Feeder gearbox, e, combined harvester

Abstract

Feeder gearbox, and combine harvester. Feeder gearboxes are provided for installation in combine harvesters. In embodiments, the feeder gearbox includes a gearbox housing, an output shaft rotatable around a geometric output shaft, and a primary drive input. The primary drive input is mechanically connected to a combine harvester drive when the feeder gearbox is installed on it. A reverse drive input is mechanically connected to a combine harvester reverse motor when the feeder gearbox is installed on the combine harvester.The feeder gearbox additionally includes a selector mechanism within the gearbox housing that moves between a primary drive position and a reverse drive position, a primary gear train that transmits rotation from the primary drive input to the output shaft when the selector mechanism is in the primary drive position, and a reverse worm drive that transmits rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position.

Description

/ 39 Gearbox for feeder and combine harvester DESCRIPTION FIELD

[001] This description refers to feeder gearboxes containing reverse auger drives, as well as to combine harvesters fitted with such feeder gearboxes. FUNDAMENTALS OF DESCRIPTION

[002] Combine harvesters (also referred to as “agricultural combines”) have greatly improved the efficiency with which corn, canola, soybeans, wheat, cereals, sunflowers, and other crops are harvested, threshed, cleaned, and collected for distribution to consumers. By common design, a combine harvester includes a feeder to which different types of harvesting heads, or more simply, “heads,” can be attached. A head may have a relatively wide, laterally elongated form factor to allow the cutting of a wide row of crops as the combine moves through a field in a forward direction. The head may also include a laterally extending auger, and other transport mechanisms, which admit harvested crops and direct the crops to an opening in a mid-rear region of the head.The feeder receives the harvested crop plants that pass through this opening and transports the crops further into the combine harvester for additional processing. To provide this function, the feeder may also contain a conveyor belt mounted on a tunnel-type feeder frame. Additionally, the feeder may include a modular gearbox (herein, the “feeder gearbox”) mounted on one side of the feeder frame. The feeder gearbox serves as a transmission and a rotational speed reduction, connecting a... Petition 870250010514, dated 07 / 02 / 2025, page 10 / 137 / 39 combine harvester drive to the feeder conveyor belt and, in many cases, to one or more driven components of the header, such as the aforementioned auger-type conveyor. The feeder gearbox also usefully provides a so-called "reverser" function, which allows the driven components of the feeder and header to be temporarily driven in a reverse direction to help remove any blockage or obstruction in the crop flow that may occur during combine harvester operation. SUMMARY OF DESCRIPTION

[003] Feeder gearboxes are provided for installation in combine harvesters including reverse drives and reverse motors. In embodiments, the feeder gearbox includes a gearbox housing, an output shaft mounted in the gearbox housing for rotation around a geometric output axis, and a primary drive input. The primary drive input is rotationally mounted in the gearbox housing and mechanically connected to the combine harvester's drive when the feeder gearbox is installed thereon. A reverse drive input is additionally rotationally mounted in the gearbox housing and mechanically connected to the reverse motor, again considered when the feeder gearbox is installed on the combine harvester.The feeder gearbox includes a shifting device or selector mechanism in the gearbox housing and moves between a primary drive position and a reverse drive position, a primary gear train that transmits rotation from the primary drive input to the output shaft when the selector mechanism is in the primary drive position, and a reverse worm drive that transmits rotation from the reverse drive input to the output shaft when the primary drive position is in the primary drive position. Petition 870250010514, dated 07 / 02 / 2025, page 11 / 137 / 39 selector mechanism is moved to the reverse drive position.

[004] In other embodiments, the feeder gearbox includes a gearbox housing, an output shaft mounted in the gearbox housing for rotation about a geometric output axis, and a planetary gear train contained in the gearbox housing. The planetary gear train in turn includes a ring gear, a sun gear, and a planetary carrier assembly. The ring gear is coupled to the gearbox housing in a rotationally fixed relationship. The sun gear is located within the gearbox housing, coaxial with the ring gear, and rotatable about the geometric output axis. Finally, the planetary carrier assembly is disposed within the gearbox housing, coaxial with the ring gear and the sun gear, and rotatable about the geometric output axis.The feeder gearbox additionally contains a reversing worm drive including a worm screw and worm gear. The worm gear engages the worm screw and is similarly rotatable around the output geometric axis. A selector mechanism is disposed within the gearbox housing and controllable to selectively mechanically couple (i) the planetary carrier assembly to the output shaft when the feeder gearbox operates in a first mode and (ii) the worm gear to the output shaft when the feeder gearbox operates in a second mode.

[005] Combine harvesters equipped with feeder gearboxes are further described. In various implementations, the combine harvester includes an impeller, a reversing motor, and a feeder gearbox. The feeder gearbox includes a gearbox housing, an output shaft rotationally mounted in the gearbox housing, a Petition 870250010514, dated 07 / 02 / 2025, page 12 / 137 / 39 primary drive input rotationally mounted in the gearbox housing and mechanically connected to the drive shaft, and a reverse drive input. The reverse drive input is rotationally mounted in the gearbox housing and mechanically connected to the reversing motor. A selector mechanism, additionally disposed within the gearbox housing, is movable between a primary drive position and a reverse drive position. A primary gear drive or train transmits rotation from the primary drive input to the output shaft when the selector mechanism is in the primary drive position, while a reversing worm drive transmits rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position.

[006] Details of one or more embodiments are presented in the attached drawings and in the description below. Other features and advantages will become apparent from the description, drawings and claims. BRIEF DESCRIPTION OF THE DRAWINGS

[007] At least one example of the present description will be described below in combination with the following figures: FIG. 1 is a side diagram of a combined harvester including a detachable tip, a feeder and a feeder gearbox containing a reversing auger drive (shown in Figs. 2-8, 11 and 12), as illustrated according to an example of the present description; FIG. 2 is a schematic of the feeder, the feeder housing, and various components used to support the operation of the feeder housing, as additionally included in the example combine harvester shown in Fig. 1; Figures 3 and 4 are front and rear isometric views, respectively, of the feeder gearbox, as illustrated in Petition 870250010514, dated 07 / 02 / 2025, page 13 / 137 / 39 in accordance with the example modality of the present description; Figures 5-7 are isometric views of the example feeder gearbox shown in Figures 2-4, depicted at various stages of assembly to reveal the reversing worm drive, the primary (planetary) gear train, a hydraulically actuated selector mechanism, and other components internal to the gearbox housing; FIG. 8 is an isometric view of the reversing worm drive, the primary (planetary) gear train, the hydraulically actuated selector mechanism, and a carrier-driven gerotor normally included in the example feeder gearbox; FIG. 9 is a cutaway isometric view of a hydraulic actuator suitably included in the selector mechanism (partially shown) of the feeder gearbox, in one embodiment; FIG. 10 is a front view of an additional indexing ring assembly suitably incorporated into the selector mechanism (partially shown) of the feeder gearbox, in one embodiment; and FIGS. 11 and 12 are cross-sectional views of the example feeder gearbox represented in direct and reverse drive modes, respectively, and including dashed lines illustrating the power transfer through the feeder gearbox.

[008] Identical reference symbols in the various drawings indicate identical elements. For the sake of simplification and clarity of illustration, descriptions and details of well-known features and techniques may be omitted to avoid unnecessarily obscuring the exemplary and non-limiting embodiments of the invention described in the subsequent Detailed Description. It should further be understood that features or elements that Petition 870250010514, dated 07 / 02 / 2025, p. 14 / 137 / 39 The images appearing in the attached figures are not necessarily drawn to scale, unless otherwise stated. DETAILED DESCRIPTION

[009] Embodiments of the present description are shown in the accompanying figures of the drawings briefly described herein. Various modifications of the example embodiments may be contemplated by those skilled in the art without departing from the scope of the present invention, as set forth in the appended claims. GENERAL REVIEW

[0010] As mentioned herein, combine harvester feeder chambers are typically equipped with modular gearboxes capable of operating in both direct and reverse drive modes. When placed in reverse drive mode, the feeder gearbox facilitates the operation of the feeder and header in a reverse direction, for example, to help remove blockages that interfere with the correct harvest intake into the combine. Several feeder gearbox designs are conventionally known and commercially available. By way of example, a known feeder gearbox design features a dual planetary gear system or train, which is used to change between direct and reverse drive modes according to commands received via operator input controls.Specifically, a selector mechanism located within the gearbox housing can be used to change whether a first rotatable component (e.g., a sun gear) or a second rotatable component (e.g., a ring gear) of the dual planetary system serves as a mechanical output of the system at a given opportune moment in time. As the sun and ring gears rotate in opposite directions, the rotational direction of the... Petition 870250010514, dated 07 / 02 / 2025, page 15 / 137 / 39 The output of the feeder gearbox (e.g., an output shaft) can be varied by positioning the selector mechanism in response to control commands provided by a combine operator. Such a design allows the feeder gearbox to be freely switched between direct drive and reverser modes, while a single mechanical input of the feeder gearbox is driven in a particular rotational direction by the combine impeller. Further description of a feeder gearbox containing such a double planetary gear train can be found in the following reference: US Patent No. 6,722,112 B2 entitled “REVERSER CONTROL FOR A COMBINE HARVESTER” and granted by the United States Patent and Trademark Office (USPTO) on April 20, 2004.

[0011] Feeder gearboxes containing double planetary gear systems, and other conventional feeder gearboxes, are capable of reliable operation for extended periods of time, while still providing reversing functionality as previously described. Nevertheless, conventional feeder gearboxes remain limited in certain respects. For example, in the case of many conventional feeder gearboxes, mechanical constraints prevent high-speed switching between direct drive and reversing modes. As a result, it may be necessary to reduce, if not completely stop, the rotation of the mechanical input of the feeder gearbox during switching from direct drive mode to reverse drive mode, and vice versa.Significant delay or "dead time" can consequently occur during switching between direct and reverse drive modes, while the gearbox may generally be unable to rapidly oscillate between direct and reverse drive of the driven components of the feeder and the... Petition 870250010514, dated 07 / 02 / 2025, page 16 / 137 / 39 tip. This can impair the efficiency of the feeder gearbox in removing blockages in the tillage intake when the gearbox operates in reverse mode, resulting in increased combine downtime. Conventional feeder gearboxes are also limited in other respects. For example, existing feeder gearboxes may rely on relatively complicated electrical feedback systems to ensure correct angular alignment between rotating members during switching between direct and reverse drive modes. This not only contributes to additional mode switching delay, but such electrical feedback systems introduce complexity, counterpart, and additional manufacturing cost to the gearbox.As a further drawback, conventional feeder gearboxes often provide limited operator control over speed variations when the feeder gearbox is placed in reverse drive mode.

[0012] There is a continued industry demand for feeder gearboxes that overcome the aforementioned shortcomings while still allowing for rapid switching between direct and reverse drive modes. To meet this demand, the following provides feeder gearboxes capable of rapidly switching between direct and reverse drive modes while having reduced complexity, manufacturing cost, and counterpart. Additionally, feeder configurations described below may allow for better control of the feeder gearbox rotational speed during reverse drive operation. Overall, such benefits are achieved through a single reversing worm drive architecture and primary gear train (e.g., planetary), combined with other components (e.g., a quick-switching indexing ring and associated shift device or selector mechanism) that allowsPetition 870250010514, dated 07 / 02 / 2025, page 17 / 137 / 39 highly efficient switching between direct and reverse drive modes. Additionally, in several embodiments, a dedicated motor (here, the “reversing motor”) can be used to drive the reversing worm drive to allow an operator to quickly engage the reversing worm drive, further providing greater speed control in reverse drive mode. The ability to quickly transition between speeds and, perhaps, rotational direction in reverse drive mode can be further enhanced in embodiments where the reversing motor takes the form of a hydraulic motor, which can be driven using a proportional control valve scheme.Additionally, the worm drive of the reverser can be selected to provide a relatively high mechanical reduction (e.g., a speed reduction greater than that provided by the primary gear train) to allow the size of the reverser motor to be minimized while still meeting torque demands. Further benefits provided by the feeder gearbox designs may include an improved lubrication scheme including, for example, a carrier-driven gerotor additionally contained within the gearbox housing. The end result is a structurally robust, relatively low-profile counterpart feeder gearbox capable of providing optimized reverse functionality to increase gearbox efficiency in assisting with the removal of obstructions or blockages in crop flow as such blockages arise during combine operation.

[0013] A further description of an example feeder gearbox containing a reversing worm drive will now be presented with regard to FIGS. 1-12. Although the example feeder gearbox is described in the context of a particular type of combine harvester, as shown in Figs. 1 and 2, it is understood that embodiments of the feeder gearbox may be used. Petition 870250010514, dated 07 / 02 / 2025, p. 18 / 137 / 39 internally to several other types of combine harvesters, with the combine harvester described below serving only as a suitable example. Additionally, the expression “combine harvester”, as it appears here, is defined to encompass any agricultural machinery used in crop harvesting and including a feeder to which a tip (or other crop intake device) may be attached, with the feeder and / or the tip containing at least one component driven through the feeder gearbox. EXAMPLE COMBINED HARVESTER AND REVERSER WORM DRIVE - CONTAINING FEEDER GEARBOX

[0014] FIGS. 1 and 2 schematically represent a front portion of a combine harvester 20 including feeder 22 on which a feeder gearbox 24 (FIG. 2) is mounted, as illustrated according to an exemplary embodiment of the present description. An exemplary tip 26 is attached to the front end of the feeder gearbox 24 for plow intake purposes. The tip 26 may be detachable from the feeder gearbox 24 and, more generally, from the combine harvester 20, and interchangeable with various other types of tips, as desired, to harvest a particular type of crop. The tip 26 takes the form of a belt-picking tip in the illustrated example and includes a tip chassis or frame 28.A collection conveyor belt 30, a transfer conveyor belt 32, and an auger-type conveyor 34 are rotationally mounted in series on the pointer frame 28, considered in a front-to-back direction. As shown in Fig. 2, the belts 30, 32 can extend around numerous rollers 36, and be supported by them, of which selected ones can be driven by one or more motors not shown additionally mounted on the pointer frame 28. Comparatively, the... Petition 870250010514, dated 07 / 02 / 2025, p. 19 / 137 / 39 auger-type conveyor 34 can be mounted on an auger shaft 38, which extends between opposite side walls of the tip frame 28 and is driven through the feeder gearbox 24 during operation of the combine 20. In the illustrated example, the auger shaft 38 is mechanically coupled to the output of the feeder gearbox via a pulley and shaft coupling 40. The particular way in which the auger-type conveyor 34 is connected to the mechanical output of the feeder gearbox 24 may differ in additional embodiments.

[0015] The feeder 22 includes a box-type housing or frame 42, which may be opened along longitudinally opposite ends to form a tunnel through which harvested plow plants pass. A feeder conveyor belt 44 is located within the feeder frame 42 and supported by a number of rollers 46 (FIG. 2), one or more of which may be driven via the feeder gearbox 24. Again, several different mechanical couplings may be used to transmit rotation from a mechanical output of the feeder gearbox 24 to the driven roller or rollers 46, as determined by the particular design of the feeder 22. In the example of FIGS. 1 and 2, specifically, a second pulley and shaft coupling 48 is provided for this purpose and mechanically couples an output of the feeder gearbox 24 to a pulley wheel provided around a projecting end of one of the rollers 46.Although the auger-type conveyor 34 of the tip 26 and the conveyor belt 44 of the feeder 22 are represented as driven by separate pulley and shaft couplings 40, 48 in the illustrated example, the driven components of the tip 26 and the feeder 22 may be driven by the same coupling or articulation system in additional embodiments of the combine harvester 20. In general, then, the particular way in which the driven components contained in the feeder 22 and / or the tip 26 are mechanically. Petition 870250010514, dated 07 / 02 / 2025, page 20 / 137 / 39 related to the output or outputs of the feeder gearbox 24 is not essential and may vary between modalities, as well as the type of component or components located in the feeder 22 and / or in the tip 26 that are driven by the gearbox 24.

[0016] As described herein, certain driven components of the feeder 26 (e.g., the auger conveyor 34) and the driven components of the feeder 22 (e.g., the conveyor belt 44) are mechanically powered through the feeder gearbox 24 during operation of the combine harvester 20. The mechanical power input applied to the feeder gearbox 24 to drive these components may be supplied by different internal drives or motors in the combine harvester 20. For example, and as schematically shown in Fig. 2, the feeder gearbox 24 may include a first mechanical input (herein, the “primary drive input”) mechanically connected to a primary drive 50 of the combine harvester 20, such as an internal combustion engine of the combine harvester.Additionally, the feeder gearbox 24 may include a second mechanical input (herein, the “reverse drive input”) mechanically connected to a second drive or motor 52 (herein, the “reverse motor 52”), which is separate and distinct from the primary drive 50. In relation to the primary drive 50 of the combine harvester 20, the reverse motor 52 may be a smaller motor of various types, including electric, pneumatic, and hydraulic motors. In the illustrated embodiment, and as indicated by symbol 54 in Fig. 2, the reverse motor 52 takes the form of a hydraulic motor and is consequently referred to hereafter as the “hydraulic reverse motor 52”. The use of a hydraulic motor for the reverse motor 52 may provide certain benefits, particularly when paired with a proportional valve control scheme that allows rapid speed control of the motor 52 and therefore of the feeder gearbox. Petition 870250010514, dated 07 / 02 / 2025, page 21 / 137 / 39 during operation in reverse drive mode, as further discussed below.

[0017] When it takes the form of a hydraulic motor, the reversing motor 52 can be driven or boosted using a hydraulic control system 56 containing at least one proportional control valve 58 that regulates the flow of hydraulic fluid to the motor 52. In such embodiments, the proportional control valve or valves 58 are fluidically coupled to the reversing motor 52 by means of appropriate flow lines, as generically represented in Fig. 2 by line 60. The hydraulic control system 56 may also include various other components 62, including valve actuators, pumps, reservoirs, filters, and the like, as is typical of such control systems. Additionally, and as indicated in Fig. 2 by line 64, one or more additional hydraulic flow lines may be present and extend from the hydraulic control system 56 to one or more ports of the feeder gearbox 24.Flow line(s) 64 may allow fluidic control of a hydraulic actuator contained in a selector mechanism used to change or switch the gearbox 24 between direct and reverse drive modes, as described in more detail below with regard to FIGS. 3-12, noting in particular FIGS. 9, 11 and 12. In further implementations, the feeder gearbox 24 may be switched between two or more operating modes (the direct and reverse drive modes described below) using a different type of selector mechanism, whether manual, electric, hydraulic and / or pneumatic, in which case flow line(s) 64 may be omitted. Additionally, several other flow lines may fluidically connect to the feeder gearbox 24, such as lubricant conduits, but are not shown in the schematic of Fig.2 for the sake of clarity; examples of such lubricant flow lines are, however, shown and described below with regard to FIGS. 3 and 4. Petition 870250010514, dated 07 / 02 / 2025, page 22 / 137 / 39

[0018] The operation of the hydraulic control system 56 is controlled by means of at least one controller, which is placed in signal communication with the hydraulic control system 56 using any suitable mechanical, hydraulic and / or electrical connection architecture (physical or wireless). For example, and with continued reference to FIG. 2, the operation of the hydraulic control system 56 may be controlled by means of a propeller control unit (ECU) 66 internally to the combine harvester 20; for example, appropriate control outputs of the ECU 66 may be electrically coupled to the actuator or actuators that position the control valve(s) 58 in the hydraulic control system 56, as indicated by the dashed line 68. The ECU 66 may also control various other functions of the primary propeller 50 and / or other internal devices in the combine harvester 20; however, this is secondary to the present description.During operation, the ECU 66 can issue commands to the hydraulic control system 56 to selectively position the selector mechanism within the feeder gearbox 24 and control the reversing motor 52, as further described herein. The ECU 66 can issue such commands in response to operator input received through one or more operator input devices 70, 72 coupled to the ECU 66 via signal lines 74, 76, respectively. The operator input devices 70, 72 can be located in the cab or operator station 51 of the combine harvester 20, as shown in Fig. 1, and manually controlled by an operator piloting the combine harvester 20. The particular form assumed by the operator input device(s) 70, 72 will vary and may include physical and / or virtual forms (e.g., graphical user interface).In the illustrated example, operator input devices 70, 72 are generically represented as including a physical button input 72, which can be used to activate the reverse drive mode of the feeder gearbox 24; and a game lever or switch. Petition 870250010514, dated 07 / 02 / 2025, page 23 / 137 / 39 rotatable 70, which can be used to control the speed of the reversing motor 52 when the feeder gearbox 24 is placed in reverse drive mode.

[0019] The mechanical output or outputs of the feeder gearbox 24 can be selectively driven by either the primary drive 50 or the reversing motor 52, depending on the particular mode in which the gearbox 24 is placed at a given opportune moment in time. As noted herein, the feeder gearbox 24 includes a primary drive input and a reverse drive input, which are mechanically connected to the primary drive 50 and the reversing motor 52, respectively, in some manner. In the illustrated embodiment, and only by way of non-limiting example, the primary drive input of the feeder gearbox 24 takes the form of an external pulley housing 78 rotationally coupled and arranged around a stationary housing of the gearbox 24, as further described below.When it takes the form of an external pulley housing like this, the primary drive input 78 (alternatively referred to as the “external pulley housing 78”) can be mechanically connected to an output shaft of the primary drive 50 via at least one pulley 80 and belt 82 (FIG. 2). Comparatively, the reverse drive input of the feeder gearbox 24 can take the form of a reverser input shaft 84, which projects at an angle from one side of the feeder gearbox housing 24. The reverser input shaft 84 is mechanically connected, either directly or indirectly, through any number of intervening motion transmission components, to an unshown output of the reverser motor 52 when the feeder gearbox 24 is installed on the combine harvester 20.

[0020] As previously indicated, the 24 feeder gearbox is operable in at least two operating modes, Petition 870250010514, dated 07 / 02 / 2025, page 24 / 137 / 39 selected using operator input devices 70, 72: a standard or direct drive mode, and a reverse drive mode. In direct drive mode, the feeder gearbox 24 mechanically couples the combine drive 50 to the mechanical output(s) of the gearbox 24 and therefore to the feeder conveyor belt 44 and to the driven components (e.g., the transfer auger 34) of the tip 26, when present. Simultaneously, the feeder gearbox 24 mechanically disconnects the reversing motor 52 from the mechanical output or outputs of the gearbox 24. In this way, the primary drive 50 can drive the feeder conveyor belt 44 and the transfer auger 34 in a forward direction as the combine harvester 20 is driven over a field by an operator seated at the operator station 51 (FIG. 1).As the combine harvester 20 is piloted in this manner, and referring briefly again to FIG. 1, crop plants are split and carried to the front opening of the header 26 by means of the collection conveyor belt 30. The split crop plants are then delivered to the feeder 22 by means of the transfer conveyor belt 32 and auger 34 at the header 26. Next, the crop plants move through the tubular frame 42 of the feeder 22 by the action of the feeder conveyor belt 44. Positioned immediately behind the feeder 22, a rotary drum conveyor 86 subsequently delivers the newly harvested crops to a threshing and separating section 88 for further processing by the combine harvester 20. The crop plants are threshed, separated and transported through still additional sections of the combine harvester 20 for further processing and cleaning.Grains, or other cut material extracted from harvested crops, are then delivered to a storage tank (grain) 90 for collection and temporary storage. Petition 870250010514, dated 07 / 02 / 2025, page 25 / 137 / 39

[0021] In the manner described above, the combine harvester 20 can collect crop plants that are split and swallowed by the tip 26 and the feeder 22 as the combine harvester 20 is driven in a forward direction. Occasionally, however, a need may arise to drive the feeder 22 and tip 26 in a reverse direction, for example, to help remove any blockage that may occur and interrupt crop intake into the combine harvester 20. Thus, when such a need arises, an operator can use controls 70, 72 to change or switch the feeder gearbox 24 to reverse drive mode; although it is not prevented to some degree that automation may be applied during the change of the gearbox 24 to reverse drive mode in other implementations.During a change to reverse drive mode, the feeder gearbox 24 mechanically couples the reversing motor 52 to the mechanical output of the feeder gearbox, such as the output shaft described below 104, while still disconnecting the combine drive 50 from it; although the combine drive 50 may continue to drive the rotation of the primary drive input (e.g., the external pulley housing 78) of the gearbox 24. In a control scheme, the feeder gearbox 24 is placed in reverse drive mode by means of transmitting appropriate pressure signals to the feeder gearbox 24 conducted through the flow line(s) 64, with the pressure signals then causing a selector mechanism in the feeder gearbox 24 to effect the desired mode change.Again, such pressure signals can be controlled by the ECU 66 in response to operator input commands received through the operator input devices 70, 72; for example, the pressure in the line or flow lines 64 can be changed in a way that causes a hydraulic actuator to select the desired operating mode of the gearbox. Petition 870250010514, dated 07 / 02 / 2025, page 26 / 137 / 39 feeder gear 24.

[0022] Notably, the feeder gearbox 24 is capable of rapidly switching between direct and reverse drive modes for the reasons described below. Additionally, when placed in reverse drive mode, the mechanical output(s) of the feeder gearbox 24 is / are driven by the reverser drive motor 52, which can allow highly responsive and possibly bidirectional speed variations of the mechanical output(s) of the gearbox 24 to optimize the efficiency with which crop blockages are released and removed. This can be particularly valid when the reverser drive motor 52 takes the form of a hydraulically driven motor implemented using a proportional control valve system, as generally shown in Fig. 2.Advantageously, giving the reverser drive motor 52 such capabilities (e.g., the ability to rapidly increase and decrease rotational speeds, as well as reverse rotational directions to allow rapid oscillation) can improve the effectiveness and efficiency with which blockages in the tillage flow are addressed. This, in turn, can decrease the downtime of the combine harvester 20 and improve the overall efficiency of the combine harvester 20 during its use. This is highly desirable. A manner in which the feeder gearbox 24 can rapidly switch between direct and reverse drive modes of operation, as well as an example internal gear architecture of the gearbox 24, will now be described more fully below with regard to FIGS. 3-12.

[0023] Going to FIGS. 3 and 4, an example of the feeder gearbox 24 is shown with the following reference numbers reported by the previous drawing figures: reference number “78” denoting the external pulley housing 78 which serves as the primary mechanical input of the example gearbox 24 in the illustrated embodiment, and the Petition 870250010514, dated 07 / 02 / 2025, page 27 / 137 / 39, reference number “84” denoting the input shaft that serves as the reverse drive input of the gearbox 24. In addition to these components, the feeder gearbox 24 further includes a gearbox housing 92, 94, which contains a reversing worm drive, a primary gear train (e.g., planetary), a selector mechanism, and various other components, as shown and described in detail below with regard to FIGS. 5-12. Noting that the construction of the gearbox housing will vary between embodiments, in the present example, the gearbox housing 92, 94 is assembled from two primary components or corresponding parts: (i) a base housing piece 92, and (ii) a housing cover piece 94. The housing cover piece 94 is nested within the outer pulley housing 78, which extends around or encircles the cover piece 94.The cover piece 94 can, however, be viewed through a number of windows 98 provided in the pulley housing 78. The outer pulley housing 78 is capable of rotating relative to the gearbox housing 92, 94 around a geometric output axis, which is represented by the double-headed arrow 100 in Fig. 3. Comparatively, the gearbox housing 92, 94 can be affixed to the feeder frame 42 and remain stationary relative to it when the feeder gearbox 24 is installed on the combine harvester 20 (FIGS. 1 and 2).

[0024] When the feeder gearbox 24 is installed on the combine harvester 20, a flexible linkage, such as the belt 82 (FIG. 2), is arranged around the outer periphery of the external pulley housing 78 and used to transmit rotation from the primary drive 50 (FIG. 2) to the pulley housing 78. When thus driven, the external pulley housing 78 rotates around the geometric output axis 100 relative to the gearbox housing 92, 94 at a relatively high rate of speed. The feeder gearbox 24 serves as a mechanical reduction Petition 870250010514, dated 07 / 02 / 2025, p. 28 / 137 / 39, which converts this high-speed rotation into a lower-speed rotation with greater torque, better suited for driving the conveyor belt of feeder 44 (FIGS. 1 and 2) and the driven components of the tip 26. In this respect, the rotation of the outer pulley housing 78 can be additionally transmitted to an inner hub piece 96, which is arranged or nested in the housing cover piece 94 and shown more clearly in Figs. 11 and 12 (described below). The inner hub piece 96 is rotationally attached to the outer pulley housing 78 by means of a screw number 102, as shown in Fig. 3. From the rotating inner hub piece 96, rotation is then transmitted to a rotating member included in the primary (planetary) gear train, such as a sun gear as described below.

[0025] With continued reference to Figs. 3 and 4, an output shaft 104 is rotationally mounted in the gearbox housing 92, 94 for rotation about the output geometric axis 100; for example, the output shaft 104 may be centrally mounted relative to the gearbox housing 92, 94 and have a longitudinal geometric axis coaxial with the output geometric axis 100, as shown. The output shaft 104 may assume several different forms, provided that an external mechanical connection can be made on at least one end portion of the output shaft 104. In the illustrated embodiment, the output shaft 104 includes an externally grooved end portion 106, which projects from an opening in the gearbox housing 92, 94 for mechanical connection to the driven components of the feeder 22 and / or the tip 26. Additionally, and as shown more clearly in Fig.4, the output shaft 104 may include an internally fluted open-end portion 108. The internally fluted shaft end portion 108 may be accessible through an opening in a tubular protrusion 110 projecting from the base housing piece 92. As the output shaft 104 is a... Petition 870250010514, dated 07 / 02 / 2025, page 29 / 137 / 39 rigid body, the end portions 106, 108 will co-rotate in such a way that the provision of two coupling points is provided for convenience of mechanical fastening, rather than providing any variance in output speed. Thus, in various implementations, one end of the output shaft 104 can be mechanically connected to the driven feeder components (e.g., the feeder conveyor belt 44 shown in Figs. 1 and 2), while the other end of the output shaft is mechanically connected to the driven components of the tip 26 (e.g., the auger conveyor 34).In alternative embodiments, both the driven components of the tip 26 (if present) and the driven components of the feeder 24 may be mechanically connected to the same end portion of the output shaft 104 or, instead, to another component that serves as the mechanical output of the feeder gearbox 24.

[0026] A support arm 114 extends from the gearbox housing 92, 94 near the reverser input shaft 84. When the feeder gearbox 24 is installed on the combine harvester 20, the support arm 114 can support the reverser motor 52 (FIG. 2) and / or components used to mechanically connect the output of the reverser motor 52 to an external (e.g., grooved) end of the reverser input shaft 84. Numerous other mechanical and / or fluid connections can additionally be made when the feeder gearbox 24 is installed on the combine harvester 20. For example, and as best shown in Fig. 4, these connections can include fluid connections to lubricant ports 120, 122 via corresponding lubricant flow lines 116, 118.In one configuration, the hydraulic port 120 can serve as an inlet port, which draws oil (or another lubricant) into the feeder gearbox 24 by the influence of a pump, such as a gerotor contained in the housing. Petition 870250010514, dated 07 / 02 / 2025, page 30 / 137 / 39 gearbox 92, 94; for example, the gerotor 132 shown in Figs. 58 and described below. Conversely, the hydraulic port 122 may serve as an outlet through which oil is extracted from the feeder gearbox 24, filtered or otherwise conditioned, and then returned through the inlet port 120. The feeder gearbox 24 may further include a hydraulic control port 124, which may receive a pressurized hydraulic fluid to control a hydraulically actuated selector mechanism 126 further disposed within the feeder gearbox 24 (shown in Figs. 5, 6, 8 and 9, also described below).

[0027] Returning now to FIGS. 5-8, the internal components of the example feeder gearbox 24 are represented in various ways, with the feeder gearbox 24 shown at different stages of assembly in Figs. 5-7 and with the gearbox housing 92, 94, the internal rotating hub piece 96, and the external pulley housing 78 hidden in Fig. 8. Overall, the feeder gearbox 24 can be described as including at least five internal subsystems or assemblies in the illustrated example: (i) a primary gear train or drive 128; (ii) a reversing worm drive 130; (iii) an internal lubrication pump (here, a gerotor 132); (iv) the previously mentioned selector mechanism 126 including, among other components, a hydraulic actuator 134; and (v) an indexing ring assembly 136. These subsystems or assemblies contained in the gearbox housing 92, 94 are each described in turn below.

[0028] First addressing the primary gear train 128, this gear train takes the form of a single planetary gear system in the illustrated embodiment and is consequently referred to hereafter as the “primary planetary gear train 128” or, more simply, as the “planetary gear train 128”. In the embodiment Petition 870250010514, dated 07 / 02 / 2025, page 31 / 137 / 39 illustrated, however, the primary gear train 128 need not be realized as a single planetary gear system in all implementations of the feeder gearbox 24 and may instead assume various other forms, provided that the primary gear train 128 includes at least two mating gears and provides a mechanical connection between the outer pulley housing 78 and the output shaft 104 of the feeder gearbox 24. In one implementation, the primary planetary gear train 128 includes a ring gear 138, a sun gear 140, and a planetary carrier assembly 142, 144.The planetary carrier assembly 142, 144 includes, in turn, a rotatable carrier 142 supporting a number of planetary gears 144; for example, the carrier 142 may support three angularly spaced planetary gears 144, which are rotationally mounted on the carrier 142 by pins 112 identified in Figs. 6 and 8. The planetary gears 144 simultaneously engage or mesh with the inner toothed periphery of the ring gear 138 and the outer toothed periphery of the sun gear in the typical manner. Additionally, the sun gear 140 and the ring gear 138 are arranged in a concentric relationship, with the ring gear 138 circumscribing the sun gear 140. Furthermore, the sun gear 140, the ring gear 138, and the planetary carrier assembly 142, 144 are coaxial with the geometric output axis 100 in the present example.The primary planetary gear train 128 is also at least partially nested in the outer pulley housing 78 to give the feeder gearbox 24 a relatively compact form factor.

[0029] The ring gear 138 of the primary planetary gear train 128 is rotationally fixed with respect to the housing of the gearbox 92, 94 and, in this way, does not rotate with the sun gear 140 and the planetary carrier assembly 142, 144 when the gear train Petition 870250010514, dated 07 / 02 / 2025, page 32 / 137 / 39 primary planetary gear 128 is driven through the outer pulley housing 78 and the rotating inner hub piece 96. Any suitable mechanical coupling or anti-rotation device may be used to prevent rotation of the ring gear 138 when the primary planetary gear train 128 is driven. For example, the ring gear 138 may be captured between the base housing piece 92 and the housing cover piece 94, with rotation of ring gear 138 prevented by screws, alignment pins, or other fasteners 146 (various of which are identified in Figs. 5-7). In this case, fasteners 146 can extend through ring gear 138, base housing piece 92, and housing cover piece 94 when feeder gearbox 24 is assembled.

[0030] Unlike the stationary ring gear 138, the sun gear 140 and the planetary carrier assembly 142, 144 rotate around the output geometric axis 100 when the primary planetary gear train 128 is driven through the outer pulley housing 78 and the rotating inner hub piece 96. Rotation of the sun gear 140, the planetary carrier assembly 142, 144, the inner hub piece 96 and the output shaft 104 around the output geometric axis 100 is facilitated by several bearing elements (e.g., ball and roller) 156 distributed throughout the feeder gearbox 24. Similarly, rotation of the reversing input shaft 84, and the worm gear described below 158 including the reversing worm drive 130, can be facilitated by any number of bearing elements. For example, as shown more clearly in Fig.5, two ball bearings 160 can be mounted around the input shaft of the reverser 84 adjacent to opposite ends of the worm screw 158.

[0031] In addition to the worm gear 158 and ball bearings 160, the worm drive of the reversing gear 130 additionally includes a gear Petition 870250010514, dated 07 / 02 / 2025, page 33 / 137 / 39 worm gear 162 positioned in meshing engagement with the worm screw 158, which is mounted on the input shaft of the reverser 84 in a rotationally fixed relationship. The worm gear 162 includes a grooved portion 164, which is selectively rotationally engaged and rotationally disengaged from the intermediate grooved portion 148 of the output shaft 104 by means of an indexing ring 152 (included in the indexing ring assembly 136) and a grooved selector collar 154 (included in the selector mechanism 126). The internally grooved selector collar 154 is engaged by a selector fork 166, which can slide along a translational geometric axis parallel to the output geometric axis 100, guided by a linear guide pin 168.The selector collar 154 can thus move between: (i) a first position (here, the “direct drive position”) in which the selector collar 154 mechanically engages a first rotatable member included in the primary gear train 128 to the indexing ring 152 (namely, the carrier 142), and (ii) a second position (here, the “reverse drive position”) in which the selector collar 154 mechanically engages a second rotatable member included in the reversing worm drive 130 to the indexing ring 152 (namely, the worm gear 162). Movement of the internally grooved selector collar 154 and the selector fork 166 is controlled by means of the hydraulic actuator 134 in the illustrated example.In alternative embodiments, a different type of hydraulic, electric or pneumatic actuator may be integrated into the feeder gearbox 24, used to position the selector collar 154, and thereby select the operating mode of the feeder gearbox 24 as desired.

[0032] In the present example of the feeder gearbox 24, movement of the internally grooved selector collar 154 and the selector fork 166 is controlled by means of the hydraulic actuator 134 which forms part of the selector mechanism 126. Describing the actuator 134 in more detail, and referring now also to FIG. 9, the hydraulic actuator 134. Petition 870250010514, dated 07 / 02 / 2025, page 34 / 137 / 39 may include a hydraulically actuated piston 170, at least one mechanical spring 172, a hydraulic chamber 174, and a cover member 176 in a possible construction. Spring 172 is disposed within hydraulic chamber 174 and sits on cover member 176. Spring 172 is selected to exert a desired resilient predisposition force on the hydraulically actuated piston 170, impelling the movement of piston 170 to a position corresponding to the direct drive position of the internally fluted selector collar 154. The hydraulically actuated piston 170 and selector collar 154 can thus normally reside in the direct drive position such that the feeder gearbox 24 operates in direct drive mode by default and transitions to reverse drive mode when the pressure within hydraulic chamber 174 is varied.In this regard, when the hydraulic pressure within the hydraulic chamber 174 is duly varied due to changes in the pressure of the hydraulic fluid supplied through the hydraulic control port 124 (FIG. 4), the hydraulic piston 170 slides along a geometric axis of translation (parallel to the geometric output axis 100 in the illustrated example) to a position corresponding to the reverse actuation position of the selector collar 154; for example, to the left in the orientation shown in Fig. 9. Again, such variations in pressure can be made by the hydraulic control system 56 (FIG. 2), through the positioning of the valve elements, in response to operator commands received through operator input devices 70, 72.

[0033] Referring now to FIG. 10 in combination with FIGS. 39, the example indexing ring assembly 136 includes the previously mentioned fluted indexing ring 152 and a number of spring-predisposed pins 178. The spring-predisposed pin caps 178 are predisposed against an inner peripheral cam surface 180 of the indexing ring 152. For example, as shown more clearly in Fig. 10, the surface of Petition 870250010514, dated 07 / 02 / 2025, page 35 / 137 / 39 internal peripheral cam 180 of the indexing ring 152 may include valleys 182 to which the heads of the spring-predisposed pins 178 engage. The opposite ends of the spring-loaded pins 178 can be received on the fluted output shaft 104. The pins 178 are thus predisposed to extend into the interior of the deeper recess of the valleys 182 to drive the indexing ring 152 into a neutral rotational position relative to the output shaft 104. Simultaneously, the fluted output shaft 104 includes an external castellated peripheral portion (identified by reference number “183” in Fig. 7), with the castellations or protrusions received in corresponding slots defined by the internal peripheral cam surface 180 of the indexing ring 152. As shown in Fig.7, the protrusions of the castellated outer peripheral portion 183 of the output shaft 104 are given widths smaller than those of the slots provided on the inner periphery of the indexing ring 152 to allow rotation of the indexing ring 152 relative to the output shaft 104 in a limited angular range in any rotational direction, after which the protrusions make contact with the inner edges of the indexing ring 152 defining the inner peripheral cam surface 180. Co-rotation of the indexing ring 152 and the output shaft 104 in a common rotational direction around the geometric output axis 100 is thus ensured, while a limited initial angular movement of the indexing ring 152 relative to the output shaft 104 is allowed to accommodate slight angular misalignments between the ring 152 and the selector collar 154.A structural configuration like this helps in the rapid switching of the 24-feeder gearbox between direct and reverse drive modes, while also eliminating any need for an electrical feedback system.

[0034] FIGS. 11 and 12 are cross-sectional views of the example 24 feeder gearbox shown in direct drive mode and in a reverse drive mode, respectively. Petition 870250010514, dated 07 / 02 / 2025, page 36 / 137 / 39 First, let's address FIG. Figure 11 shows the feeder gearbox 24 in direct drive mode, where dashed line 184 represents the transfer of power flow through rotating components of the gearbox 24. Here, the internally grooved selector collar 154 is positioned to mechanically couple the indexing ring 152 to the grooved tubular extension 150 projecting from the carrier body 142 to the ring 152. As rotational input is applied to the pulley housing 78 by the action of the primary drive 50 of the combine harvester 20 (indicated in Fig. 11 by arrow 186), the inner hub piece 96 rotates together with the pulley housing 78 around the geometric output axis 100. The same occurs with the sun gear 140, which is grooved in the inner hub piece 96, co-rotating with the pulley housing 78 and the inner hub piece 96.

[0035] The rotation of the sun gear 140 drives the rotation of the planetary gears 144 and, more generally, the planetary carrier assembly 142, 144, noting again that the outer ring gear 138 is rotationally fixed to the gearbox housing 92, 94 and remains stationary. Since the selector collar 154 is currently in the forward drive position (the rightmost position in Fig. 11), rotation of the planetary carrier assembly 142 is transferred via the grooved portion 150 of the carrier 142 through the grooved selector collar 154, through the indexing ring 152, and to the middle grooved portion 148 of the output shaft 104. The rotational output of the feeder gearbox 24 (represented by arrow 188) is thus driven through the primary drive input of the feeder gearbox 24 (here, the outer pulley housing 78) when the feeder gearbox 24 is placed in direct drive mode.Overall, then, rotation is transferred from the sun gear 140, through the planetary carrier assembly 142, 144, and to the output shaft 104 when the gearbox. Petition 870250010514, dated 07 / 02 / 2025, page 37 / 137 / 39 of feeder 24 is installed on the combine harvester 20, the propeller 50 drives rotation of the primary drive input of the gearbox 24 (here, the external pulley housing 78 coupled to the sun gear 140 in a rotationally fixed relationship), and the selector mechanism 126 is in the primary drive position.

[0036] When it is desired to transition the feeder gearbox 24 to reverse drive mode, as indicated by operator commands received via operator input devices 70, 72 (FIG. 2), the pressure inside the hydraulic chamber 174 of the hydraulic actuator 134 (FIG. 9) is varied by the hydraulic control system 56 (FIG. 2). As previously described, this pressure variation inside the hydraulic chamber 174 causes the hydraulic piston 170, the selector fork 166 and the selector collar 154 to move to the reverse drive position; that is, to slide to the left in Figs. 11 and 12, as indicated by arrow 190. In this way, the selector mechanism 126 (which includes the hydraulic actuator 134 and the selector collar 154) is commanded to move from the primary drive position (FIG. 11) to the reverse drive position (FIG. 12).Substantially simultaneously, or following the movement of the selector mechanism 126 to the reverse drive position, the hydraulic control system 56 can also command the hydraulic control system 56 to circulate hydraulic fluid through the hydraulic reversing motor 52 to initiate rotation of the reversing input shaft 84 (if it is not already rotating) and thereby drive the output shaft 104 via the reversing worm drive 130. Specifically, and as represented by arrow 192 in Fig. 12, the reversing motor 52 applies rotational input to the reversing worm drive 130 via the reversing input shaft 84 when the feeder gearbox 24 operates in reverse drive mode.

[0037] As additionally indicated by the power flow line Petition 870250010514, dated 07 / 02 / 2025, page 38 / 137 / 39 In Fig. 12, rotation is transmitted through the worm screw 158 to the worm gear 162, from the grooved portion 164 of the worm gear 162, through the selector collar 154 and the indexing ring 152, and to the output shaft 104. Arrow 194 further represents the rotational output of the feeder gearbox 24 when operating in reverse drive mode and driven by the hydraulic reversing motor 52. More generally, rotation is transferred from the worm screw 158, through the worm gear 162, and to the output shaft 104 when the feeder gearbox 24 is installed on the combine harvester 20, the reversing motor 52 drives rotation from the reverse drive input (here, the reversing input shaft 84), and the selector mechanism 126 is in the drive position. reverse.Notably, when the feeder gearbox 24 operates in reverse drive mode, the outer pulley housing 78 may continue to rotate under the influence of the combine 20 drive 50; however, rotation of the outer pulley housing 78, and the corresponding rotation of the inner hub piece 96, sun gear 140 and planetary carrier assembly 142, 144 is not transferred to the output shaft 104 since the shaft 104 is currently rotationally decoupled from the tubular extension or grooved portion 150 of the carrier 142 by the selector collar 154 when in the reverse drive position. Put more succinctly, when in the reverse drive position, the selector mechanism 126 rotationally couples the worm gear 162 to the output shaft 104, while still rotationally decoupling the planetary carrier assembly 142, 144 from it.Conversely, when in the primary drive position, the selector mechanism 126 rotationally couples the planetary carrier assembly 142, 144 to the output shaft 104, while also rotationally disengaging the worm gear 162 from it.

[0038] In the manner described above, the rapid switching between the direct and reverse drive modes of the feeder gearbox 24 is Petition 870250010514, dated 07 / 02 / 2025, page 39 / 137 / 39 enabled. Furthermore, as the worm drive of the reverser 130 is driven by a dedicated motor (namely, the reverser motor 52 shown in Fig. 2), the direction in which the input of the worm drive of the reverser 130 rotates can be rapidly changed or oscillated, particularly the reverser motor 52 takes the form of a hydraulic motor controlled using one or more proportional control valves 58 (FIG. 2). Highly responsive bidirectional speed control is consequently obtained when the feeder gearbox 24 is placed in reverse drive control to maximize the efficiency with which the gearbox 24 is able to remove blockages that interrupt the flow of crop during operation of the combine harvester 20.An operator of the combine harvester 20 can use the input device 70 (e.g., a game lever or multi-position switch) to control the speed of the reversing motor 52 and thereby quickly remove any blockage in most cases. As an additional option, the ECU 66 (FIG. 2) can store one or more pre-programmed slack routines or schedules in a computer-readable memory. When executed via operator input controls 70, 72, the slack routine can cause the ECU 66 to command the reversing motor 52 to quickly increase, decrease, and reverse the speed of the reversing motor 52, in a manner optimized to quickly remove tillage intake blockages. In such embodiments, an operator can select a pre-programmed slack routine for execution using any suitable physical or virtual interface, such as any of the operator input controls 70, 72 shown in Fig. 2.As a more specific, though not limiting, example, ECU 66 may be operable in a quick lock-up mode in which ECU 66 commands the proportional control valve(s) 58 to repeatedly switch or oscillate between actuating the output shaft of the reversing motor 52 in a first rotational direction and in a second rotational direction, while the... Petition 870250010514, dated 07 / 02 / 2025, page 40 / 137 / 39 selector mechanism 126 resides in the reverse drive position shown in Fig. 12.

[0039] In several embodiments, the worm drive of the reversing gear 130 is advantageously selected to provide a relatively large mechanical reduction (rotational speed); for example, a rotational speed reduction greater than, and perhaps at least twice, that provided by the primary planetary gear train 128. For example, in one embodiment, the worm drive of the reversing gear 130 can be selected to provide a speed reduction equivalent to or greater than about 8:1 to convert the high-speed, low-torque input provided by the reversing motor 52 into a low-speed, high-torque output, optimized for driving the feeder 24 and / or the tip 26 (FIGS. 1 and 2) in reverse drive mode. Comparatively, the rotational speed reduction provided by the primary planetary gear train 128 can be approximately 4:1 in one embodiment.By selecting the worm drive of the reversing gear 130 to provide a large reduction in rotational speed, the size of the reversing motor 52 can be minimized, particularly when it takes the form of a hydraulic motor. In other embodiments, the worm drive of the reversing gear 130 can provide a speed reduction less than or equal to that provided by the primary planetary gear train 128.

[0040] Reliable operation of the feeder gearbox 24 can be optimized by actively lubricating the internal components of the gearbox 24, particularly the rotating components associated with the primary planetary gear train 128. In this regard, and as previously indicated, embodiments of the feeder gearbox 24 additionally include an internal lubricant pump for extracting lubricant to the gearbox housing 92, 94 in the form of the gerotor 132. By way of example, and referring briefly again to FIG. 8, the gerotor 132 may include an input gear 198, which Petition 870250010514, dated 07 / 02 / 2025, page 41 / 137 / 39 projects from a gerotor housing 200 and engages an external toothed peripheral portion 202 of the carrier 142. A lubricant port 204 may be provided in the gerotor housing 200 for receiving oil or another liquid lubricant. Such a structural configuration allows the rotor within the gerotor housing 200 to be rotationally driven by the rotation of the carrier 142 and, more generally, the primary planetary gear train 128. Additionally, in at least some implementations, the rotation of the planetary carrier assembly 142, 144 may be driven by the primary drive 50 of the combine harvester 20 independently of the particular mode in which the feeder gearbox 24 is placed.Thus, in such implementations, the gerotor 132 can similarly remain mechanically connected and continuously driven by the propeller 50 to ensure uninterrupted lubricant flow to the housing of the gearbox 92, 94. Low-friction rotation of the rotating components contained in the feeder gearbox 24 can thus be promoted to extend the overall service life of the gearbox 24. NUMBERED EXAMPLES OF THE GEARBOX FOR FEEDER AND COMBINE HARVESTERS EQUIPPED WITH THE SAME

[0041] The following examples of the feeder gearbox and associated combine harvesters are additionally provided and listed for ease of reference.

[0042] 1. A feeder gearbox is provided for installation in a combine harvester including a propeller and a reversing motor. In one embodiment, the feeder gearbox includes a gearbox housing, an output shaft mounted in the gearbox housing for rotation about a geometric output shaft, a primary drive input rotationally mounted in the gearbox housing and mechanically connected to Petition 870250010514, dated 07 / 02 / 2025, page 42 / 137 / 39 when the feeder gearbox is installed on the combine harvester, and a reverse drive input rotationally mounted in the gearbox housing and mechanically connected to the reversing motor when the feeder gearbox is installed on the combine harvester. A selector mechanism is disposed within the gearbox housing and movable between a primary drive position and a reverse drive position. A primary gear train or drive transmits rotation from the primary drive input to the output shaft when the selector mechanism is in the primary drive position, while a reverser worm drive transmits rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position.

[0043] 2. The feeder gearbox of example 1, wherein the primary gear train provides a first speed reduction during transmission of rotation from the primary drive input to the output shaft. Additionally, the reversing worm drive provides a second speed reduction during transmission of rotation from the reversing drive input to the output shaft, the second speed reduction being greater than the first speed reduction.

[0044] 3. The feeder gearbox of example 1, wherein the primary gear train includes a planetary carrier assembly having planetary gears supported by a carrier, the planetary carrier assembly additionally rotatable relative to the gearbox housing around the geometric output axis.

[0045] 4. The feeder gearbox of example 3, wherein the primary gear train additionally includes: (i) a sun gear that engages the planetary gears and is rotatable relative to the gearbox housing about the geometric output axis; and (ii) a ring gear that circumscribes the sun gear, Petition 870250010514, dated 07 / 02 / 2025, page 43 / 137 / 39 engaging the planetary gears, and rotationally fixed in relation to the gearbox housing.

[0046] 5. The feeder gearbox of example 4, in which rotation is transferred from the sun gear, through the planetary carrier assembly, and to the output shaft when the feeder gearbox is installed on the combine harvester, the propeller drives the rotation of the primary drive input, and the selector mechanism is in the primary drive position.

[0047] 6. The feeder gearbox of Example 4, additionally including a gerotor within the gearbox housing and mechanically coupled to the planetary carrier assembly. The gerotor impels the flow of lubricant into the gearbox housing when driven by the rotation of the planetary carrier assembly.

[0048] 7. The feeder gearbox of Example 4, wherein the primary drive input includes an outer pulley housing coupled to the sun gear in a rotationally fixed relationship, the primary gear train at least partially nested in the outer pulley housing.

[0049] 8. The feeder gearbox of example 3, wherein the reversing worm drive includes a worm screw and a worm gear, which is engaged by the worm screw and which is rotatable around the geometric output shaft. Rotation is transferred from the worm screw, through the worm gear, and to the output shaft when the feeder gearbox is installed on the combine harvester, the reversing motor drives the rotation of the reverse drive input, and the selector mechanism is in the reverse drive position.

[0050] 9. The feeder gearbox of example 8, wherein the reverse drive input includes a shaft projecting from the gearbox housing and coupled to the worm screw in a Petition 870250010514, dated 07 / 02 / 2025, page 44 / 137 / 39 fixed rotational relationship.

[0051] 10. The feeder gearbox of example 1, wherein the selector mechanism includes an indexing ring coupled to the output shaft for co-rotation therewith and a selector collar engaging the indexing ring. The selector collar is sliding relative to the indexing ring between: (i) a first position in which the selector collar mechanically couples a first rotatable member included in the primary gear train to the indexing ring; and (ii) a second position in which the selector collar mechanically couples a second rotatable member included in the reversing worm drive to the indexing ring.

[0052] 11. The feeder gearbox of example 10, wherein the first rotatable member and the second rotatable member comprise a carrier and a worm gear, respectively.

[0053] 12. A feeder gearbox for installation in a combine harvester, the feeder gearbox including: a gearbox housing, an output shaft mounted in the gearbox housing for rotation about a geometric output axis, and a planetary gear train contained in the gearbox housing. The planetary gear train in turn includes: a ring gear coupled to the gearbox housing in a rotationally fixed relationship with it; a sun gear within the gearbox housing, coaxial with the ring gear, and rotatable about the geometric output axis; and a planetary carrier assembly within the gearbox housing, coaxial with the ring gear and the sun gear, and rotatable about the geometric output axis.The feeder gearbox additionally includes a reversing worm drive having a worm screw contained within the gearbox housing as well. Petition 870250010514, dated 07 / 02 / 2025, page 45 / 137 / 39 a worm gear engaged by the worm screw and rotatable around the geometric output axis. A selector mechanism is controllable to selectively mechanically couple (i) the planetary carrier assembly to the output shaft when the feeder gearbox operates in a first mode and (ii) the worm gear to the output shaft when the feeder gearbox operates in a second mode.

[0054] 13. The feeder gearbox of example 12, additionally including a gerotor within the gearbox housing and mechanically coupled to the planetary carrier assembly, the gerotor configured to be driven by the rotation of the planetary carrier assembly to impel the flow of lubricant to the gearbox housing.

[0055] 14. The feeder gearbox of example 12, in which the worm drive of the reversing gear provides a reduction in rotational speed at least twice that provided by the planetary gear train.

[0056] 15. Embodiments of a combine harvester equipped with a feeder gearbox are further provided. In one embodiment, the combine harvester includes an impeller, a reversing motor, and a feeder gearbox. The feeder gearbox in turn includes: an output shaft rotationally mounted in the gearbox housing; a primary drive input rotationally mounted in the gearbox housing and mechanically connected to the impeller; a reverse drive input rotationally mounted in the gearbox housing and mechanically connected to the reversing motor; a selector mechanism within the gearbox housing and movable between a primary drive position and a reverse drive position; a primary gear train that transmits rotation from the input of Petition 870250010514, dated 07 / 02 / 2025, page 46 / 137 / 39 primary drive for the output shaft when the selector mechanism is in the primary drive position; and a worm drive of the reverser that transmits rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position. CONCLUSION

[0057] In this way, feeder gearboxes were provided that could quickly switch between direct and reverse drive modes, while still having reduced complexity, manufacturing costs, and counterpart. Feeder gearbox embodiments include reverse worm drives and other components that allow a dedicated motor (the “reversing motor” described above) to drive the gearbox's rotation output (e.g., a centrally mounted output shaft) when the feeder gearbox operates in reverse drive mode.Greater operator control over speed variations when the feeder gearbox operates in reverse mode can be achieved as a result, while a relatively large reduction in rotational speed can be provided by the reversing worm drive (e.g., a rotational speed reduction greater than, and perhaps at least twice, that provided by, the primary gear train) to allow the size of the reversing motor to be minimized. Additionally, rapid switching between direct and reverse drive modes can be enabled using a selector mechanism, which allows quick switching between modes without requiring excessive reduction or rotational impediment of the primary drive input of the feeder gearbox, such as the external pulley housing in the example described above.Feeder gearbox designs may also include other unique and useful features, such as a gerotor driven through the carrier of a planetary gear system that serves as the gear train. Petition 870250010514, dated 07 / 02 / 2025, page 47 / 137 / 39 primary gear (e.g., planetary) of the feeder gearbox.

[0058] As used herein, the singular forms “a”, “an” and “the” should include the plural forms equally, unless the context clearly indicates otherwise. It is further understood that the terms “comprises” and / or “comprising”, when used in this specification, specify the presence of declared resources, integers, steps, operations, elements and / or components, but do not preclude the presence or addition of one or more other resources, integers, steps, operations, elements, components and / or groups thereof.

[0059] The description of the present description is given for illustrative and descriptive purposes only, but it is not to be considered exhaustive or limited to the description in the form described. Many modifications and variations will be apparent to those skilled in the art without departing from the scope and spirit of the description. Embodiments explicitly referenced herein have been chosen and described in order to better explain the principles of the description and its practical application, and to enable others skilled in the art to understand the description and recognize many alternatives, modifications, and variations in the example(s) described. Thus, various embodiments and implementations beyond those explicitly described are within the scope of the following claims. Petition 870250010514, dated 07 / 02 / 2025, p. 48 / 137

Claims

1 / 4 CLAIMS 1. Feeder gearbox (24) for installation in a combine harvester (20) including a propeller (50) and a reversing motor (52), the feeder gearbox (24) comprising: a gearbox housing (92, 94); an output shaft (104) mounted in the gearbox housing (92, 94) for rotation around a geometric output shaft (100); a primary drive input rotationally mounted in the gearbox housing (92, 94) and mechanically connected to the propeller (50) when the feeder gearbox (24) is installed in the combine harvester (20); a reverse drive input rotationally mounted in the gearbox housing (92, 94) and mechanically connected to the reversing motor (52) when that feeder gearbox (24) is installed on the combine harvester (20);a selector mechanism (126) within the gearbox housing (92, 94) and movable between a primary drive position and a reverse drive position; characterized in that it further comprises: a primary gear train (128) that transmits rotation from the primary drive input to the output shaft (104) when the selector mechanism (126) is in the primary drive position; and a reversing worm drive (130) that transmits rotation from the reverse drive input to the output shaft (104) when the selector mechanism (126) is in the reverse drive position.

2. Feeder gearbox (24) according to claim 1, characterized in that the primary gear train (128) provides a first speed reduction during transmission of rotation from the primary drive input to the output shaft (104); and in that the reversing worm drive (130) provides a second speed reduction during transmission of rotation from the reversing drive input to the output shaft (104), the second speed reduction being greater than the first speed reduction.

3. Feeder gearbox (24) according to claim 1, characterized in that the primary gear train (128) comprises a planetary carrier assembly including planetary gears (144) supported by a carrier (142), the planetary carrier assembly being rotatable relative to the gearbox housing (92, 94) around the geometric output axis (100).

4. Feeder gearbox (24) according to claim 3, characterized in that the primary gear train (128) further comprises: a sun gear (140) that engages those planetary gears (144) and that is rotatable relative to the gearbox housing (92, 94) around the geometric output axis (100); and a ring gear (138) that circumscribes the sun gear (140), engaging those planetary gears (144), and rotationally fixed relative to the gearbox housing (92, 94).

5. Feeder gearbox (24) according to claim 4, characterized in that the rotation is transferred from the sun gear (140), through the planetary carrier assembly, and to the output shaft (104) when that feeder gearbox (24) is installed on the combine harvester (20), the drive actuator drives the rotation of the primary drive input, and the selector mechanism is in the primary drive position.

6. Feeder gearbox (24) according to claim 4, characterized in that it further comprises Petition 870260077434, dated 04 / 08 / 2026, page 12 / 25 3 / 4 a gerotor (132) within the gearbox housing (92, 94) and mechanically coupled to the planetary carrier assembly.

7. Feeder gearbox (24) according to claim 3, characterized in that the reversing worm drive (130) comprises: a worm screw (158); and a worm gear (162) engaged by the worm screw (158) and rotatable around the geometric output shaft (100); wherein the rotation is transferred from the worm screw (158), through the worm gear (162), and to the output shaft (104) when the feeder gearbox (24) is installed on the combine harvester (20), the reversing motor (52) drives the rotation of the reverse drive input, and the selector mechanism is in the reverse drive position.

8. Feeder gearbox (24) according to claim 7, characterized in that the reverse drive input comprises a shaft (84) projecting from the gearbox housing (92, 94) and is coupled to the worm screw (158) in a rotationally fixed relationship.

9. Feeder gearbox (24) according to claim 1, characterized in that it further comprises an indexing ring (152) coupled to the output shaft (104) for co-rotation therewith; wherein the selector mechanism (126) further comprises a selector collar (154) engaging the indexing ring (152) and sliding with respect to it between: a first position in which the selector collar (154) mechanically couples a first rotatable member included in the primary gear train (128) to the indexing ring (152); and a second position in which the selector collar (154) couples Petition 870260077434, dated 04 / 08 / 2026, page. 13 / 25 4 / 4 mechanically a second member that is rotatable included in the reversing worm drive (130) to the indexing ring (152).

10. Feeder gearbox (24) according to claim 9, characterized in that the first rotatable member and the second rotatable member comprise a carrier (142) and a worm gear (162), respectively.

11. Combine harvester (20), comprising: a propeller (50); a reversing motor (52); and characterized in that it further comprises a feeder gearbox (24) as defined in any one of claims 1 to 10.

12. Combine harvester (20) according to claim 11, characterized in that the reversing motor (52) comprises a hydraulic motor having a motor output shaft mechanically connected to the reversing worm drive (130).

13. Combine harvester (20) according to claim 12, characterized in that it further comprises: a controller; and a proportional control valve (58) operatively coupled to the controller and hydraulically coupled to the hydraulic motor, the controller operable in an embodiment in which the controller commands said proportional control valve (58) to repeatedly switch between driving the motor output shaft in a first rotational direction and in a second rotational direction when the selector mechanism (126) is in that reverse drive position. Petition 870260077434, dated 04 / 08 / 2026, page 14 / 25

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