Center knife drive for an agricultural harvester

A header for an agricultural harvester comprising a frame and an epicyclical drive supported by the frame. The epicyclical drive includes a first rotatable wheel having a first substantially vertical rotational axis and a first disk. The first disk includes a first eccentric axis rotatable about the first rotational axis. The epicyclical drive further includes a second rotatable wheel having a second substantially vertical rotational axis and a second disk. The second disk includes a second eccentric axis rotatable about the second rotational axis. The header further includes a first cutter bar directly connected to the first disk and a second cutter bar directly connected to the second disk. Operation of the epicyclical drive results in substantially linear oscillating motion of the cutter bars.

The exemplary embodiments of present invention relate generally to a header of a plant cutting machine (e.g., a combine harvester) and, more specifically, to a header having an epicyclical drive directly connected to and driving a cutter bar.

BACKGROUND OF THE DISCLOSURE

An agricultural harvester e.g., a plant cutting machine, such as, but not limited to, a combine or a windrower, generally includes a header operable for severing and collecting plant or crop material as the harvester is driven over a crop field. The header has a plant cutting mechanism, e.g., a cutter bar, for severing the plants or crops via, for example, an elongate sickle mechanism that reciprocates sidewardly relative to a non-reciprocating guard structure. After crops are cut, they are collected inside the header and transported via a conveyor such as a draper belt towards a feederhouse located centrally inside the header.

Epicyclical cutter bar knife drives oscillate first and second sickle mechanisms of cutter bars in opposite directions in order to cut crop. However, conventional epicyclical knife drives generate detrimental moments and/or other forces that can lead to stresses in the knife drives as well as at the connections of the driver elements to the cutter bar.

BRIEF SUMMARY OF THE DISCLOSURE

In accordance with an exemplary embodiment there is provided a header for an agricultural harvester comprising a frame and an epicyclical drive supported by the frame. The epicyclical drive includes a first rotatable wheel having a first substantially vertical rotational axis and a first disk. The first disk has a first eccentric axis rotatable about the first substantially vertical rotational axis, wherein operation of the epicyclical drive results in oscillating motion of the first disk in a direction transverse to the first substantially vertical rotational axis. A first cutter bar is directly connected to the first disk extending in a direction substantially transverse to the first substantially vertical rotational axis. The oscillating motion of the first disk is in line with a longitudinal axis of the first cutter bar.

In accordance with the exemplary embodiment, the epicyclical drive further includes a second rotatable wheel having a second substantially vertical rotational axis, and a second disk. The second disk has a second eccentric axis rotatable about the second substantially vertical rotational axis, wherein operation of the epicyclical drive results in oscillating motion of the second disk in a direction transverse to the second substantially vertical rotational axis. A second cutter bar is directly connected to the second disk extending in a direction substantially transverse to the second substantially vertical rotational axis. The oscillating motion of the second disk is in line with a longitudinal axis of the second cutter bar.

An aspect of the exemplary embodiment is that the first and second disks are configured to oscillate in opposing directions and in a direction along a single plane. Further, the second substantially vertical rotational axis is parallel to and spaced from the first substantially vertical rotational axis. In addition, the second rotatable wheel is adjacent the first rotatable wheel and the first rotatable wheel is adjacent to the first cutter bar.

Another aspect of the exemplary embodiment is that the first substantially vertical rotational axis of the first rotatable wheel is parallel to the first eccentric axis of the first disk, and the second substantially vertical rotational axis of the second rotatable wheel is parallel to the second eccentric axis of the second disk. Additionally, the first eccentric axis is substantially vertical and the epicyclical drive faces an upwardly direction.

Another aspect of the exemplary embodiment is that the epicyclical drive is mounted centrally along the frame. A further aspect of the exemplary embodiment is that the epicyclical drive includes a drive mechanism extending between and operatively engaged with the first and second rotatable wheels. The drive mechanism includes a drive shaft that engages a first driven gear operatively connected to the first rotatable wheel and a second driven gear operatively connected to the second rotatable wheel.

Another aspect of the exemplary embodiment is that the header includes a central cutter bar adjacent the epicyclical drive. The central cutter bar has a longitudinal extent greater than a width of the epicyclical drive and positioned between the first and second cutter bars.

Another aspect of the exemplary embodiment is that the header includes a conveyor supported by the frame, and the epicyclical drive is positioned between the first and second cutter bars and the conveyor. The conveyor can be in infeed conveyor or a lateral draper conveyor.

In accordance with the exemplary embodiments of the present disclosure, there is provided an epicyclical knife drive disk that is directly connected to the cutter bar. When the exemplary embodiments are used in combination with an agricultural harvester, the exemplary embodiments overcome one or more of the disadvantages of conventional harvesters by providing a header having an epicyclical knife drive connected directly to the elongate cutter bar, thereby eliminating intervening structure(s) between the knife drive and the cutter bar as well as detrimental stresses associated with such structures. In addition, the assembly has less mass and is lighter in weight which is advantageous as the combine requires less energy to lift the header, and there is less mass to float on the ground thereby reducing the likelihood of the cutter bars digging into the ground during operation.

Other features and advantages of the subject disclosure will be apparent from the following more detail description of the exemplary embodiments.

DETAILED DESCRIPTION OF THE DISCLOSURE

Reference will now be made in detail to the various exemplary embodiments of the subject disclosure illustrated in the accompanying drawings. Wherever possible, the same or like reference numbers will be used throughout the drawings to refer to the same or like features. It should be noted that the drawings are in simplified form and are not drawn to precise scale. Certain terminology is used in the following description for convenience only and is not limiting. Directional terms such as top, bottom, left, right, above, below and diagonal, are used with respect to the accompanying drawings. The term “distal” shall mean away from the center of a body. The term “proximal” shall mean closer towards the center of a body and/or away from the “distal” end. The words “inwardly” and “outwardly” refer to directions toward and away from, respectively, the geometric center of the identified element and designated parts thereof. Such directional terms used in conjunction with the following description of the drawings should not be construed to limit the scope of the subject application in any manner not explicitly set forth. Additionally, the term “a,” as used in the specification, means “at least one.” The terminology includes the words above specifically mentioned, derivatives thereof, and words of similar import.

The terms “grain,” “ear,” “stalk,” “leaf,” and “crop material” are used throughout the specification for convenience and it should be understood that these terms are not intended to be limiting. Thus, “grain” refers to that part of a crop which is harvested and separated from discardable portions of the crop material. The header of the subject application is applicable to a variety of crops, including but not limited to wheat, soybeans and small grains. The terms “debris,” “material other than grain,” and the like are used interchangeably.

“Substantially” as used herein shall mean considerable in extent, largely but not wholly that which is specified, or an appropriate variation therefrom as is acceptable within the field of art.

Furthermore, the described features, advantages and characteristics of the exemplary embodiments of the subject disclosure may be combined in any suitable manner in one or more embodiments. One skilled in the relevant art will recognize, in light of the description herein, that the subject disclosure can be practiced without one or more of the specific features or advantages of a particular exemplary embodiment. In other instances, additional features and advantages may be recognized in certain embodiments that may not be present in all exemplary embodiments of the present disclosure.

Referring now to the drawings,FIG. 1illustrates an agricultural harvester100in accordance with an exemplary embodiment of the present disclosure. For exemplary purposes only, the agricultural harvester is illustrated as a combine harvester. The harvester100includes a header102attached to a forward end of the harvester100, which is configured to cut crops, including (without limitation) small grains (e.g., wheat, soybeans, grain, etc.), and to induct the cut crops into a feederhouse106as the harvester moves forward over a crop field.

The header102includes a frame103having a floor104that is supported in desired proximity to the surface of a crop field. First and second cutting assemblies200A,200B extend transversely along a forward edge of the floor104i.e., in a widthwise direction of the harvester. The first and second cutting assemblies300A,300B, described in greater detail hereinafter, are configured to cut crops in preparation for induction into the feederhouse106. The header may include one or more draper conveyor belts for conveying cut crops to the feederhouse106, which is configured to convey the cut crops into the harvester for threshing and cleaning as the harvester moves forward over a crop field. The header102can further include an elongated, rotatable reel116which extends above and in close proximity to the first and second cutting assemblies300A,300B. The rotatable reel116is configured to cooperate with one or more draper conveyors in conveying cut crops to the feederhouse106for threshing and cleaning. While the foregoing aspects of the harvester are being described with respect to the header shown, the cutting assembly of the subject application can be applied to any other header having use for such a cutting assembly.

The cutting assemblies300A,300B extend along a forward edge110of the floor104, and are generally bounded by a first side edge112and an opposing second side edge114, both adjacent to the floor.

According to an exemplary embodiment as shown inFIG. 1, the cutting assemblies300A,300B include a first cutter bar342and a second cutter bar342′. The cutting assemblies300A,300B are driven by a knife drive assembly320, unillustrated inFIG. 1but described below, that drives cutter knife heads341,341′ in oscillating motion whereby the knife heads move laterally to the left and right. Additional exemplary cutter knife heads applicable to the present exemplary embodiments are disclosed e.g., in U.S. Pat. Nos. 7,730,709 and 8,151,547, the entire disclosures of which are incorporated by reference herein in their entirety for all purposes.

Referring toFIGS. 3 and 4, the knife drive assembly320includes a housing322that houses a pair of epicyclical drives224,226that convert rotational motion to oscillating motion in a manner described in more detail below. The first and second epicyclical drives224,226are indirectly mounted to the header frame103by virtue of the housing222.

FIG. 2depicts both an exploded perspective view of the first epicyclical drive224and an assembled perspective view of the second epicyclical drive226. The first epicyclical drive224(wherein the second epicyclical drive226is constructed in a mirror image-like fashion) includes a first rotatable wheel232having a first vertical or substantially vertical rotational axis234. The first epicyclical drive further includes a first disk236having a first vertical or substantially vertical eccentric axis238rotatable about the first vertical or substantially vertical rotational axis234. A first fitting240, described below, is received in and carried by the first disk236. Operation of the first epicyclical drive results in rotational motion of the first disk236, as well as linear oscillating or substantially linear oscillating motion of the first disk236in a direction transverse to the first vertical or substantially vertical rotational axis234. The oscillating motion of the first disk236is in line with a longitudinal axis of the first cutter bar342.

Likewise, the second epicyclical drive226includes a second rotatable wheel232′ having a second vertical or substantially vertical rotational axis234′. The second epicyclical drive further includes a second disk236′ having a second vertical or substantially vertical eccentric axis238′ rotatable about the second vertical or substantially vertical rotational axis. A second fitting240′, described below, is received in and carried by the second disk236. Operation of the second epicyclical drive results rotational motion of the second disk236′, as well as linear oscillating or substantially linear oscillating motion of the second disk in a direction transverse to the second vertical or substantially vertical rotational axis. So constructed and arranged, the second rotatable wheel232′ is adjacent the first rotatable wheel232and the second vertical or substantially vertical rotational axis234′ is parallel to and spaced from the first vertical or substantially vertical rotational axis234. In addition, the first vertical or substantially vertical rotational axis of the first rotatable wheel is parallel to the first eccentric axis of the first disk, and the second vertical or substantially vertical rotational axis of the second rotatable wheel is parallel to the second eccentric axis of the second disk. In other words, the first and second eccentric axes are likewise vertical or substantially vertical.

The first rotatable wheel232is mounted for rotation on an outer bearing or bushing246which is seated in a first upwardly facing opening248of a first lower rotatable wheel250. The first rotatable wheel232is affixed for rotation to the first lower rotatable wheel250via a generally crescent-shaped connector252by fasteners such as screws, bolts, or the like. The first lower rotatable wheel250is mounted for rotation in a lower outer bearing or bushing254. Situated between the first rotatable wheel232and the first lower rotatable wheel250is a stationary central gear256having internal gear teeth258. A shaft260has external gear teeth262adapted to matingly engage the internal gear teeth258of the central gear256. Shaft260has portions264,266that respectively rotate in an upper inner bearing or bushing268which resides in an opening270in the first rotatable wheel232and a lower inner bearing or bushing272which resides in an opening274in the first lower rotatable wheel250. The upper end of the shaft260has a splined or toothed exterior276that is adapted to matingly engage a similarly splined or toothed interior of the first fitting240, and the shaft260is secured to the first fitting240by a bolt or the like. It is seen inFIG. 2that the second epicyclical drive226includes a second lower rotatable wheel250′ having a second upwardly facing opening248′ for receiving the assembled components of the second epicyclical drive.

Movement of the several components of the first epicyclical drive224is as follows. A suitable drive mechanism284such as the illustrated fluid motor, a drive shaft, a power take-off (PTO) shaft, an electric motor, belts, chains or a combination of such drives includes a drive shaft285having a drive gear287, e.g. a bevel gear. As shown inFIG. 2, the drive mechanism extends between and is operatively engaged with the first and second rotatable wheels232,232′. The drive shaft285, via the gear287, engages and rotates a gear278, e.g. a bevel gear, in a first direction. Affixed to the gear278is a gear280, e.g., a spur gear, which engages and drives a first driven gear286operatively connected to the first rotatable wheel232. More particularly, the first driven gear286is affixed to the first lower rotatable wheel250and is driven by gear280causing rotation thereof as well as the first rotatable wheel232in a direction opposite the first direction about the first vertical or substantially vertical rotational axis234. As a result, the shaft260is carried by the upper and lower inner bearings or bushings268,272residing in openings270,274in the first rotatable wheel232and the first lower rotatable wheel250whereby the shaft260is caused to orbit about the first substantially vertical rotational axis234. As the shaft260orbits about the first substantially vertical rotational axis234, its gear teeth262engage gear teeth258of the stationary central gear256causing counter-rotation of the shaft260and the first disk236engaged therewith via the first fitting240. Thus, as the first disk236rotates, it exhibits a linear oscillating or substantially linear oscillating motion in a direction transverse to the first substantially vertical rotational axis234.

Operation of the second epicyclical drive226produces an identical but opposite oscillating motion in its second disk236′. That is, the gear280rotates in a first direction and engages and drives a second driven gear286′ operatively connected to the second rotatable wheel232′. More particularly, the second driven gear286′ is affixed to the second lower rotatable wheel250′ and is driven by gear280causing rotation thereof as well as the second rotatable wheel232′ in a direction opposite or substantially opposite the first direction about the second vertical or substantially vertical rotational axis234′. Further, the unillustrated components of the second epicyclical drive226move in directions opposite their counterparts in the first epicyclical drive224. Thus, the first and second disks236,236′ of the first and second epicyclical drives are configured to oscillate in opposing directions and in a direction along a single plane. Consequently, at one extreme in the motion of the first and second epicyclical drives224,226, the first and second disks236,236′ are at a minimum spaced apart distance from one another and at the opposite extreme the first and second disks236,236′ are at a maximum spaced apart distance from one another for purposes of vibration cancellation. As is known in the art, vibration causes wear and tear on the various moving components of a cutter bar knife drive assembly. Thus, the present construction effectively minimizes vibration thereby effectively reducing harmful wear and tear.

In order to achieve effective vibration cancellation, the first and second epicyclical drives224,226are timed such that the cutter bars342,342′ have substantially equal and opposite motions. The driven gear278and the gear280affixed thereto provide a timing coupling suitable to achieve this motion. In other words, the oscillating motions of the first and second disks236,236′ are configured to coincide with one another to effectuate vibration cancellation between the first and second cutter bars. Accordingly, when connected to cutter bar knife heads241,241′ the disks236,236′ of the first and second epicyclical drives224,226move the cutter bars back and forth in horizontal or substantially horizontal motion as the cutting knives of the cutter bars cut crop while the agricultural harvester100and header102move forwardly over the crop.

The first and second cutter bars are configured, e.g., as shown inFIGS. 3 and 4. The first cutter bar342extends in a direction transverse to the first vertical or substantially vertical rotational axis234, and the second cutter bar342′ extends in a direction transverse to the second vertical or substantially vertical rotational axis234′ opposite the first cutter bar. In this way, the oscillating motion of the first disk236is in line with a longitudinal axis of the first cutter bar342and the oscillating motion of the second disk236′ is in line with a longitudinal axis of the second cutter bar342′.

Referring toFIGS. 2-4, the first rotatable wheel232is adjacent to the first cutter bar342and the second rotatable wheel232′ is adjacent to the second cutter bar342′. Further, the medial ends of the first and second cutter bars342,342′ at the cutter bar knife heads241,241′ are formed with circular openings289,289′, respectively, which rotatably receive the first and second disks236,236′. In this way, the first and second cutter bars are directly connected to and moved by the first and second disks236,236′, respectively.

In addition, the first and second vertical or substantially vertical rotational axes of the first and second epicyclical drives224,226extend perpendicular or substantially perpendicular to the cutter bars342,342′ of the header102. In other words, the vertical or substantially vertical rotational axes234,234′ of the epicyclical drives face an upwardly or substantially upwardly direction whereby the first rotatable wheels232,232′ are oriented horizontally or substantially horizontally, i.e., their rotational axes being vertical or substantially vertical. In short, the epicyclical drives224,226face an upwardly direction.

As shown inFIG. 3, the epicyclical drives224,226are mounted centrally along the header frame. It is understood however that the epicyclical drives may be mounted to the header frame at a distance spaced from the center of the header. The header comprises at least one conveyor supported by the header frame for transporting cut crop from the cutter bars to the feederhouse106. In the illustrated example, the at least one conveyor is an infeed draper conveyor390and/or a lateral draper conveyor392the functions and operations of which are well known in the art. The epicyclical drives224,226are positioned between the first and second cutter bars342,342′ and the conveyor, e.g. the infeed draper conveyor390. It is understood, however, that the epicyclical drives may be positioned between the first and second cutter bars and one or the other of the lateral draper conveyors392.

As shown inFIGS. 3 and 4, the header further comprises a central cutter bar294adjacent the epicyclical drives224,226. According to an aspect, the central cutter bar has a longitudinal extent greater than a width of the epicyclical drives and positioned between the first and second cutter bars.FIG. 3reveals that cutter bars342,342′ overlap the cutting region of the central cutter bar294to assure gapless cutting of crop across the width of the header102.FIG. 4reveals that cutter bars342,342′ include sloped portions293,293′, respectively, located adjacent the medial ends of the cutter bars for providing vertical clearance to accommodate the housing322as the cutter bars oscillate back and forth.

It is understood that while the epicyclical drives224,226have been described above as being directly supported by the frame103, the subject disclosure is not so limited. That is, the epicyclical drives can be indirectly supported by the frame. For example, the epicyclical drives can be carried by pivoting flex arms that are themselves connected to the frame.

According to the exemplary embodiments of the subject disclosure, the epicyclical drives224,226are directly connected to and move their respective cutter bars without any intervening structures. In other words, the cutter bars directly engage the first and second disks236,236′ of the epicyclical drives at the circular openings289,289′. This advantageously results in a compact arrangement of parts which avoids the need for drive elements or other intervening structure to span a distance between the epicyclical drives and the cutter bars. Consequently, moments or other forces that can lead to detrimental stresses in the epicyclical drives are minimized. Stated differently, the direct connection of the epicyclical drives224,226to the first and second cutter bars minimizes fatigue caused by moments arising from arms extending from epicyclical drives to the cutter bars as is the case with conventional epicyclical knife drives.

Additionally, the assembly has less mass and is lighter in weight than conventional designs which is advantageous because the combine requires less energy to lift the header and there is less mass to float on the ground thereby reducing the likelihood of the cutter bars digging into the ground during operation.