Feeder housing gearbox with reverse worm drive and combine harvester equipped with same

Abstract

A feed chamber gearbox mounted on a combine harvester is provided. In an embodiment, the feed chamber gearbox includes a gearbox housing, an output shaft rotatable about an output axis, and a main drive input. When the feed chamber gearbox is mounted on the combine harvester, the main drive input is mechanically connected to the engine of the combine harvester. When the feed chamber gearbox is mounted on the combine harvester, the reverse drive input is mechanically connected to the reverse motor of the combine harvester. The feed chamber gearbox further includes: a selector mechanism, the selector mechanism is within the gearbox housing and is movable between a main drive position and a reverse drive position; a main gear train, when the selector mechanism is in the main drive position, the main gear train transfers rotation from the main drive input to the output shaft; and a reverse worm drive, when the selector mechanism is in the reverse drive position, the reverse worm drive transfers rotation from the reverse drive input to the output shaft.

Description

Field of the Invention

[0001] The present disclosure relates to a feeder house gearbox accommodating a reverse worm drive, and to a combine harvester equipped with such a feeder house gearbox. Background Art

[0002] Combine harvesters (also referred to as "agricultural combine harvesters") have greatly improved the efficiency of harvesting, threshing, cleaning and collecting corn, rapeseed, soybeans, wheat, oats, sunflowers and other crops for distribution to consumers. According to the usual design, the combine harvester includes a feed chamber to which different types of harvesting heads or more simply "headers" can be attached. The header can have a relatively wide laterally elongated form factor to allow cutting and ingestion of a wide row of crops when the harvester travels across the field in the forward direction. The header can also include a laterally extending augers and other conveying mechanisms that ingest the harvested crops and direct the crops to an opening in the rear middle region of the header. The feed chamber receives the harvested crop plants through this opening and delivers the crops deeper into the combine harvester for further processing. In order to provide this function, the feed chamber can also accommodate a conveyor belt installed in a tunnel-shaped feed chamber frame. In addition, the feed house may include a modular gearbox (herein "feed house gearbox") mounted to the side of the feed house frame. The feed house gearbox serves as a transmission and rotational speed reducer connecting the engine of the combine harvester to the feed house conveyor belt and, in many cases, to one or more driven components of the header, such as the auger conveyor mentioned above. The feed house gearbox also usefully provides so-called "reverse" functionality that enables the driven components of the feed house and header to be temporarily driven in a reverse direction to help clear any blockages or obstructions in the grain flow that may occur during operation of the combine harvester. Summary of the invention

[0003] A feeder housing gearbox for mounting on a combine harvester comprising an engine and a reverse motor is provided. In an embodiment, the feeder housing gearbox comprises a gearbox housing, an output shaft mounted to the gearbox housing for rotation about an output axis, and a main drive input. The main drive input is rotatably mounted to the gearbox housing and mechanically connected to the engine of the combine harvester when the feeder housing gearbox is mounted on the combine harvester. A reverse drive input is further rotatably mounted to the gearbox housing and mechanically connected to the reverse motor, which is also contemplated when the feeder housing gearbox is mounted on the combine harvester. The feed chamber gearbox includes: a shifter or selector mechanism, which is within the gearbox housing and can be moved between a main drive position and a reverse drive position; a main gear train, which transfers rotation from the main drive input part to the output shaft when the selector mechanism is in the main drive position; and a reverse worm drive, which transfers rotation from the reverse drive input part to the output shaft when the selector mechanism is moved to the reverse drive position.

[0004] In other embodiments, the feed chamber gearbox includes: a gearbox housing; an output shaft, the output shaft is mounted to the gearbox housing for rotation about an output axis; and a planetary gear train, the planetary gear train is contained in the gearbox housing. The planetary gear train, in turn, includes a ring gear, a sun gear, and a planet 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 output axis. Finally, the planet carrier assembly is disposed within the gearbox housing, coaxial with the ring gear and the sun gear, and rotatable about the output axis. The feed chamber gearbox further houses a reverse worm drive including a worm and a worm wheel. The worm wheel engages the worm and is likewise rotatable about the output axis. A selector mechanism is disposed within the gearbox housing and is controllable to selectively (i) mechanically couple the planet carrier assembly to the output shaft when the feed chamber gearbox is operated in a first mode, and (ii) mechanically couple the worm gear to the output shaft when the feed chamber gearbox is operated in a second mode.

[0005] A combine harvester equipped with a feed chamber gearbox is further disclosed. In various embodiments, the combine harvester includes an engine, a reverse motor and a feed chamber gearbox. The feed chamber gearbox includes: a gearbox housing; an output shaft, the output shaft being rotatably mounted to the gearbox housing; a main drive input, the main drive input being rotatably mounted to the gearbox housing and mechanically connected to the engine; and a reverse drive input. The reverse drive input is rotatably mounted to the gearbox housing and mechanically connected to the reverse motor. A selector mechanism further disposed in the gearbox housing is movable between a main drive position and a reverse drive position. When the selector mechanism is in the main drive position, a main gear drive or a main gear train transfers rotation from the main drive input to the output shaft, and when the selector mechanism is in the reverse drive position, a reverse worm drive transfers rotation from the reverse drive input to the output shaft.

[0006] The details of one or more embodiments are set forth in the accompanying drawings and the description below. Other features and advantages will be apparent from the description, drawings, and claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] At least one example of the present disclosure will be described below in conjunction with the following drawings:

[0008] Figure 1 Includes a removable header, feed housing and a reverse worm drive (in Figures 2 to 8 , Fig.11 and Fig.12 A side view of a combine harvester having a feeder housing gearbox as shown, as illustrated according to an example of the present disclosure;

[0009] Figure 2 If further included in Figure 1 Schematic diagram of a header, a feeder house, a feeder house gearbox, and various components for supporting the functions of the feeder house gearbox in an exemplary combine harvester shown in ;

[0010] Figure 3 and Figure 4 are front and rear isometric views, respectively, of a feed chamber gearbox as illustrated according to an exemplary embodiment of the present disclosure;

[0011] Figures 5 to 7 is depicted as in various stages of assembly to reveal the reverse worm drive, main (planetary) gear train, hydraulically actuated selector mechanism and other components inside the gearbox housing Figures 2 to 4 An isometric view of an exemplary feed chamber gearbox shown in;

[0012] Figure 8is an isometric view of a reverse worm drive, main (planetary) gear train, hydraulically actuated selector mechanism, and carrier driven gear rotor usefully included in an exemplary feed chamber gearbox;

[0013] Fig. 9 is an isometric cross-sectional view of a hydraulic actuator suitably included in a selector mechanism (partially shown) of a feed chamber gearbox in an embodiment;

[0014] Fig.10 is a front view of an indexing ring assembly further suitably included in a selector mechanism (partially shown) of a feed housing gear box in an embodiment; and

[0015] Fig.11 and Fig.12 are cross-sectional views of an exemplary feed housing gearbox depicted in forward and reverse drive modes, respectively, and including dashed lines illustrating power transfer through the feed housing gearbox.

[0016] In the various drawings, similar reference numerals indicate similar elements. For simplicity and clarity of illustration, descriptions and details of well-known features and technologies may be omitted to avoid unnecessarily obscuring the exemplary and non-limiting embodiments of the present invention described in the subsequent detailed description. It should be further understood that unless otherwise specified, the features or elements appearing in the drawings are not necessarily drawn to scale. DETAILED DESCRIPTION

[0017] Embodiments of the present disclosure are illustrated in the accompanying drawings of the drawings briefly described above. Various modifications to the exemplary 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.

[0018] Overview

[0019] As mentioned above, the combine harvester feeder house is usually equipped with a modular gearbox capable of operating in forward and reverse drive modes. When placed in the reverse drive mode, the feeder house gearbox facilitates driving the feeder house and header in the reverse direction, for example, helping to clear a jam that interferes with the correct uptake of crops into the harvester. Various feeder house gearbox designs are conventionally known and commercially available. By way of example, a known feeder house gearbox design is characterized by a dual planetary gear train or system, which is used to shift between the forward drive mode and the reverse drive mode according to commands received via an operator input control member. Specifically, a selector mechanism located in the gearbox housing can be used to change whether a first rotatable member (e.g., a sun gear) or a second rotatable member (e.g., a ring gear) of the dual planetary system is used as a mechanical output of the system at a given point in time. When the sun gear and the ring gear rotate in opposite directions, in response to a control command provided by an operator of the combine harvester, the rotation direction of the feeder house gearbox output (e.g., an output shaft) can be changed by positioning the selector mechanism. Thus, such a design allows the feeder housing gearbox to switch freely between forward drive mode and reverse drive mode while the single mechanical input of the feeder housing gearbox is driven in a particular rotational direction by the engine of the combine harvester. Further description of a feeder housing gearbox housing such a double planetary gear train can be found in the following reference: U.S. Patent No. 6,722,112 B2, entitled "REVERSER CONTROL FOR COMBINE HARVER" and issued by the United States Patent and Trademark Office (USPTO) on April 20, 2004.

[0020] The feed chamber gearbox and other conventional feed chamber gearboxes that house a dual planetary gear system are able to operate reliably over extended periods of time while providing reverse functionality in the manner previously described. Nevertheless, conventional feed chamber gearboxes are still limited in certain aspects. For example, in the case of many conventional feed chamber gearboxes, mechanical constraints exclude high-speed switching between forward and reverse drive modes. Therefore, when switching from forward drive mode to reverse drive mode, it may be necessary to slow down (if not completely stop) the rotation of the mechanical input of the feed chamber gearbox, and vice versa. Therefore, when switching between forward drive mode and reverse drive mode, significant delays or "dead time" may occur, and the gearbox is generally not able to oscillate quickly between the forward and reverse drives of the driven components of the feed chamber and the header. When the gearbox is operated in reverse mode, this may reduce the efficiency of the feed chamber gearbox in clearing the blockage in the crop intake, resulting in increased harvester downtime. Conventional feed chamber gearboxes are also limited in other aspects. For example, existing feed room gearboxes may rely on relatively complex electrical feedback systems to ensure proper angular alignment between rotating components when switching between forward drive mode and reverse drive mode. Not only does this further contribute to delays in mode switching, but such electrical feedback systems introduce additional complexity, part count, and manufacturing cost to the gearbox. Another disadvantage is that conventional feed room gearboxes typically provide limited operator control over speed changes when the feed room gearbox is placed in the reverse drive mode.

[0021] Therefore, there is a continuous industrial demand for a feed chamber gearbox that can overcome the defects described above and enable rapid switching between forward drive mode and reverse drive mode. In order to meet this demand, a feed chamber gearbox that can rapidly switch between forward drive mode and reverse drive mode while reducing complexity, manufacturing cost and number of parts is provided below. In addition, the embodiments of the feed chamber described below can allow enhanced control of the rotation speed of the feed chamber gearbox when operating in reverse drive mode. Generally, such benefits are achieved by combining a unique reverse worm drive and a main (e.g., planetary) gear train architecture, such as with other components (e.g., rapid switching indexing ring and associated shifter or selector mechanism), enabling efficient switching between forward drive mode and reverse drive mode. In addition, in various embodiments, a dedicated motor (in this article, "reverse motor") can be utilized to drive the reverse worm drive to allow the operator to rapidly engage the reverse worm drive while further providing greater speed control in the reverse drive mode. In embodiments where the reverse motor takes the form of a hydraulic motor, the ability to quickly switch between speeds and possible directions of rotation in the reverse drive mode can be further enhanced, and the hydraulic motor can be driven using a proportional control valve scheme. In addition, the reverse worm drive can be selected to provide a relatively high mechanical speed reduction (e.g., a speed reduction that exceeds the speed reduction provided by the main gear train) to minimize the size of the reverse motor while meeting torque requirements. Still other benefits provided by embodiments of the feed chamber gearbox can include an improved lubrication scheme, which includes, for example, a bracket-driven gear rotor further contained within the gearbox housing. The end result is a structurally robust, relatively low-parts feed chamber gearbox that is capable of providing optimized reverse functionality to improve the efficiency of the gearbox in assisting in removing blockages or obstructions in the crop flow, as such blockages can occur during continued combine harvester operation.

[0022] Now combine Figures 1 to 12 , sets forth additional description of an exemplary feeder housing gearbox housing a reverse worm drive. Although the exemplary feeder housing gearbox is described in the context of a particular type of combine harvester, such as in Figure 1 and Figure 2 Schematically shown in FIG, but it will be appreciated that embodiments of the feeder housing gearbox may be utilized on various other types of combine harvesters, with the combine harvester described below being merely one suitable example. Furthermore, the term "combine harvester" as it appears herein is defined to encompass any agricultural machine utilized in the harvesting of crops and including a feeder housing to which a header (or other crop ingestion device) may be attached, wherein the feeder housing and / or header houses at least one component driven by a feeder housing gearbox.

[0023] Exemplary combine harvester and feeder housing gearbox housing a reverse worm drive

[0024] Figure 1 and Figure 2 The forward portion of a combine harvester 20 is schematically depicted, and the combine harvester 20 includes a feeder housing 22, a feeder housing gearbox 24 ( Figure 2 ) is mounted to the feed house 22, as illustrated in accordance with an exemplary embodiment of the present disclosure. An exemplary header 26 is attached to the front end of the feed house gearbox 24 for crop ingestion purposes. The header 26 can be removed from the feed house gearbox 24, and more generally, can be removed from the combine harvester 20 and interchanged with various other types of headers as needed to harvest specific types of crops. In the illustrated example, the header 26 takes the form of a belt pickup header and includes a header chassis or frame 28. As seen in the fore-aft direction, the pick-up conveyor belt 30, the transfer conveyor belt 32 and the auger conveyor 34 are rotatably mounted to the header frame 28 in tandem. As shown in FIG. Figure 2 , the belts 30, 32 may extend around and be supported by a plurality of rollers 36, wherein selected rollers may be driven by one or more unillustrated motors further mounted to the header frame 28. In comparison, the auger 34 may be mounted to an auger shaft 38 that extends between opposing side walls of the header frame 28 and is driven by the feed house gearbox 24 during operation of the combine harvester 20. In the illustrated example, the auger shaft 38 is mechanically coupled to the feed house gearbox output via a pulley and shaft coupling 40. In other embodiments, the particular manner in which the auger 34 is coupled to the mechanical output of the feed house gearbox 24 may be different.

[0025] The feeder chamber 22 includes a box-like housing or frame 42 that may be open along opposite longitudinal ends to form a passage through which the harvested crops pass. The feeder chamber conveyor belt 44 is located within the feeder chamber frame 42 and is supported by a plurality of rollers 46 ( Figure 2 ) supported, one or more of the plurality of rollers may be driven by the feed chamber gearbox 24. Likewise, a variety of different mechanical couplings may be utilized to transfer rotation from the mechanical output of the feed chamber gearbox 24 to one or more driven rollers 46, as determined by the particular design of the feed chamber 22. Figure 1 and Figure 2In the example of the present invention, in particular, a second pulley and shaft coupling 48 is provided for this purpose and mechanically couples the output of the feed house gearbox 24 to a pulley disposed around the protruding end of one of the rollers 46. Although in the illustrated example, the auger 34 of the header 26 and the conveyor belt 44 of the feed house 22 are depicted as being driven by separate pulley pulleys and shaft couplings 40, 48, in other embodiments of the combine harvester 20, the driven components of the header 26 and the feed house 22 may be driven by the same coupling or linkage system. In general, however, the particular manner in which the driven components housed in the feed house 22 and / or header 26 are mechanically coupled to one or more outputs of the feed house gearbox 24 is not required and may vary between embodiments, as may the type of one or more components located in the feed house 22 and / or header 26 that are driven by the gearbox 24.

[0026] As just described, during operation of the combine harvester 20, certain driven components of the header 26 (e.g., the auger 34) and driven components of the feeder house 22 (e.g., the conveyor belt 44) are mechanically powered through the feeder house gearbox 24. The mechanical power input applied to the feeder house gearbox 24 to drive these components may be provided by a different engine or motor on the combine harvester 20. For example, and as Figure 2 As schematically indicated in , the feed house gearbox 24 can include a first mechanical input (herein, a "main drive input") mechanically coupled to a main engine 50 of the combine harvester 20 (e.g., an internal combustion engine of the harvester). Additionally, the feed house gearbox 24 can include a second mechanical input (herein, a "reverse drive input") mechanically coupled to a second motor or engine 52 (herein, a "reverse motor 52") that is separate and distinct from the main engine 50. The reverse motor 52 can be various types of smaller motors, including electric motors, pneumatic motors, and hydraulic motors, relative to the main engine 50 of the combine harvester 20. In the illustrated embodiment, and as shown in FIG. Figure 2 As indicated by the symbol 54 in the figure, the reversing motor 52 takes the form of a hydraulic motor and is therefore referred to as the "hydraulic reversing motor 52" below. The use of a hydraulic motor for the reversing motor 52 can provide certain benefits, especially when paired with a proportional valve control scheme that enables rapid control of the motor 52 and therefore the feed chamber gearbox 24 when operating in the reverse drive mode, as discussed further below.

[0027] When in the form of a hydraulic motor, the reversing motor 52 may be driven or powered using a hydraulic control system 56 that houses at least one proportional control valve 58 that regulates the flow of hydraulic fluid to the motor 52. In such an embodiment, the one or more proportional control valves 58 are connected via appropriate flow lines (e.g., Figure 2 6 (in general, represented by line 60 in FIG. 1 ) is fluidly coupled to the reversing motor 52. As is typical of such control systems, the hydraulic control system 56 may also include various other components 62, including valve actuators, pumps, reservoirs, filters, and the like. Additionally, and as shown in FIG. Figure 2 As indicated 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 feed chamber gearbox 24. The flow line(s) 64 may enable fluid control of a hydraulic actuator housed within a selector mechanism that is used to shift or switch the gearbox 24 between a forward drive mode and a reverse drive mode, as described below in conjunction with Figures 3 to 12 More fully described, with particular attention to Fig. 9 , Fig.11 and Fig.12 In other embodiments, the feed chamber gearbox 24 may be switched between two or more operating modes (the forward and reverse drive modes described below) utilizing a different type of selector mechanism (manual, electric, hydraulic, and / or pneumatic in nature), in which case the flow line(s) 64 may be omitted. Additionally, various other flow lines may be fluidly connected to the feed chamber gearbox 24, such as lubricant conduits, but for clarity purposes only, these are not described herein. Figure 2 However, the following is combined with Figure 3 and Figure 4 Examples of such lubricant flow lines are shown and described.

[0028] The operation of the hydraulic control system 56 is controlled via at least one controller that is placed in signal communication with the hydraulic control system 56 using any suitable mechanical, hydraulic, and / or electrical (wired or wireless) connection architecture. By way of example, and with continued reference to Figure 2, the operation of the hydraulic control system 56 can be controlled via an engine control unit (ECU) 66 on the combine harvester 20; for example, an appropriate control output of the ECU 66 can be electrically connected to one or more actuators that position (multiple) control valves 58 within the hydraulic control system 56, as indicated by the dashed line 68. The ECU 66 can also control various other functions of the main engine 50 and / or other devices on the harvester 20; however, this is auxiliary to the present disclosure. During operation, the ECU 66 can issue commands to the hydraulic control system 56 to selectively position the selector mechanism within the feed chamber gearbox 24 and control the reverse motor 52, as further described herein. The ECU 66 can issue such commands in response to operator inputs received via one or more operator input devices 70, 72 connected to the ECU 66 via signal lines 74, 76, respectively. As Figure 1 , the operator input devices 70, 72 can be located in the operator cabin or station 51 of the combine harvester 20 and manually controlled by the operator driving the combine harvester 20. The specific form adopted by (multiple) operator input devices 70, 72 will vary and can include physical and / or virtual (e.g., graphical user interface) forms. In the illustrated example, the operator input devices 70, 72 are generally depicted as including: a physical button input 72, which can be used to activate the reverse drive mode of the feeder housing gearbox 24; and a rotatable joystick or switch 70, which can be used to control the speed of the reverse motor 52 when the feeder housing gearbox 24 is placed in the reverse drive mode.

[0029] Depending on the particular mode in which the gearbox 24 is placed at a given point in time, one or more mechanical outputs of the feed chamber gearbox 24 may be selectively driven by the main engine 50 or the reverse motor 52. As described above, the feed chamber gearbox 24 includes a main drive input and a reverse drive input that are mechanically coupled in some manner to the main engine 50 and the reverse motor 52, respectively. In the illustrated embodiment, and by way of non-limiting example only, the main drive input of the feed chamber gearbox 24 takes the form of an outer pulley housing 78 that is rotatably coupled to and disposed about the stationary housing of the gearbox 24, as further described below. When in the form of such an outer pulley housing, the main drive input 78 (alternatively referred to as an "outer pulley housing 78") may be driven by at least one pulley 80 and a belt 82 ( Figure 2) is mechanically coupled to the output shaft of the main engine 50. Comparatively, the reverse drive input of the feed house gearbox 24 may take the form of a reverse input shaft 84 that protrudes at an angle from the side of the housing of the feed house gearbox 24. When the feed house gearbox 24 is mounted on the combine harvester 20, the reverse input shaft 84 is mechanically coupled to the unillustrated output of the reverse motor 52, either directly or indirectly through any number of intermediate motion-transmitting components.

[0030] As previously indicated, the feed house gearbox 24 is operable in at least two operating modes, as selected using the operator input devices 70, 72: a default or forward drive mode and a reverse drive mode. In the forward drive mode, the feed house gearbox 24 mechanically couples the combine harvester engine 50 to one or more mechanical outputs of the gearbox 24, and therefore to the feed house conveyor belt 44 and the driven components of the header 26 (e.g., the transfer auger 34), when present. Simultaneously, the feed house gearbox 24 mechanically disconnects the reverse motor 52 from the one or more mechanical outputs of the gearbox 24. In this manner, the feed house gearbox 24 is not manually operated by an operator seated at the operator station 51 ( Figure 1 ) when the operator drives the combine harvester 20 on the field, the main engine 50 can drive the feeder conveyor belt 44 and the transfer screw 34 in the forward direction. When driving the combine harvester 20 in this manner, and again briefly referring to Figure 1 , the crop plants are cut and brought into the mouth or forward opening of the header 26 via the pick-up conveyor belt 30. The cut crops are then delivered to the feed house 22 via the transfer conveyor belt 32 and the auger 34 in the header 26. Thereafter, the crops travel through the tubular frame 42 of the feed house 22 under the action of the feed house conveyor belt 44. Immediately behind the feed house 22, a rotary drum conveyor 86 then delivers the newly harvested crops to the threshing and separator section 88 for further processing by the harvester 20. The crop plants are threshed, separated and conveyed through further parts of the combine harvester 20 for further processing and cleaning. The grain or other crop material extracted from the harvested crop plants is then delivered to the storage (grain) box 90 for collection and temporary storage.

[0031] In the manner described above, when the harvester 20 is driven in the forward direction, the combine harvester 20 can collect the crop plants cut and ingested by the header 26 and the feeder 22. However, occasionally, it may be necessary to drive the feeder 22 and the header 26 in the reverse direction to, for example, help clear any blockage that may occur and interrupt the ingestion of crops into the harvester 20. Therefore, when such a need arises, the operator can use the control members 70, 72 to shift or switch the feeder gearbox 24 into the reverse drive mode; although in other embodiments, when the gearbox 24 is switched into the reverse drive mode, it is not excluded that a certain degree of automation can be applied. When switched into the reverse drive mode, the feeder gearbox 24 mechanically couples the reverse motor 52 to the mechanical output of the feeder gearbox, for example, the output shaft 104 described below, while disconnecting the combine harvester engine 50 from it; although the combine harvester engine 50 can continue to drive the rotation of the main drive input (e.g., the outer pulley housing 78) of the gearbox 24. In one control scheme, the feed chamber gearbox 24 is placed in the reverse drive mode via the delivery of an appropriate pressure signal to the feed chamber gearbox 24 through the flow line(s) 64, wherein the pressure signal then causes a selector mechanism within the feed chamber gearbox 24 to effect the desired change of mode. Likewise, such pressure signals may be controlled by the ECU 66 in response to operator input commands received via the operator input devices 70, 72; for example, the pressure within one or more of the flow lines 64 may be altered in a manner that causes a hydraulic actuator to select the desired operating mode of the feed chamber gearbox 24.

[0032] Notably, for reasons described below, the feeder housing gearbox 24 is capable of rapidly switching between forward drive mode and reverse drive mode. Additionally, when placed in the reverse drive mode, the mechanical output(s) of the feeder housing gearbox 24 are driven by the reverse drive motor 52, which may allow for highly responsive and possibly bi-directional speed variation of the mechanical output(s) of the gearbox 24 to optimize efficiency in loosening and removing crop jams. This may be particularly true when the reverse drive motor 52 is in the form of a hydraulic motor drive implemented using a proportional control valve system, such as Figure 2 Advantageously, providing the reverse drive motor 52 with such capabilities (e.g., the ability to quickly ramp up and down rotational speed and reverse the direction of rotation to allow for rapid oscillation) can improve the effectiveness and efficiency of resolving blockages in crop flow. This in turn can reduce downtime of the combine harvester 20 and improve the overall efficiency of the combine harvester 20 during use. This is highly desirable. Now, the following will be combined with Figures 3 to 12 One manner in which the feed housing gearbox 24 may be rapidly switched between forward and reverse drive operating modes and an exemplary internal gear architecture of the gearbox 24 is more fully described.

[0033] Go to Figure 3 and Figure 4 , an example of a feed chamber gearbox 24 is shown with the following reference numerals carried over from the previous figures: reference numeral "78" designates an outer pulley housing 78 that serves as the main mechanical input of the exemplary gearbox 24 in the illustrated embodiment, and reference numeral "84" designates an input shaft that serves as the reverse drive input of the gearbox 24. In addition to these components, the feed chamber gearbox 24 further includes a gearbox housing 92, 94 that houses a reverse worm drive, a main (e.g., planetary) gear train, a selector mechanism, and various other components, which are described below in conjunction with Figures 5 to 12 Detailed description and illustration of the invention. Note that the gearbox housing construction will vary between embodiments, in this example, the gearbox housings 92, 94 are assembled from two main components or mating parts: (i) a base housing member 92, and (ii) a housing cover member 94. The housing cover member 94 is nested within the outer pulley housing 78, which extends around or surrounds the cover member 94. However, the cover member 94 can be seen through a plurality of windows 98 provided in the pulley housing 78. The outer pulley housing 78 is rotatable relative to the gearbox housings 92, 94 about an output axis, which is located at a position 120° from the output axis. Figure 3 In contrast, the gearbox housings 92, 94 may be attached to the feeder housing frame 42 and when the feeder housing gearbox 24 is mounted on the combine harvester 20 ( Figure 1 and Figure 2 ) remains stationary relative to the feed chamber frame 42.

[0034] When the feeder housing gearbox 24 is mounted on the combine harvester 20, for example, with 82 ( Figure 2 ) is disposed about the outer periphery of the outer pulley housing 78 and is used to transfer rotation from the main engine 50 ( Figure 2 ) to the pulley housing 78. When so driven, the outer pulley housing 78 rotates about the output axis 100 at a relatively high speed ratio relative to the gearbox housings 92, 94. The feed chamber gearbox 24 acts as a mechanical speed reducer to convert this high speed rotation to a lower speed rotation at a higher torque, better suited for driving the feed chamber conveyor belt 44 ( Figure 1 and Figure 2 ) and the driven component of the header 26. In this regard, the rotation of the outer pulley housing 78 can be further transmitted to the inner hub member 96, which is disposed or nested in the housing cover 94 and Fig.11 and Fig.12 (described below). Figure 3As shown in FIG. 1 , the inner hub member 96 is rotationally attached to the outer pulley housing 78 by a plurality of bolts 102. Rotation is then transferred from the rotating inner hub member 96 to rotating members included in the main (planetary) gear train, such as a sun gear as described below.

[0035] Continue to refer Figure 3 and Figure 4 , the output shaft 104 is rotatably mounted to the gearbox housing 92, 94 for rotation about the output axis 100; for example, the output shaft 104 can be centrally mounted relative to the gearbox housing 92, 94 and have a longitudinal axis coaxial with the output axis 100, as shown. The output shaft 104 can take a variety of different forms, as long as at least one end portion of the output shaft 104 can be externally mechanically connected. In the illustrated embodiment, the output shaft 104 includes an end portion 106 with external splines, which protrudes from an opening in the gearbox housing 92, 94 for mechanical connection to a driven component of the feed chamber 22 and / or the header 26. In addition, and as Figure 4 As best shown in the drawings, the output shaft 104 may include an open end portion 108 with internal splines. The internally splined shaft end portion 108 may be accessed through an opening in a tubular boss 110 that protrudes from the base housing member 92. Because the output shaft 104 is a rigid body, the end portions 106, 108 will rotate together, so that provision is made for two connection points for ease of mechanical attachment, rather than providing any change in output speed. Thus, in various embodiments, one end of the output shaft 104 may be mechanically coupled to a driven feed chamber component (e.g., Figure 1 and Figure 2 4) and the other end of the output shaft is mechanically linked to a driven component of the header 26 (e.g., the auger 34). In alternative embodiments, both the driven component of the header 26 (if present) and the driven component of the feed chamber 24 may be mechanically linked to the same end portion of the output shaft 104, or alternatively, to another component that serves as a mechanical output of the feed chamber gearbox 24.

[0036] The support arm 114 extends from the gearbox housing 92, 94 proximate the reverse input shaft 84. When the feeder gearbox 24 is installed on the combine harvester 20, the support arm 114 can support the reverse motor 52 ( Figure 2 ) and / or a component used to mechanically connect the output of the reverse motor 52 to the outer (e.g., splined) end of the reverse input shaft 84. When the feeder gearbox 24 is installed on the combine harvester 20, a number of other mechanical and / or fluid connections can be made. For example, and as Figure 4As best shown in FIG. 1 , these connections may include fluid connections to lubricant ports 120, 122 via corresponding lubricant flow lines 116, 118. In one configuration, hydraulic port 120 may be used as an inlet port that is located within a pump (e.g., a gear rotor housed within a gearbox housing 92, 94; e.g., Figures 5 to 8 The feed chamber gearbox 24 is provided with a hydraulic control port 124 that can receive pressurized hydraulic fluid to enable a hydraulically actuated selector mechanism 126 (e.g., a hydraulic actuator 126) to be further disposed within the feed chamber gearbox 24. Figure 5 , Figure 6 , Figure 8 and Fig. 9 and described below).

[0037] Next go to Figures 5 to 8 , depicting the internal components of an exemplary feed chamber gearbox 24 in various ways, wherein the feed chamber gearbox 24 is Figures 5 to 7 1 and 12 are shown in various stages of assembly and wherein the gearbox housings 92, 94, the inner rotating hub member 96 and the outer pulley housing 78 are in Figure 8 Generally, in the illustrated example, the feed housing gearbox 24 can be described as including at least five internal subsystems or components: (i) a main gear train or drive 128; (ii) a reverse worm drive 130; (iii) an internal lubrication pump (here, a gear rotor 132); (iv) the previously mentioned selector mechanism 126, including, among other components, a hydraulic actuator 134; and (v) an indexing ring assembly 136. Each of these subsystems or components housed in the gearbox housings 92, 94 is described in turn below.

[0038] Reference is first made to the main gear train 128, which in the illustrated embodiment takes the form of a single planetary gear system, and is therefore referred to hereinafter as the "main planetary gear train 128," or more simply, the "planetary gear train 128." Despite the illustrated embodiment, the main gear train 128 need not be implemented as a single planetary gear system across all embodiments of the feed chamber gearbox 24, and may instead take a variety of other forms, so long as the main gear train 128 includes at least two meshing gears and provides a mechanical connection between the outer pulley housing 78 and the output shaft 104 of the feed chamber gearbox 24. In one embodiment, the main planetary gear train 128 includes a ring gear 138, a sun gear 140, and planet carrier assemblies 142, 144. The planet carrier assemblies 142, 144 in turn include a rotatable carrier 142 that supports a plurality of planet gears 144; for example, the carrier 142 may support three angularly spaced planet gears 144, which are rotated by Figure 6 and Figure 8 140 and 144. The pin 112 identified in FIG. 140 is rotatably mounted to the carrier 142. The planet gears 144 engage or mesh with both the inner tooth periphery of the ring gear 138 and the outer tooth periphery of the sun gear in a typical manner. In addition, the sun gear 140 and the ring gear 138 are arranged in a concentric relationship, wherein the ring gear 138 circumscribing the sun gear 140. In addition, in this example, the sun gear 140, the ring gear 138 and the planet carrier assemblies 142, 144 are coaxial with the output axis 100. The main planetary gear train 128 is also at least partially nested within the outer pulley housing 78 to give the feed chamber gearbox 24 a relatively compact form factor.

[0039] The ring gear 138 of the primary planetary gear train 128 is rotationally fixed relative to the gearbox housings 92, 94 and therefore does not rotate with the sun gear 140 and the planet carrier assemblies 142, 144 when the primary planetary gear train 128 is driven via the outer pulley housing 78 and the rotating inner hub member 96. Any suitable mechanical coupling or anti-rotation feature may be utilized 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 member 92 and the housing cover member 94, wherein rotation of the ring gear 138 is prevented by bolts, alignment pins, or other fasteners 146 (in the Figures 5 to 7 In this case, the fasteners 146 may extend through the ring gear 138, the base housing member 92, and the housing cover member 94 when the feed chamber gearbox 24 is assembled.

[0040] In contrast to the stationary annular gear 138, the sun gear 140 and the planet carrier assemblies 142, 144 rotate about the output axis 100 when the main planetary gear train 128 is driven through the outer pulley housing 78 and the inner hub member 96. The rotation of the sun gear 140, the planet carrier assemblies 142, 144, the inner hub member 96 and the output shaft 104 about the output axis 100 is facilitated by various rolling element (e.g., ball and roller) bearings 156 distributed throughout the feed chamber gearbox 24. Similarly, the rotation of the reverse input shaft 84 and the worm 158 described below included in the reverse worm drive 130 can be facilitated by any number of rolling element bearings. For example, as shown in FIG. Figure 5 As best shown in FIG. 1 , two ball bearings 160 may be mounted about the reverse input shaft 84 adjacent opposite ends of the worm 158 .

[0041] In addition to the worm 158 and the ball bearing 160, the reverse worm drive 130 further includes a worm wheel 162 positioned in meshing engagement with the worm 158, which is mounted in a rotationally fixed relationship to the reverse input shaft 84. The worm wheel 162 includes a spline portion 164 that is selectively rotationally coupled to and rotationally decoupled from the splined intermediate portion 148 of the output shaft 104 via the indexing ring 152 (included in the indexing ring assembly 136) and the splined selector collar 154 (included in the selector mechanism 126). The internally splined selector collar 154 is engaged by a selector fork 166, which can slide along a translation axis parallel to the output axis 100, as guided by a linear guide pin 168. Thus, the selector collar 154 can be moved between: (i) a first position (herein, the "forward drive position"), in which the selector collar 154 mechanically couples a first rotatable member included in the main gear train 128 (i.e., the carrier 142) to the indexing ring 152; and (ii) a second position (herein, the "reverse drive position"), in which the selector collar 154 mechanically couples a second rotatable member included in the reverse worm drive 130 (i.e., the worm gear 162) to the indexing ring 152. In the illustrated example, the movement of the internally splined selector collar 154 and the selector fork 166 is controlled via the hydraulic actuator 134. In alternative embodiments, different types of hydraulic, electric, or pneumatic actuators may be integrated into the feed chamber gearbox 24 and used to position the selector collar 154 and thereby select the operating mode of the feed chamber gearbox 24 as desired.

[0042] In the present example of the feed chamber gearbox 24, the movement of the internally splined selector collar 154 and the selector fork 166 is controlled via a hydraulic actuator 134 which forms part of the selector mechanism 126. The actuator 134 is described in more detail and is now also referred to. Fig. 9In one possible configuration, the hydraulic actuator 134 may include a hydraulically actuated piston 170, at least one mechanical spring 172, a hydraulic chamber 174, and a cap member 176. The spring 172 is disposed within the hydraulic chamber 174 and is seated against the cap member 176. The spring 172 is selected to exert a desired resilient biasing force on the hydraulically actuated piston 170, thereby causing the piston 170 to move to a position corresponding to the forward drive position of the selector collar 154 with internal splines. Thus, the hydraulically actuated piston 170 and the selector collar 154 may normally reside in the forward drive position, such that the feed chamber gearbox 24 operates in the forward drive mode by default, and switches to the reverse drive mode when the pressure within the hydraulic chamber 174 changes. In this regard, when the hydraulic pressure within the hydraulic chamber 174 increases due to the pressure through the hydraulic control port 124 ( Figure 4 ) when the pressure of the supplied hydraulic fluid changes appropriately, the hydraulic piston 170 slides along the translation axis (in the illustrated example parallel to the output axis 100) into a position corresponding to the reverse drive position of the selector collar 154; for example, Fig. 9 Likewise, such pressure changes can be controlled by the hydraulic control system 56 ( Figure 2 ) is achieved by positioning the valve element in response to operator commands received via the operator input devices 70, 72.

[0043] Now combine Figures 3 to 9 For reference Fig.10 , the exemplary indexing ring assembly 136 includes the previously mentioned splined indexing ring 152 and a plurality of spring biased pins 178. The caps of the spring biased pins 178 are biased against the inner peripheral cam surface 180 of the indexing ring 152. For example, as Fig.10 As best shown in the figure, the inner peripheral cam surface 180 of the indexing ring 152 may include a valley 182 into which the head of the spring biasing pin 178 engages. The opposite end of the spring biasing pin 178 can be received in the splined output shaft 104. Therefore, the pin 178 is biased to extend into the deepest recess of the valley 182 to urge the indexing ring 152 to a neutral rotational position relative to the output shaft 104. At the same time, the splined output shaft 104 includes an externally toothed peripheral portion (at Figure 7 183), wherein the teeth or projections are received in corresponding grooves defined by the inner peripheral cam surface 180 of the indexing ring 152. Figure 7As shown in , the protrusion of the toothed outer peripheral portion 183 of the output shaft 104 is given a width that is less than the width of the groove provided in the inner periphery of the index ring 152 to allow the index ring 152 to rotate relative to the output shaft 104 within a limited angular range in either rotational direction before the protrusion contacts the inner edge of the index ring 152 defining the inner peripheral cam surface 180. Thus, common rotation of the index ring 152 and the output shaft 104 about the output axis 100 in a common rotational direction is ensured while permitting initial limited angular movement of the index ring 152 relative to the output shaft 104 to accommodate slight angular misalignment between the ring 152 and the selector collar 154. Thus, such a structural configuration facilitates rapid switching of the feed housing gearbox 24 between forward and reverse drive modes without requiring any electrical feedback system.

[0044] Fig.11 and Fig.12 2 is a cross-sectional view of an exemplary feed chamber gearbox 24 shown in forward drive mode and reverse drive mode, respectively. Fig.11 , the feed housing gearbox 24 is shown in a forward drive mode, wherein the dashed line 184 represents the power flow transmission through the rotating components of the gearbox 24. Here, the internally splined selector collar 154 is positioned to mechanically couple the indexing ring 152 to the splined tubular extension 150 protruding from the body of the bracket 142 toward the ring 152. When the rotational input is applied to the pulley housing 78 by the action of the main engine 50 of the combine harvester 20 (at Fig.11 The inner hub member 96 rotates with the pulley housing 78 about the output axis 100 (indicated by arrow 186 in the figure). The sun gear 140, which is splined to the inner hub member 96, also rotates with the pulley housing 78 and the inner hub member 96.

[0045] The rotation of the sun gear 140 drives the rotation of the planetary gears 144 (and more generally, the planetary carrier assemblies 142, 144), again noting that the outer ring gear 138 is rotationally fixed to the gearbox housings 92, 94 and remains stationary. Fig.11144, rotation of the planet carrier assemblies 142, 144 is transmitted via the splined portion 150 of the carrier 142, through the splined selector collar 154, through the indexing ring 152, and to the splined intermediate portion 148 of the output shaft 104. When the feed house gearbox 24 is placed in the forward drive mode, the rotational output of the feed house gearbox 24 (indicated by arrow 188) is driven through the main drive input (here, the outer pulley housing 78) of the feed house gearbox 24. Typically, then, when the feed house gearbox 24 is installed on the combine harvester 20, rotation is transmitted from the sun gear 140, through the planet carrier assemblies 142, 144 and to the output shaft 104, the engine 50 drives the rotation of the main drive input of the gearbox 24 (here, the outer pulley housing 78 coupled to the sun gear 140 in a rotationally fixed relationship), and the selector mechanism 126 is in the main drive position.

[0046] When it is desired to shift the feed housing gearbox 24 into reverse drive mode, such as by switching the feed housing gearbox 24 into reverse drive mode via the operator input devices 70, 72 ( Figure 2 ) received by the operator, the hydraulic actuator 134 ( Fig. 9 ) is controlled by the hydraulic control system 56 ( Figure 2 As previously described, this pressure change within hydraulic chamber 174 causes hydraulic piston 170, selector fork 166 and selector collar 154 to translate into the reverse drive position; that is, slide to Fig.11 and Fig.12 , as indicated by arrow 190. In this manner, the selector mechanism 126 (which includes the hydraulic actuator 134 and the selector collar 154) is commanded from the primary drive position ( Fig.11 ) moves to the reverse drive position ( Fig.12 ). Substantially simultaneously, or following the movement of the selector mechanism 126 into the reverse drive position, the hydraulic control system 56 may also command the hydraulic control system 56 to circulate hydraulic fluid through the hydraulic reverse motor 52 to initiate rotation of the reverse input shaft 84 (if not already rotating) and thereby drive the output shaft 104 through the reverse worm drive 130. Specifically, and as Fig.12 When the feed housing gearbox 24 is operated in the reverse drive mode, the reverse motor 52 applies a rotational input to the reverse worm drive 130 via the reverse input shaft 84 , as represented by arrow 192 in FIG.

[0047] like Fig.12As further indicated by power flow line 196 in FIG. 1 , rotation is transferred through the worm 158 to the worm gear 162, from the splined portion 164 of the worm gear 162, through the selector collar 154 and indexing ring 152, and to the output shaft 104. Arrow 194 further represents the rotational output of the feeder housing gearbox 24 when operating in the reverse drive mode and driven by the hydraulic reverse motor 52. More generally, when the feeder housing gearbox 24 is installed on the combine harvester 20, rotation is transferred from the worm 158, through the worm gear 162, and to the output shaft 104, the reverse motor 52 drives rotation of the reverse drive input (here, the reverse input shaft 84), and the selector mechanism 126 is in the reverse drive position. Notably, when the feeder housing gearbox 24 is operated in the reverse drive mode, the outer pulley housing 78 can continue to rotate under the influence of the engine 50 of the harvester 20; however, the rotation of the outer pulley housing 78 and the corresponding rotation of the inner hub member 96, the sun gear 140 and the planet carrier assemblies 142, 144 are not transmitted to the output shaft 104 because, when in the reverse drive position, the shaft 104 is now rotationally decoupled from the splined tubular extension or portion 150 of the carrier 142 by the selector collar 154. More succinctly, when in the reverse drive position, the selector mechanism 126 rotationally couples the worm gear 162 to the output shaft 104 while rotationally decoupling the planet carrier assemblies 142, 144 therefrom. Conversely, when in the main drive position, the selector mechanism 126 rotationally couples the planet carrier assemblies 142, 144 to the output shaft 104 while rotationally decoupling the worm gear 162 therefrom.

[0048] In the manner described above, a fast switch between the forward drive mode and the reverse drive mode of the feed chamber gearbox 24 is achieved. Figure 2 The direction in which the input of the reverse worm drive 130 rotates can be rapidly changed or oscillated when driven by a reverse motor 52 shown in FIG. 1 . Specifically, the reverse motor 52 is driven by one or more proportional control valves 58 ( Figure 2 ) to control the reverse motor 52. Thus, when the feeder gearbox 24 is placed in reverse drive control, highly responsive bi-directional speed control is achieved to maximize the efficiency with which the gearbox 24 is able to remove blockages that interrupt crop flow during operation of the combine harvester 20. The operator of the combine harvester 20 can utilize an input device 70 (e.g., a joystick or a multi-position switch) to control the speed of the reverse motor 52 and thereby quickly clear any such blockage in most circumstances. As another option, the ECU 66 ( Figure 2) may store one or more pre-programmed clearing routines or schedules in computer readable memory. When executed via operator input controls 70, 72, the clearing routines may cause ECU 66 to command reverse motor 52 to quickly ramp up, ramp down, and reverse the speed of reverse motor 52, such as to be optimized to quickly clear a crop intake jam. In such an embodiment, the operator may utilize any suitable physical or virtual interface (e.g., Figure 2 ) to select a preprogrammed clearing routine for execution. As a more specific but non-limiting example, the ECU 66 may be operable in a rapid jam removal mode in which the ECU 66 commands the proportional control valve(s) 58 to repeatedly switch or oscillate between driving the output shaft of the reversing motor 52 in a first rotational direction and in a second rotational direction while the selector mechanism 126 resides in Fig.12 in the reverse drive position shown in .

[0049] In various embodiments, the reverse worm drive 130 is advantageously selected to provide a relatively large mechanical (rotational speed) reduction; for example, a rotational speed reduction that exceeds and may be at least twice the rotational speed reduction provided by the main planetary gear train 128. For example, in one embodiment, the reverse worm drive 130 may be selected to provide a speed reduction equal to or greater than about 8:1 to convert the low torque, high speed input provided by the reverse motor 52 into a high torque, low speed output that is optimized for driving the feeder housing 24 and / or header 26 in the reverse drive mode ( Figure 1 and 2 ). Comparatively, in embodiments, the rotational speed reduction provided by the primary planetary gear train 128 may be approximately 4:1. By selecting the reverse worm drive 130 to provide a large rotational speed reduction, particularly when in the form of a hydraulic motor, the size of the reverse motor 52 may be minimized. In other embodiments, the reverse worm drive 130 may provide a speed reduction that is less than or equal to the speed reduction provided by the primary planetary gear train 128.

[0050] By actively lubricating the internal components of the gearbox 24, particularly the rotating components associated with the main planetary gear train 128, reliable operation of the feed chamber gearbox 24 can be optimized. In this regard, and as previously indicated, embodiments of the feed chamber gearbox 24 further include an internal lubricant pump for drawing lubricant into the gearbox housing 92, 94 in the form of the gear rotor 132. By way of example, and again briefly referring to Figure 8, the gear rotor 132 may include an input gear 198 that protrudes from the gear rotor housing 200 and engages the toothed outer peripheral portion 202 of the bracket 142. A lubricant port 204 may be provided in the gear rotor housing 200 for receiving oil or another liquid lubricant. Such a structural configuration enables the rotor within the gear rotor housing 200 to be driven rotationally by the rotation of the bracket 142 and more generally by the rotation of the main planetary gear train 128. In addition, in at least some embodiments, the rotation of the planetary carrier assembly 142, 144 can be driven by the main engine 50 of the combine harvester 20, regardless of the specific mode in which the feed chamber gearbox 24 is placed. Therefore, in such an embodiment, the gear rotor 132 can also remain mechanically connected to the engine 50 and continuously driven by the engine 50 to ensure uninterrupted lubricant flow into the gearbox housing 92, 94. Therefore, low-friction rotation of the rotating components contained in the feed chamber gearbox 24 can be promoted to extend the overall service life of the gearbox 24.

[0051] Enumerated example of a feeder housing gearbox and a combine harvester equipped with the feeder housing gearbox

[0052] The following examples of feed house gearboxes and associated combine harvesters are further provided and numbered for ease of reference.

[0053] 1. A feeder housing gearbox for mounting on a combine harvester including an engine and a reverse motor is provided. In an embodiment, the feeder housing gearbox comprises: a gearbox housing; an output shaft, the output shaft being mounted to the gearbox housing for rotation about an output axis; a main drive input, the main drive input being rotatably mounted to the gearbox housing and mechanically connected to the engine when the feeder housing gearbox is mounted on the combine harvester; and a reverse drive input, the reverse drive input being rotatably mounted to the gearbox housing and mechanically connected to the reverse motor when the feeder housing gearbox is mounted on the combine harvester. A selector mechanism is disposed within the gearbox housing and is movable between a main drive position and a reverse drive position. When the selector mechanism is in the main drive position, a main gear train or drive transfers rotation from the main drive input to the output shaft, and when the selector mechanism is in the reverse drive position, a reverse worm drive transfers rotation from the reverse drive input to the output shaft.

[0054] 2. The feed chamber gearbox of example 1, wherein the main gear train provides a first speed reduction when transferring rotation from the main drive input to the output shaft, and the reverse worm drive provides a second speed reduction when transferring rotation from the reverse drive input to the output shaft, the second speed reduction being greater than the first speed reduction.

[0055] 3. A feed chamber gearbox according to example 1, wherein the main gear train comprises a planet carrier assembly having planetary gears supported by a carrier, the planet carrier assembly being further rotatable relative to the gearbox housing about the output axis.

[0056] 4. A feed chamber gearbox according to Example 3, wherein the main gear system further includes: (i) a sun gear, which engages the planetary gears and is rotatable around the output axis relative to the gearbox housing; and (ii) a ring gear, which surrounds the sun gear, engages the planetary gears and is rotationally fixed relative to the gearbox housing.

[0057] 5. A feed chamber gearbox according to Example 4, wherein, when the feed chamber gearbox is mounted on the combine harvester, rotation is transmitted from the sun gear to the planetary carrier assembly and to the output shaft, the engine drives the rotation of the main drive input, and the selector mechanism is in the main drive position.

[0058] 6. The feed chamber gearbox of example 4, further comprising a gear rotor within the gearbox housing and mechanically coupled to the planet carrier assembly. The gear rotor, when driven by rotation of the planet carrier assembly, causes lubricant flow into the gearbox housing.

[0059] 7. A feed chamber gearbox according to Example 4, wherein the main drive input portion includes an outer pulley housing, which is connected to the sun gear in a rotationally fixed relationship, and the main gear train is at least partially nested in the outer pulley housing.

[0060] 8. The feed house gearbox of example 3, wherein the reverse worm drive comprises: a worm; and a worm wheel, the worm wheel being engaged by the worm and rotatable about the output axis. When the feed house gearbox is mounted on the combine harvester, rotation is transmitted from the worm through the worm wheel and to the output shaft, the reverse motor drives rotation of the reverse drive input, and the selector mechanism is in the reverse drive position.

[0061] 9. A feed chamber gearbox according to example 8, wherein the reverse drive input comprises a shaft projecting from the gearbox housing and coupled to the worm in a rotationally fixed relationship.

[0062] 10. The feed chamber gearbox of example 1, wherein the selector mechanism comprises: an indexing ring coupled to the output shaft for common rotation therewith; and a selector collar engaging the indexing ring. The selector collar is slidable relative to the indexing ring between the following positions: (i) a first position, wherein the selector collar mechanically couples a first rotatable member included in the main gear train to the indexing ring; and (ii) a second position, wherein the selector collar mechanically couples a second rotatable member included in the reverse worm drive to the indexing ring.

[0063] 11. The feed chamber gearbox of example 10, wherein the first rotatable member and the second rotatable member comprise a carrier and a worm gear, respectively.

[0064] 12. A feeder housing gearbox for mounting on a combine harvester, the feeder housing gearbox comprising: a gearbox housing; an output shaft mounted to the gearbox housing for rotation about an output axis; and a planetary gear train contained in the gearbox housing. The planetary gear train further comprises: a ring gear coupled to the gearbox housing in a rotationally fixed relationship therewith; a sun gear within the gearbox housing, coaxial with the ring gear, and rotatable about the output axis; and a planet carrier assembly within the gearbox housing, coaxial with the ring gear and the sun gear, and rotatable about the output axis. The feeder housing gearbox further comprises a reverse worm drive having: a worm contained in the gearbox housing; and a worm wheel engaged by the worm and rotatable about the output axis. A selector mechanism is controllable to selectively (i) mechanically couple the planet carrier assembly to the output shaft when the feed chamber gearbox operates in a first mode and (ii) mechanically couple the worm gear to the output shaft when the feed chamber gearbox operates in a second mode.

[0065] 13. The feed chamber gearbox according to Example 12 further includes a gear rotor, which is within the gearbox housing and mechanically connected to the planetary carrier assembly, and the gear rotor is configured to be driven by the rotation of the planetary carrier assembly to promote lubricant flow into the gearbox housing.

[0066] 14. A feed chamber gearbox according to example 12, wherein the reverse worm drive provides a rotational speed reduction that is at least twice the rotational speed reduction provided by the planetary gear train.

[0067] 15. An embodiment of a combine harvester equipped with a feed chamber gearbox is further provided. In an embodiment, the combine harvester includes an engine, a reverse motor and a feed chamber gearbox. The feed chamber gearbox further includes: an output shaft, the output shaft being rotatably mounted to the gearbox housing; a main drive input, the main drive input being rotatably mounted to the gearbox housing and mechanically connected to the engine; a reverse drive input, the reverse drive input being rotatably mounted to the gearbox housing and mechanically connected to the reverse motor; a selector mechanism, the selector mechanism being within the gearbox housing and movable between a main drive position and a reverse drive position; a main gear train, when the selector mechanism is in the main drive position, the main gear train transfers rotation from the main drive input to the output shaft; and a reverse worm drive, when the selector mechanism is in the reverse drive position, the reverse worm drive transfers rotation from the reverse drive input to the output shaft.

[0068] in conclusion

[0069] Thus, a feed chamber gearbox capable of rapid switching between a forward drive mode and a reverse drive mode while having reduced complexity, manufacturing cost, and number of parts has been provided. An embodiment of the feed chamber gearbox includes a reverse worm drive and other components so that a dedicated motor (the "reverse motor" described above) is enabled to drive rotation of a gearbox output (e.g., a centrally mounted output shaft) when the feed chamber gearbox is operated in the reverse drive mode. Thus, better operator control of speed changes can be achieved when the feed chamber gearbox is operated in the reverse mode while a relatively large reduction in rotational speed (e.g., a reduction in rotational speed exceeding and possibly at least twice the reduction in rotational speed provided by the main gear train) can be provided by the reverse worm drive to minimize the size of the reverse motor. In addition, rapid switching between the forward drive mode and the reverse drive mode can be achieved using a selector mechanism that allows rapid switching between modes without requiring excessive slowing or rotational stopping of the main drive input of the feed chamber gearbox (e.g., the outer pulley housing in the above-described exemplary embodiment). Embodiments of the feed chamber gearbox may also include other unique and useful features, such as a gear rotor driven by a carrier of a planetary gear system that serves as the main (eg, planetary) gear train of the feed chamber gearbox.

[0070] Unless expressly stated otherwise, as used herein, the singular forms "a", "an" and "the" are intended to include the plural meaning. It will be further understood that the terms "comprises" and / or "comprising" when used in this specification specify the presence of stated features, integers, steps, operations, elements and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof.

[0071] The description of the present disclosure has been presented for the purpose of illustration and description, but is not intended to be exhaustive or limited to the disclosure of the disclosed form. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the present disclosure. The embodiments explicitly cited herein are selected and described to best explain the principles of the present disclosure and its practical application, and to enable other persons of ordinary skill in the art to understand the present disclosure and recognize many replacements, modifications and variations to the described (multiple) examples. Therefore, various embodiments and implementations other than those explicitly described are within the scope of the following claims.

Claims

1. A feeder housing gearbox, the feeder housing gearbox being used to be mounted on a combine harvester including an engine and a reverse motor, the feeder housing gearbox comprising: Gearbox housing; an output shaft mounted to the gearbox housing for rotation about an output axis; a main drive input rotatably mounted to the gearbox housing and mechanically linked to the engine when the feed house gearbox is installed on the combine harvester; a reverse drive input rotatably mounted to the gearbox housing and mechanically linked to the reverse motor when the feed house gearbox is installed on the combine harvester; a selector mechanism located within the gearbox housing and movable between a main drive position and a reverse drive position; a main gear train that transfers rotation from the main drive input to the output shaft when the selector mechanism is in the main drive position; and A reverse worm drive transfers rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position.

2. The feed chamber gearbox according to claim 1, wherein: The main gear train provides a first speed reduction when transferring rotation from the main drive input to the output shaft; and wherein the reverse worm drive provides a second speed reduction when transferring rotation from the reverse drive input to the output shaft, the second speed reduction being greater than the first speed reduction.

3. The feed chamber gearbox according to claim 1, wherein: The main gear train includes a planet carrier assembly including planet gears supported by a carrier, the planet carrier assembly being rotatable relative to the gearbox housing about the output axis.

4. The feed chamber gearbox according to claim 3, wherein: The main gear train further comprises: a sun gear engaging the planetary gears and rotatable relative to the gearbox housing about the output axis; and A ring gear surrounds the sun gear, engages the planet gears and is rotationally fixed relative to the gearbox housing.

5. The feed chamber gearbox according to claim 4, wherein: When the feed house gearbox is mounted on the combine harvester, rotation is transmitted from the sun gear, through the planet carrier assembly, and to the output shaft, the engine drives rotation of the main drive input, and the selector mechanism is in the main drive position.

6. The feed chamber gearbox according to claim 4, further comprising: A gear rotor is located within the gearbox housing and is mechanically coupled to the planet carrier assembly, the gear rotor facilitating lubricant flow into the gearbox housing when driven by rotation of the planet carrier assembly.

7. The feed chamber gearbox according to claim 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 being at least partially nested within the outer pulley housing.

8. The feed chamber gearbox according to claim 3, wherein: The reverse worm drive comprises: Worm; and a worm wheel engaged by the worm and rotatable about the output axis; Wherein, when the feed house gearbox is mounted on the combine harvester, rotation is transmitted from the worm, through the worm wheel, and to the output shaft, the reverse motor drives rotation of the reverse drive input, and the selector mechanism is in the reverse drive position.

9. The feed chamber gearbox according to claim 8, wherein: The back-drive input includes a shaft projecting from the gearbox housing and coupled to the worm in a rotationally fixed relationship.

10. The feed chamber gearbox according to claim 1, further comprising: an indexing ring coupled to the output shaft for common rotation therewith; Wherein, the selector mechanism further comprises a selector collar, the selector collar engaging the indexing ring and being slidable relative to the indexing ring between the following positions: a first position in which the selector collar mechanically couples a first rotatable member included in the main gear train to the indexing ring; and A second position in which the selector collar mechanically couples a second rotatable member included in the reverse worm drive to the indexing ring.

11. The feed chamber gearbox according to claim 10, wherein: The first rotatable member and the second rotatable member include a carrier and a worm gear, respectively.

12. A feeder housing gearbox for installation on a combine harvester, the feeder housing gearbox comprising: Gearbox housing; an output shaft mounted to the gearbox housing for rotation about an output axis; a planetary gear train housed in the gearbox housing, the planetary gear train comprising: a ring gear coupled to the gearbox housing in a rotationally fixed relationship thereto; a sun gear located within the gearbox housing, coaxial with the ring gear, and rotatable about the output axis; and a planet carrier assembly located within the gearbox housing, coaxial with the ring gear and the sun gear, and rotatable about the output axis; A reverse worm drive, the reverse worm drive comprising: a worm gear housed in the gearbox housing; and a worm gear engaged by the worm and rotatable about the output axis; and A selector mechanism is controllable to (i) selectively mechanically couple the planet carrier assembly to the output shaft when the feed chamber gearbox is operating in a first mode, and (ii) selectively mechanically couple the worm gear to the output shaft when the feed chamber gearbox is operating in a second mode.

13. The feed chamber gearbox according to claim 12, further comprising: A gear rotor is located within the gearbox housing and mechanically coupled to the planet carrier assembly, the gear rotor being configured to be driven by rotation of the planet carrier assembly to cause a flow of lubricant into the gearbox housing.

14. The feed chamber gearbox according to claim 12, wherein: The reverse worm drive provides a rotational speed reduction that is at least twice that provided by the planetary gear train.

15. A combine harvester comprising: engine; Reverse motor; and A feed chamber gear box, the feed chamber gear box comprising: Gearbox housing; an output shaft rotatably mounted to the gearbox housing; a main drive input rotatably mounted to the gearbox housing and mechanically linked to the engine; a reverse drive input rotatably mounted to the gearbox housing and mechanically linked to the reverse motor; a selector mechanism located within the gearbox housing and movable between a main drive position and a reverse drive position; a main gear train that transfers rotation from the main drive input to the output shaft when the selector mechanism is in the main drive position; and A reverse worm drive transfers rotation from the reverse drive input to the output shaft when the selector mechanism is in the reverse drive position.

16. The combine harvester according to claim 15, wherein: The reverse motor includes a hydraulic motor having a motor output shaft mechanically linked to the reverse worm drive.

17. The combine harvester according to claim 16, further comprising: Controller; and a proportional control valve operably coupled to the controller and hydraulically coupled to the hydraulic motor, the controller being operable in a mode in which, when the selector mechanism is in the reverse drive position, the controller commands the proportional control valve to repeatedly switch between driving the motor output shaft in a first rotational direction and driving the motor output shaft in a second rotational direction.

18. The combine harvester according to claim 16, wherein: The main gear train comprises: a planet carrier assembly including planetary gears supported by a carrier, the planet carrier assembly being rotatable relative to the gearbox housing about the output axis; a sun gear engaging the planetary gears and rotatable relative to the gearbox housing about the output axis; and A ring gear surrounds the sun gear, engages the planet gears and is rotationally fixed relative to the gearbox housing.

19. The combine harvester according to claim 18, wherein: The reverse worm drive comprises: a worm gear housed in the gearbox housing; and A worm gear is engaged by the worm and is rotatable about the output axis.

20. The combine harvester according to claim 19, wherein: When in the primary drive position, the selector mechanism rotationally couples the planet carrier assembly to the output shaft while rotationally decoupling the worm gear from the output shaft; and Wherein, when in the reverse drive position, the selector mechanism rotationally couples the worm gear to the output shaft while rotationally decoupling the planet carrier assembly from the output shaft.

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