28 and concaves 32 cooperatively defining an annular space 66 therebetween that presents an annular gap G (see FIG. 6). However, it is within the ambit of the present invention where the harvester 20 has an alternative concave arrangement.

[0029] The illustrated concaves 32 are shiftably supported relative to the harvester frame 22 to move generally toward or away from the rotor 28 along a direction transverse to the rotor axis R to adjust the size of the annular space 66. The concaves 32 are preferably supported on the harvester frame 22 by the concave guides 34 and the concave adjustment device 36.

[0030] Each concave 32 is preferably supported at opposite ends thereof by respective guides 34. Each guide 34 includes first and second guide portions 68,70 that cooperatively define a guide slot 72 (see FIG. 6). Each guide 34 also includes a stop 74 pivotally attached to an arm 76, with the stop 74 being slidably received by the guide portions 68,70 and the arm 76 being attached to the corresponding concave 32 (see FIG. 6).

[0031] The guide portions 68,70 are preferably arranged so that the guide slots 72 are in a generally upright orientation. As will be discussed, the guides 34 cooperate so that the concaves 32 can be shifted toward or away from the rotor 28 along the transverse direction. Additional preferred features of the guides 34 are disclosed in U.S. Patent No. 8, 133, 100, which is hereby incorporated in its entirety by reference herein.

[0032] The concave adjustment device 36 is constructed to support and shift the concaves 32 along the transverse direction to control the position of the concaves 32 relative to the rotor 28 and thereby control the size of the annular space 66. As will be discussed, the concave adjustment device 36 preferably includes a cam mechanism to drive the concaves 32. The concave adjustment device 36 is preferably constructed to have minimal interference with the flow of grain and MOG through the harvester 20, particularly through the concaves 32. [0033] The illustrated concave adjustment device 36 preferably includes fore and aft cam housings 78a,b, axial support 80, fore and aft cam wheels 82a,b, linkage 84, and linear motor 86. Because the cam housings 78a,b are substantially the same as one another and cam wheels 82a,b are substantially the same as one another (except that cam wheel 82a has an integrally formed lever to be attached to linkage 84), reference will be made primarily to cam housing 78a and cam wheel 82a.

[0034] Turning to FIGS. 2-5, the axial support 80 preferably includes an elongated sleeve 88, a spacer bar 90 integrally attached to the sleeve 88, and an elongated rod 92 rotatably received by the sleeve 88. The sleeve 88 and spacer bar 90 cooperatively present a series of openings 94 spaced axially along the support 80.

[0035] The rod 92 preferably presents opposite rod ends 96 that are slidably received by corresponding slots 50. Thus, the axial support 80 is preferably slidably mounted on the rotor bulkheads 44,46 to slide up and down between an uppermost position (see FIG. 9) and a lowermost position (see FIG. 7). The openings 94 are preferably configured to receive corresponding ones of the lugs 58 so that the lugs 58 of each concave 32 engage and are supported by the sleeve 88. Thus, sliding movement of the axial support 80 along the slots 50 preferably causes corresponding sliding movement of the concaves 32 relative to the rotor bulkheads 44,46. In turn, the axial support 80 provides sliding movement of the concaves 32 toward or away from the rotor 28. As will be discussed, the rod 92 preferably drivingly interconnects the cam wheels 82 so that the cam wheels 82 can cooperatively raise or lower the axial support 80.

[0036] However, it is within the ambit of the present invention where an alternative structure is used to support and shift the concaves 32 relative to the rotor 28. The concave adjustment device 36 may have spaced apart concave supports that do not extend continuously between the rotor bulkheads. For instance, the cam wheels 82 could be independently powered and rotated by corresponding motors and linkages.

[0037] Turning to FIGS. 4-9, the cam housings 78 are preferably operable to control movement of the respective cam wheels 82. The cam housing 78a includes a pair of plates 98 integrally attached to one another. The cam housing 78a presents a slotted opening 100 and multiple holes 102 that permit the cam housing 78a to be attached to rotor bulkhead 44 with fasteners (not shown). Cam housing 78b is similar to cam housing 78a, but is attached to rotor bulkhead 46 and located between plates of the rotor bulkhead 46.

[0038] The slotted opening 100 is defined by an endless inner surface 104 and is positioned adjacent the respective slot 50. As will be discussed, the cam housings 78 are operable to support respective cam wheels 82, with the inner surface 104 operating as a follower surface. [0039] While the concave adjustment device 36 preferably includes the illustrated cam housings 78, it is within the ambit of the present invention where the cam housings 78 are alternatively shaped and/or configured. Moreover, for some aspects of the present invention, the concave adjustment device 36 could be devoid of cam housings 78. For instance, the cam wheels 82 could drivingly engage surfaces of the rotor bulkheads 44,46 or another surface.

[0040] The cam wheels 82 are preferably operable to be drivingly rotated to position the concaves 32 relative to the rotor 28. The illustrated cam wheel 82a is preferably unitary and includes a disc portion 106 and a lever portion 108 fixed to one another. The cam wheel 82b is also unitary and comprises another disc portion 106. The cam wheels 82 each present a keyed bore 1 10 that receives the respective rod end 96 (which has a complemental keyed profile) so that the cam wheels 82 and rods 92 rotate with one another (see FIGS. 7-9). The keyed bore 1 10 generally defines cam axis C.

[0041] The illustrated disc portion 106 presents an outwardly-facing cam surface 1 12 that operably engages the inner surface 104 of the cam housing 78. Thus, the cam wheel 82 can slide and/or roll along the inner surface 104, which acts as a follower surface. Preferably, the cam surface 1 12 is shaped and eccentrically positioned relative to the keyed bore 1 10 so that the cam surface 1 12 defines a lobe 1 14 with a central lobe axis L that is offset from the cam axis C.

[0042] However, it is within the scope of the present invention where the cam wheel 82 is alternatively shaped and/or configured. For instance, the cam wheel 82 could present multiple lobes spaced around the keyed bore 1 10. Also, the cam wheel 82 could present an alternative cam surface to drive the concaves 32. For instance, the cam wheel 82 could define a slot that engages a complemental feature on the cam housing 78.

[0043] The cam wheels 82 are preferably drivingly interconnected by the rod 92 so that the cam wheels 82 are simultaneously rotatable to cooperatively raise or lower the axial support 80. Furthermore, this preferred interconnection of the cam wheels 82 allows the cam wheels 82 to be powered by a single linear motor 86. However, for some aspects of the present invention, the cam wheels 82 could be detached from each other so as to be independently rotatable. For instance, the cam wheels 82 could be independently powered and rotated by corresponding motors and linkages. [0044] It will also be appreciated that, for some aspects of the present invention, an alternative cam element could be used in place of the cam wheel 82, such as a sliding wedge. For instance, wedge-shaped cams could be mounted in lateral sliding engagement with respective rotor bulkheads 44,46 and the axial support 80 so that sliding movement of the cams in a lateral direction causes movement of the axial support 80 and the concaves 32 along the transverse direction.

[0045] Again, the illustrated cam wheel 82 is preferably attached to the rod 92 so that the cam wheels 82 and axial support 80 can move with one another along the transverse direction. The cam wheels 82 are rotatable on the cam housings 78 to shift the axial support 80 between the uppermost and lowermost positions (see FIGS. 7 and 9), with the rod 92 generally following the path defined by the slot 50. As will be discussed, the linkage 84 is operably connected to the cam wheel 82a to rotate the cam wheels 82 and rod 92 between cam rotational positions associated with the uppermost and lowermost positions.

[0046] Because the axial support 80 is attached to the concaves 32, the cam wheels 82 are preferably rotatably mounted relative to the concaves 32 so that the cam axis C moves relative to the rotor bulkheads 44,46. However, it is within the scope of the present invention where the cam wheels 82 are rotatably mounted so that the cam axis C is fixed relative to the cam housings 78 and/or the rotor bulkheads 44,46.

[0047] The cam wheels 82 preferably engage follower surfaces (i.e., the inner surfaces 104) that are fixed relative to the rotor bulkheads 44,46. However, the principles of the present invention are applicable where the cam wheels 82 engage a surface that moves with the concaves 32. For instance, the cam wheels 82 could be pivotally mounted relative to the rotor bulkheads 44,46 so that the cam surfaces slidably engage the axial support 80 to shift the axial support 80 and concaves 32 (e.g., where the cam axis C is fixed relative to the rotor bulkheads 44,46). Also, the cam wheels 82 could be mounted with the cam surface 1 12 slidably engaging the concaves 32.

[0048] Turning to FIGS. 6-9, the concave adjustment device 36 is preferably powered by the linear motor 86, with the linkage 84 drivingly connecting the linear motor 86 and the cam wheel 82a. The linear motor 86 includes a reciprocating linear motor piston 1 16 that presents an exposed piston end. The illustrated linear motor 86 is pivotally mounted to the harvester frame 22 at a motor pivot joint 1 17. In the usual manner, the linear motor piston 1 16 is driven along a driving axis P defined by the piston 16. The linear motor 86 preferably comprises an electrically-powered actuator supplied by AGCO Corporation, Inc., Part No. 700730000. However, the principles of the present invention are applicable where an alternative motor is used. For instance, a pneumatic or hydraulic cylinder could be used in place of the electrically- powered actuator. Also, a rotating electric motor could be used to shift the cam wheel 82a.

[0049] The linear motor 86 is preferably operably coupled to a control console (not shown) in the operator enclosure 26 so that the operator can selectively operate the linear motor 86 by moving the piston 1 16 into or out of the motor body.

[0050] The linkage 84 preferably includes a spring-loaded cam link 1 18 and an intermediate link 120. The cam link 1 18 preferably includes a body 122, a slidable piston 124, and a spring (not shown) located within the body 122 to urge the piston 124 in a direction into the body 122. The slidable piston 124 is pivotally attached to the cam wheel 82a at a cam pivot joint 126.

[0051] The spring-loaded cam link 1 18 is preferably included in the linkage 84 to absorb excessive loads from the concaves 32. For instance, a hard foreign object ingested by the rotor 28 could cause one or both of the concaves 32 to be suddenly and/or violently shifted downwardly away from the rotor 28. Such shifting of the concaves 32 would cause the cam wheel 82a to suddenly and/or violently pull the slidable piston 124 in a direction away from the body 122. The spring within the cam link 1 18 permits the slidable piston 124 to move outwardly from the body 122 and, thereby, isolates the body 122, intermediate link 120, and linear motor 86 from potentially sudden and/or violent forces applied by the concaves 32.

[0052] The intermediate link 120 preferably drivingly interconnects the cam link 1 18 and the linear motor 86 so that the cam link 1 18 defines a driven link axis D that is generally oblique to the driving axis P of the linear motor piston 16. The intermediate link 120 comprises a unitary body that is pivotally mounted to the linear motor piston 1 16 at a piston pivot joint 128 and pivotally mounted to the body at a body pivot joint 130. The intermediate link 120 is also preferably pivotally mounted to the rotor bulkhead 44 with a bearing 132 at a base pivot joint 134 spaced from the pivot joints 128,130. Thus, reciprocating movement of the linear motor piston 1 16 causes corresponding pivoting of the intermediate link 120, which in turn causes movement of the cam link 1 18 and rotation of the cam wheels 82 and the rod 92.

[0053] The linear motor 86 preferably cooperates with the axial support 80, cam wheels 82, and linkage 84 to shift the concaves 32 upwardly and downwardly relative to the rotor bulkheads 44,46 to change the size of the gap G between the concaves 32 and rotor 28. For instance, the linear motor piston 1 16 is preferably extended to shift the concaves 32 downwardly toward the lowermost position (see FIGS. 2, 6, and 7). Also, the linear motor piston 1 16 is preferably retracted to shift the concaves 32 upwardly toward the uppermost position (see FIGS. 3-5 and 9). However, the linear motor piston 1 16 could be alternatively actuated to power the concaves 32 between the uppermost and lowermost positions. The concave adjustment device 36 also preferably provides a continuous range of concave positions intermediate the uppermost and lowermost positions (see, e.g., FIG. 8). However, it is also within the ambit of the present invention where the concave adjustment device 36 provides a series of discrete concave positions between the uppermost and lowermost positions.

[0054] The size of gap G of the annular space 66 is preferably selectively adjustable using the illustrated concave adjustment device 36. For instance, to increase the size of gap G by driving the concaves 32 and axial support 80 toward the lowermost position, the linear motor 86 is actuated to shift the linear motor piston 1 16 toward an extended position relative to the body of the linear motor 86 (see FIGS. 2, 6, and 7). To decrease the size of gap G by driving the concaves 32 and axial support 80 toward the uppermost position, the linear motor 86 is actuated to shift the linear motor piston 1 16 toward a retracted position relative to the body of the linear motor 86 (see FIGS. 3-5 and 9). Again, the linear motor 86 is preferably operably coupled to a control console (not shown) mounted in the operator enclosure 26 to permit the operator to conveniently actuate the linear motor 86 and thereby adjust the concaves 32.

[0055] In operation, the harvester 20 severs and collects crop material via the header and preferably transfers the severed crop material to the rotor 28 and concaves 32 via the feederhouse 38 and beater 40. In the usual manner, the rotor 28 spins relative to the concaves 32 as severed crop material is introduced into the annular space 66. The rotor 28 and concaves 32 cooperatively thresh and separate grain from MOG, with grain falling through apertures 60 of the concaves 32.

[0056] The gap G of the annular space 66, defined between the rotor 28 and concaves 32, is selectively sized by the operator to control the threshing and separating process. The size of the gap G is adjusted by actuating the linear motor 86 to extend or retract the linear motor piston 1 16. For instance, the operator can enlarge the size of gap G between the rotor 28 and concaves 32 by extending the linear motor piston 1 16. Alternatively, the operator can reduce the size of gap G by retracting the linear motor piston 1 16.

[0057] The preferred forms of the invention described above are to be used as illustration only, and should not be utilized in a limiting sense in interpreting the scope of the present invention. Obvious modifications to the exemplary embodiments, as hereinabove set forth, could be readily made by those skilled in the art without departing from the spirit of the present invention.

[0058] The inventors hereby state their intent to rely on the Doctrine of Equivalents to determine and assess the reasonably fair scope of the present invention as pertains to any apparatus not materially departing from but outside the literal scope of the invention as set forth in the following claims.

Claims

1. A crop harvester operable to process severed crop material, said crop harvester comprising:

a harvester frame;

a crop-processing rotor rotatably supported by the harvester frame to define a rotor axis; a concave extending axially along the rotor and generally positioned below the rotor, with the crop-processing rotor being rotatable relative to the concave so that the concave and rotor cooperatively receive and process severed crop material, said concave shiftably supported relative to the harvester frame to be moved generally toward or away from the rotor along a direction substantially transverse to the rotor axis to control processing of severed crop material; and

a cam element shiftably mounted relative to the harvester frame and operably coupled to the concave so that shifting of the cam element relative to the harvester frame causes shifting of the concave relative to the rotor along the transverse direction.

2. The crop harvester as claimed in claim 1 ,

said harvester frame including at least two rotor bulkheads spaced from one another along the rotor axis, with the cam housing attached to a corresponding one of the rotor bulkheads.

3. The crop harvester as claimed in claim 1 or claim 2; and a concave adjustment device including the cam element and an axial support element extending along the rotor axis to at least partly support the concave, said cam element being rotatably attached to the axial support element.

4. The crop harvester as claimed in claim 3, said cam element comprising a pair of cam elements drivingly interconnected by the axial support element so that the pair of cam elements cooperatively shift the axial support element and. the concave relative to the rotor along the transverse direction.

5. The crop harvester as claimed in claim 3 or 4, said concave adjustment device including a cam housing mounted on the harvester frame,

said cam element presenting a cam surface and said cam housing presenting a follower surface,

said cam and follower surfaces slidably engaging -one another so that movement of the cam element shifts at least a portion of the cam element relative to the cam housing along the transverse direction.

6. The crop harvester as claimed in any preceding claim,

said cam element comprising a cam wheel rotatably mounted for rotation about a cam axis that extends generally parallel to the rotor axis.

7. The crop harvester as claimed in claim 6,

said cam wheel rotatably mounted relative to the concave so that at least a portion of the cam wheel moves with the concave along the transverse direction as the concave shifts relative to the rotor.

8. The crop harvester as claimed in claim 6 or 7,

said cam wheel comprising a pair of cam wheels drivingly interconnected by the axial support element so that the pair of cam wheels rotate with one another.

9. The crop harvester as claimed in any one of claims 6 to 8,

said cam wheel presenting an eccentric cam surface that extends about the cam axis.

10. The crop harvester as claimed in claim 5,

said cam element comprising a cam wheel rotatably mounted relative to the concave to rotate about a cam axis that extends generally parallel to the rotor axis, said follower surface defining a slotted opening of the cam housing, with the slotted opening at least partly receiving the cam wheel.

1 1. The crop harvester as claimed in any preceding claim,

said concave including a pair of concaves extending axially alongside one another, with the pair of concaves and rotor cooperatively defining an annular space therebetween.

12. The crop harvester as claimed in claim 1 1 ,

said concave adjustment device including an axial support element attached to the cam element,

said axial support element extending along the rotor axis to at least partly support the pair of concaves.

13. The crop harvester as claimed in any preceding claim ; and a concave adjustment device including a power source and a linkage that drivingly interconnects the motor and the cam element so that actuation of the motor causes shifting of the concave relative to the rotor along the transverse direction.

14. The crop harvester as claimed in claim 13,

said power source comprising a linear motor that includes a drive piston that extends along a driving axis to power the linkage,

said linkage including a driven cam link that extends along a driven axis at an oblique angle relative to the driving axis.

15. The crop harvester as claimed in claim 14,

said driven cam link comprising a spring-loaded link that permits relative movement between the linear motor and the cam element when force applied to the linkage by the cam element exceeds a predetermined force level.

16. The crop harvester as claimed in claim 15,

said linkage including an intermediate link mounted to the harvester frame, said intermediate link drivingly interconnecting and restricting off-axis movement of the drive piston and the driven cam link.

17. The crop harvester as claimed in claim 16,

said intermediate link being pivotally mounted to the harvester frame at a base pivot joint,

said intermediate link pivotally mounted to the drive piston and the driven cam link at a driven pivot joint spaced from the base pivot joint.

18. The crop harvester as claimed in claim 17,

said concave adjustment device including an axial support element extending along the rotor axis to at least partly support the concave,

said cam element comprising a pair of cam elements drivingly interconnected by the axial support element so that the pair of cam elements cooperatively shift the axial support element and the concave relative to the rotor along the transverse direction. 9. The crop harvester as claimed in claim 18,

said linkage being drivingly attached to one of the pair of cam elements.