System and method for self-propelled garden machines

Abstract

Systems and methods are described for providing motive force with respect to various devices using a self-engaging / disengaging transmission configuration. An autonomous state transmission (210) can include a transmission unit configured for autonomously engaging and disengaging power transfer from a driving input member (201) to a driven output member (202) without utilizing external gearing or additional mechanical feedback. Embodiments of the autonomous state transmission can utilize various roller clutch configurations in communication with an override control for disengaging the roller clutch (220). The override control (221) can implement various configurations of a slip mechanism to facilitate engaging and / or disengaging the roller clutch (220). According to some examples, an override force detection is made using motion of the driving input member (201) and / or driven output member (202) and provides an override control (221) to the autonomous state transmission (210). Embodiments of the autonomous state transmission (210) can operate bidirectionally to autonomously engage and disengage power transfer from a driving input to a driven output.

Description

TECHNICAL FIELD

[0001] The present invention relates generally to self-propelled garden machines, and more particularly to self-engagement / disengagement transmission technology in the context of self-propelled garden machines. BACKGROUND

[0002] Various forms of garden machines are commonly used to perform many routine tasks in everyday life. For example, personnel engaged in work and leisure-related tasks use garden machines such as lawn mowers, snow throwers, edgers, tillers, and the like on a daily basis. These garden machines typically include one or more motors (e.g., electric or internal combustion motors) of some form that output power via a shaft, which drive one or more implements configured for the relevant task. As examples, a lawn mower can drive an implement in the form of a grass-cutting blade operable to cut grass, a snow thrower can drive implements in the form of an auger operable to collect and pulverize snow and an impeller operable to propel snow, an edger can drive an implement in the form of an edging blade operable to cut grass and dig a trench in the soil, and a tiller can drive an implement in the form of a tine rotor operable to agitate the soil. Using such garden machines, the labor required of a user to perform the task manually can be significantly reduced. However, it is still often necessary for the user to provide motive force to the garden machine, such as by pushing and / or pulling the garden machine within or throughout the area in which the relevant task is performed.

[0003] Configurations of self-propelled garden machines have become prevalent in recent times. A self-propelled garden machine can, for example, utilize one or more motors (e.g., electric or internal combustion motors) that output power via a shaft to drive one or more wheels and / or other mobile members (e.g., tracks) to propel the garden machine during use. The motor(s) used to provide motive force to the self-propelled garden machine can be the same as or different from the motor(s) used to energize the implement(s). Whether utilizing a separate motor to provide motive force or sharing a motor between driving the implement(s) and providing motive force, a self-propelled garden machine can not only reduce the physical labor of a user to perform a task, but also the substantial effort required of a user to move the garden machine within or throughout the area in which the task is performed. However, implementing self-propelled operation of a garden machine is not without challenges and drawbacks.

[0004] The simplest power transmission systems implemented by self-propelled garden machines (e.g., those with direct drive, claw and spline, etc. configurations) generally prevent the motion operation of the garden machine from being over-speeded. For example, when the garden machine is self-propelled, it is generally prevented that the user manually pushes the garden machine at a rate faster than that provided by the self-propulsion implemented by the transmission system. Additionally, such simple transmission systems generally present problems with the movement of the garden machine when the motor is stopped and / or causes the garden machine to move in a direction opposite to the self-propulsion under power of the transmission system. For example, if the garden machine is to be pushed or pulled in such a state, the wheels can remain engaged with the motor when it is stopped, requiring the user to increase the motion force (e.g., to overcome the friction of the wheels on the ground and / or manually turn the motor).

[0005] More complex transmission systems have been implemented in self-propelled garden machines (e.g., those with clutch-based transmission mechanisms) in order to generally provide an improved user experience in the motion operation of the garden machine compared to the simple transmission system implementations. However, the cost of such complex transmission systems is generally that the configuration is less suitable for the environment in which the garden machine can be used or can not be ideal in it, and this does not provide a robust solution for solving many problems related to the movement of the garden machine.

[0006] As an example of a more complex transmission system implementation, U.S. Patent No. 10,524,417, entitled “Walk-Behind, Self-Propelled Machine” (hereinafter “Fan,” the disclosure of which is incorporated herein by reference), assigned to Fan et al., provides a clutch-based transmission mechanism for a lawn mower. The clutch-based transmission mechanism of Fan enables a user to manually push the lawn mower in a forward direction or pull the lawn mower in an opposite direction when the motor is deactivated and the self-propelled forward mode is exited, and likewise enables a user to manually push the lawn mower in a forward direction or pull the lawn mower in an opposite direction when the motor is deactivated and the self-propelled backward mode is exited. To provide this operability, the clutch-based transmission mechanism of Fan uses first and second drive gears (e.g., gears disposed on an output shaft of the clutch-based transmission) and corresponding first and second wheel gears (e.g., gears formed as part of a wheel assembly) to interface with driven wheels. Such an implementation relies on a combination of gears external to the clutch-based transmission mechanism itself and gears disposed at the wheels, thus being highly susceptible to damage and / or interference from lawn material (e.g., grass clippings, soil, stones, etc.) and not well suited for environments in which the lawn mower is used. Moreover, the implementation of the clutch-based transmission mechanism of Fan does not accommodate a user to overspeed the motion operation of the garden machine, thus providing a configuration in which the user is prevented from pushing / pulling the lawn mower at a rate faster than that provided by the self-propulsion when the motor is activated and either the self-propelled forward mode or the self-propelled backward mode is implemented. Similarly, the clutch-based transmission mechanism of Fan does not accommodate a user to push / pull the lawn mower in a direction opposite to that provided by the self-propulsion when the motor is activated and either the self-propelled forward mode or the self-propelled backward mode is implemented, thus the user must provide an increased motion force to overcome the motion force of the self-propulsion transmission system. SUMMARY

[0007] The present invention relates to systems and methods for providing motion with respect to various devices that use a self-engagement / disengagement transmission configuration. In accordance with embodiments of the present invention, implementations of autonomous state transmissions using a self-engagement / disengagement transmission configuration are provided to perform garden machine self-propulsion motion operations. For example, autonomous state transmissions implemented in accordance with the concepts of the present invention can be used in garden machines configured for various tasks to provide robust self-propulsion implementations of lawn mowers, snow blowers, turf edgers, tillers, spreaders, garden carts, etc.

[0008] For example, autonomous state transmissions of embodiments of the present disclosure can include a transmission unit configured to autonomously control a force transfer state (e.g., engagement and disengagement) with respect to power transmission from a drive input member (e.g., a shaft, gear, etc.) to a driven output member (e.g., a shaft, gear, etc.) without utilizing external gearing or additional mechanical feedback. For example, autonomous state transmissions implemented in accordance with aspects of the present disclosure rely solely on motion of the drive input member and / or the driven output member to control the force transfer state (e.g., engagement / disengagement of power transmission from the drive input member to the driven output member). According to some examples of autonomous state transmissions, motion of the drive input member and / or the driven output member performs an override force (e.g., a manual force sufficient to override a self-propelled motion operation, a manually pushing / pulling motion operation when a motor providing a motion force is deactivated, etc.) detection and provides override control of the autonomous state transmission. Accordingly, the complete mechanism of autonomous state transmissions of embodiments of the present disclosure can be fully contained within a single package or continuous housing (such as can only have the drive input member and the driven output member as external interfaces).

[0009] Embodiments of autonomous state transmissions can be bidirectional operating to autonomously engage and disengage power transmission members from a drive input member to a driven output member. For example, bidirectional autonomous state transmissions can operate to disengage (e.g., abort power transmission from the drive input to the driven output) from other engaged states (e.g., providing a forward self-propel or a rearward self-propel motion force) in response to an override force (e.g., over-speeding a motion operation) in a direction of motion and an override under-speed force (e.g., under-speeding a motion operation) opposite the direction of motion. As a particular example, bidirectional autonomous state transmissions of example embodiments are configured to transition from an engaged state to a disengaged state in response to a user pushing a walk-behind garden machine equipped with the bidirectional autonomous state transmission with sufficient force to override a self-propel motion operation (e.g., an override force) and manually push the garden machine at a faster rate than the self-propel provided by the bidirectional autonomous state transmission (e.g., over-speeding the bidirectional autonomous state transmission). Additionally, bidirectional autonomous state transmissions of this example embodiment are configured to transition from an engaged state to a disengaged state in response to a user pushing a walk-behind garden machine equipped with the bidirectional autonomous state transmission with sufficient force to override a self-propel motion operation to manually slow the movement of the garden machine at a slower rate than the self-propel provided by the bidirectional autonomous state transmission (or even in reverse) (e.g., under-speeding the bidirectional autonomous state transmission).

[0010] The self-engagement / disengagement transmission configuration of the autonomous status transmission can implement a clutch and associated override control. For example, embodiments of the autonomous status transmission can utilize various override control roller clutches in communication with disengaging the roller clutch. The override control of the above-described embodiments of the autonomous status transmission may, for example, implement a slip mechanism of various configurations to facilitate engagement / disengagement of the roller clutch (e.g., based on override forces from over- and / or under-speed, manual motion operation, etc.). The slip mechanism of the override control embodiments of the autonomous status transmission may, for example, be configured for a slip action in which the override control does not interfere with the engagement status of the clutch in normal motion operation. However, the slip mechanism of the override control embodiments can be configured to respond to an override force transmitted via the driven output member (e.g., over- and / or under-speed) for a non-slip action to provide feedback control regarding the disengagement status of the clutch.

[0011] The foregoing has outlined rather broadly the features and technical advantages of the present application so that it can be better understood in view of the following detailed description. Additional features and advantages of the application will be described hereinafter which form the subject of the claims of the application. Those skilled in the art will appreciate that the conception, upon which, the disclosure is based, can be readily utilized as the basis for the designing of other structures for carrying out the same purposes of the present application. It will be realized by those skilled in the art that such equivalent constructions do not depart from the spirit and scope of the application as set forth in the appended claims. The novel features which are believed to be characteristic of the application, both as to its organization and method of operation, together with further objects and advantages will be better understood from the following description when considered in connection with the accompanying drawings. It is to be expressly understood, however, that each of the drawings is provided for the purpose of illustration only and is not intended as a definition of the limits of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0012] For a more complete understanding of the present application, reference is now made to the following description taken in conjunction with the accompanying drawings in which:

[0013] FIG. 1A and FIG. 1B An example of a self-propelled garden machine is shown in which an autonomous status transmission of an embodiment of the present application is arranged;

[0014] FIG. 2A to FIG. 2J A number of different views of a first exemplary autonomous status transmission of an embodiment of the present application are shown;

[0015] FIG. 3A to FIG. 3F A number of different views of a second exemplary autonomous status transmission of an embodiment of the present application are shown; and

[0016] FIG. 4A to FIG. 4D A schematic diagram showing operation of a portion of a roller clutch mechanism utilized in accordance with an embodiment of the present application. DETAILED DESCRIPTION

[0017] Various configurations of self-propelled garden machines can be used to perform a variety of work or leisure related tasks. For example, garden machines such as lawn mowers, snow throwers, turf edgers, tillers, spreaders, garden carts, and the like can be provided with one or more motors (e.g., electric or internal combustion) and associated transmission systems (e.g., drive shafts, gears, clutches, axles, etc.) configured to effect self-propelled movement operation of the garden machine. For example, one or more motors of a self-propelled garden machine can drive one or more wheels and / or other mobile members (e.g., tracks) to reduce the amount of physical effort required by a user to move the garden machine, such as when operating the garden machine to perform a corresponding task.

[0018] Transmission system configurations of various garden machines can implement autonomous state transmissions in accordance with concepts of the present disclosure. According to embodiments of the present application, implementations of autonomous state transmissions include self-engaging / disengaging transmission configurations that effect self-propelled movement operation of the garden machine. For example, autonomous state transmissions of embodiments of the present application can include transmission units configured to autonomously engage and disengage power transmission from a driving input member (e.g., shaft, gear, etc.) to a driven output member (e.g., shaft, gear, etc.) without utilizing external gearing or additional mechanical feedback. For example, autonomous state transmission configurations of embodiments of the present application can be utilized to facilitate robust self-propelled implementation of garden machines, such as by providing transmission systems well suited for use in environments in which garden machines can be used, accommodating over-speed and / or under-speed of self-propelled movement operation, and the like.

[0019] FIG. 1A and FIG. 1B Examples of self-propelled garden machines in which autonomous state transmissions of embodiments of the present application are arranged are shown. In particular, FIG. 1A An example of a self-propelled garden machine implementation as 100A is shown, while FIG. 1B An example of a self-propelled garden machine implementation as a snow thrower 100B is shown. It should be appreciated that lawn mower 100A and snow thrower 100B are exemplary configurations in which autonomous state transmissions of self-propelled garden machines can be utilized, and are not intended to limit the applicability of autonomous state transmissions implemented in accordance with concepts herein.

[0020] FIG. 1A and FIG. 1BEach of the illustrated examples includes an autonomous state transmission 110 configured for driving the wheels 101 in accordance with the concepts of the present disclosure, embodiments of which are further described below. The autonomous state transmission 110 can be driven, for example, by a motor arranged for supplying motive power to the self-propelled garden machine. According to alternative embodiments, the autonomous state transmission 110 can be driven by a motor arranged for driving an implement of the self-propelled garden machine.

[0021] FIG. 1A And FIG. 1B The complete mechanism of the autonomous state transmission 110 of the embodiments of

[0022] FIG. 2A to FIG. 2J And FIG. 3A to FIG. 3F Details regarding exemplary implementations of autonomous state transmissions in accordance with the concepts of the present disclosure are illustrated. FIG. 2A to FIG. 2J The autonomous state transmission 210 of FIG. 3A to FIG. 3F The autonomous state transmission 310 of FIG. 1A And / or FIG. 1B The configuration of the autonomous state transmission 110 of

[0023] Referring first to FIG. 2A to FIG. 2J An illustrated embodiment of the autonomous state transmission 210 will be described to aid in the understanding of the concepts of the present disclosure. It should be understood that while particular configurations of the autonomous state transmission 210 are illustrated and described, numerous changes, substitutions and modifications can be made to one or more components of the illustrated example of the autonomous state transmission 210 without departing from the spirit and scope of the present disclosure.

[0024] As FIG. 2AThe autonomous state transmission 210 is shown to include a drive input member (shown as a drive shaft 201) and a driven output member (shown as a driven shaft 202). Motion power to the drive input member can be provided by one or more motors of the self-propelled grounds maintenance machine relative to the grounds maintenance machine. The autonomous state transmission 210 autonomously engages and disengages power transmission from the drive shaft 201 to the driven shaft 202. The driven shaft 202 can be in communication with one or more motion members (e.g., wheels, tracks, etc.) of the self-propelled grounds maintenance machine to facilitate self-propelled motion operation of the grounds maintenance machine. It should be appreciated that the drive shaft 201 and / or the driven shaft 202 of embodiments of the autonomous state transmission 210 can be configured differently than shown, such as to provide an input gear and / or an output gear, a universal joint, etc.

[0025] FIG. 2A The autonomous state transmission 210 of the illustrated embodiment is arranged in a configuration in which its external interfaces include only the drive input member (drive shaft 201) and the driven output member (driven shaft 202), with the remainder of the autonomous state transmission 210 arranged within an enclosure or housing formed by mating housings 211 and 212. Accordingly, motion of the drive shaft 201 (e.g., drive input) and / or the driven shaft 202 (e.g., driven output) of the autonomous state transmission 210 is utilized for override force (e.g., manual force sufficient to override self-propelled motion operation of the grounds maintenance machine) detection and to provide override control of the force transmission state of the autonomous state transmission 210.

[0026] FIG. 2B and FIG. 2C The autonomous state transmission 210 is shown with its mating housings 211 and 212 and corresponding input and output bearings removed to thereby expose its internal components. The autonomous state transmission 210 implements a clutch and associated override control configuration. Accordingly, the illustrated embodiment of the autonomous state transmission 210 includes a clutch assembly 220 configured for selectively transmitting motion force provided via the drive shaft 201 to the driven shaft 202. The illustrated embodiment of the autonomous state transmission 210 further includes an override force feedback assembly 230 (including gears 231-234 and shaft 235) configured for selectively communicating override force provided via the driven shaft 202 to the clutch assembly 220 to thereby facilitate override control of the autonomous state transmission 210.

[0027] The clutch assembly 220 of embodiments of the autonomous state transmission 210 includes a roller clutch configuration in communication with the override force feedback assembly 230 to thereby facilitate control to disengage the roller clutch. As shown, the roller clutch assembly 220 includes a roller 221 and a roller cage 222. The roller 221 is configured to be selectively engaged by the roller cage 222 to thereby transmit motion force provided via the drive shaft 201 to the driven shaft 202. The roller cage 222 is configured to be selectively disengaged from the roller 221 to thereby disengage the roller clutch assembly 220 and prevent transmission of motion force provided via the drive shaft 201 to the driven shaft 202. FIG. 2DAs shown, the exemplary roller clutch configuration of clutch assembly 220 includes an inner ring 225 coupled to drive shaft 201 and an outer ring 227 coupled to driven shaft 202. Inner ring 225 is preferably coupled to drive shaft 201 such that rotation of the drive shaft is transmitted to inner ring 225 without substantially sliding the inner ring relative to drive shaft 201. In contrast, overrunning interface 221 is preferably disposed in sliding relationship with drive shaft 201 such that rotation of drive shaft 201 permits at least some rotational sliding of overrunning interface 221.

[0028] In FIG. 2D In the roller clutch configuration of clutch assembly 220, inner ring 225 is nested within the circumference of inner surface 228 of outer ring 227. Inner ring 225 includes an eccentric outer surface that includes roller surfaces 226a-226f, with vertices disposed at junctions of the roller surfaces (e.g., vertices at the junction of roller surfaces 226a and 226b, vertices at the junction of roller surfaces 226b and 226c, etc.) arranged closer to inner surface 228 of outer ring 227 than the rest of the roller surfaces. Rolling members 224a-224f (e.g., cylindrical pins) of clutch assembly 220 are arranged in the regions between a corresponding one of roller surfaces 226a-226f and the opposing surface of inner surface 228. The space or gap between the vertices of roller surfaces 226a-226f and inner surface 228 is preferably less than the diameter of rolling members 224a-224f. Roller surfaces 226a-226f of inner ring 225, rolling members 224a-224f, and inner surface 228 of outer ring 227 of embodiments cooperate to achieve the engaged and disengaged modes of clutch assembly 220.

[0029] FIG. 4A to FIG. 4D The cooperative interaction of the roller surfaces of the inner ring, the rolling members, and the inner surface of the outer ring of the exemplary roller clutch configuration is illustrated. Inner ring 425 can correspond, for example, to inner ring 225 of clutch assembly 220 described above and inner ring 325 of clutch assembly 320 described below, with roller surfaces 426 representing any of the roller surfaces thereof. Similarly, rolling members 424 can represent any of the rolling members of clutch assemblies 220 and 320. Outer ring 427 having inner surface 428 can correspond to outer ring 227 having inner surface 228 and outer ring 327 having inner surface 328. As with embodiments of clutch assemblies 220 and 320, inner ring 425 can be coupled to a drive input member (e.g., a drive shaft in communication with a motor, a gear, etc.) and outer ring 427 can be coupled to a driven output member (e.g., a driven shaft in communication with a moving member, a gear, etc.).

[0030] FIG. 4AThe disengaged mode of operation is shown with respect to the illustrated roller clutch configuration. For example, when the drive input member and the driven output member are at rest (e.g., the motor powering the drive input member is deactivated and the lawn care machine in which the roller clutch configuration is disposed is not being manually moved), the rolling member 424 can rest at the roller surface 426 (e.g., the rolling member’s neutral or disengaged position), at which time the area between the inner surface 428 and the roller surface 426 is maximized. Accordingly, the rolling member 424 is not in simultaneous and / or firm contact with both the roller surface 426 and the inner surface 428, and the roller clutch is disengaged. In the disengaged mode, the outer ring 427 and the inner ring 425 are free to move relative to one another (e.g., one ring can rotate while the other ring remains stationary, one ring can rotate at a different speed than the other ring, etc.). For example, as shown in the disengaged mode of operation of FIG. 5, the rolling member 424 is free to roll in the area between the roller surface 426 and the inner surface 428 of the opposing surface (e.g., the rolling member 424 is in the disengaged position) if a force is applied that causes the outer ring 427 and the inner ring 425 to move relative to one another (e.g., the lawn care machine in which the roller clutch configuration is disposed is being manually moved by a user pushing the lawn care machine). FIG. 4B Accordingly, the rolling member 424 is not in simultaneous and / or firm contact with both the roller surface 426 and the inner surface 428, and the roller clutch is disengaged. In the disengaged mode, the outer ring 427 and the inner ring 425 are free to move relative to one another (e.g., one ring can rotate while the other ring remains stationary, one ring can rotate at a different speed than the other ring, etc.). For example, as shown in the disengaged mode of operation of FIG. 5, the rolling member 424 is free to roll in the area between the roller surface 426 and the inner surface 428 of the opposing surface (e.g., the rolling member 424 is in the disengaged position) if a force is applied that causes the outer ring 427 and the inner ring 425 to move relative to one another (e.g., the lawn care machine in which the roller clutch configuration is disposed is being manually moved by a user pushing the lawn care machine).

[0031] FIG. 4CAn engaged mode of the roller clutch configuration is shown. For example, when the drive input is driven (e.g., a motor powering the garden machine in which the roller clutch configuration is disposed exerts a force on the drive input) and the inner ring 425 is rotating (e.g., shown as clockwise), the rolling member 424 can be urged to move toward one end of the roller surface 426 (e.g., near the apex between the roller surface 426 of the inner ring 425 and the adjacent roller surface), at which point the area between the inner surface 428 and the roller surface 426 is maximized. Accordingly, the rolling member 424 becomes in simultaneous and firm contact with both the roller surface 426 and the inner surface 428 (e.g., pinched to prevent the rolling member 424 from rolling, thereby placing the rolling member 424 in an engaged position), and the roller clutch is engaged. In the engaged mode, the outer ring 427 and the inner ring 425 are no longer free to move relative to one another. By this operation, the roller clutch configuration in the engaged mode can transfer a motive force between the drive input and the driven output.

[0032] FIG. 4C The engaged mode roller clutch can become disengaged in various different ways. For example, the engaged roller clutch configuration can again become disengaged upon ceasing to exert a force on the inner ring 425 (e.g., terminating the motive force provided by the motor powering the garden machine in which the roller clutch configuration is disposed on the drive input). As another example, the engaged roller clutch configuration can become disengaged upon overrunning (e.g., providing sufficient overrunning force in the direction of motion of the garden machine in which the roller clutch configuration is disposed to overrunningly operate the garden machine). FIG. 4D The roller clutch configuration is shown disengaged due to overrunning, in which the overrunning force causes the outer ring 427 to rotate at a faster rate than the inner ring 425 for at least a short period of time (e.g., the cushioning operation of the present embodiments described in further detail below facilitates the outer ring rotating at a faster rate than the inner ring for a short period of time, after which the other rings and is the inner ring remain stationary relative to one another). By this overrunning force, the rolling member 424 is released from its simultaneous and / or firm contact with both the roller surface 426 and the inner surface 428. Accordingly, the rolling member 424 can shift to a central region of the roller surface 426 (e.g., away from the apex between the roller surface 426 of the inner ring 425 and the adjacent roller surface), thereby becoming disengaged, and no longer transfer a motive force between the drive input and the driven output.

[0033] Referring again to FIG. 2DThe rollerized configuration of clutch assembly 220 is engaged to transfer the motion force provided via drive shaft 201 to driven shaft 202 when one or more of rolling members 224a-224f is simultaneously and securely in contact with its corresponding inner ring 225 rollerized surface and outer ring 227 inner surface 228 (e.g., pinched to prevent it from rolling). Correspondingly, when driven shaft 202 is rotated clockwise or counterclockwise, inner ring 225 is correspondingly rotated such that driven shaft 202 and inner ring 225 are rotated with sufficient speed and force to apply a centrifugal force sufficient to urge rolling members 224a-224f toward the respective apexes of the rollers and into engagement with inner surface 228 and captured in a non-rolling relationship between outer ring 227 and inner ring 225. Conversely, the rollerized configuration of clutch assembly 220 is disengaged to impede the transfer of motion force from drive shaft 201 to driven shaft 202 when rolling members 224a-224f are in a rolling relationship with their corresponding inner ring 225 rollerized surface and / or outer ring 227 inner surface 228 (e.g., rolling within the area between one of rollerized surfaces 226a-226f and inner surface 228).

[0034] FIG. 2D The exemplary rollerized clutch configuration of clutch assembly 220 illustrated includes an overcontrol interface 221 that operates in cooperation with over force feedback assembly 230 to disengage the rollerized clutch in response to an over force provided to clutch assembly 220 via driven shaft 202. Overcontrol interface 221 of the illustrated embodiment includes gear portion 222 and rolling member retainers 223a-223f. According to embodiments of clutch assembly 220, overcontrol interface 221 is arranged in a partially nested relationship with outer ring 227 and inner ring 225. The partially nested implementation of overcontrol interface 221 arranges rolling member retainers 223a-223f within the area between inner surface 228 and the opposing surfaces of rollerized surfaces 226a-226f, with rolling member retainers 223a-223f interleaved with rolling members 224a-224f. That is, in the partially nested implementation of embodiments, rolling member 224a is arranged between rolling member retainers 223a and 223b, rolling member 224b is arranged between rolling member retainers 223b and 223c, and so on including rolling member 224f arranged between rolling member retainers 223f and 223a.

[0035] In operation according to embodiments of the application, the scroll member retainers 223a-223f of the override control interface 221 can be used to cause or otherwise facilitate achieving engaged and / or disengaged positions of the scroll members 224a-224f. The scroll member retainers 223a-223f of embodiments can be controlled to facilitate achieving engaged and / or disengaged positions relative to the scroll members 224a-224f via transmission of forces through the gear portion 222 by the override force feedback assembly 230. For example, an override force provided to the driven shaft 202 can be transmitted through the gear portion 222 by the override force feedback assembly 230 to the override control interface 221, which can cause the scroll member retainers 223a-223f to move relative to the scroll members 224a-224f and cause and / or hinder their engaged and / or disengaged positions. However, when no override force is provided to the driven shaft 202, the override force feedback assembly 230 is configured to enable the override control interface 221 to facilitate engagement and / or holding of the scroll members 224a-224f in engaged positions.

[0036] FIG. 2E Operation of the autonomous state transmission 210 is shown according to examples of the present disclosure when the clutch assembly 220 is in the engaged mode, with the direction of rotational forces of the various components indicated by the associated angular velocity vectors. The numbers provided in association with the shown angular vectors designate the order in which the gear components of the example autonomous state transmission transmit forces. FIG. 2E

[0037] FIG. 2E Examples of the autonomous state transmission 210 can correspond, for example, to situations in which the garden machine in which the autonomous state transmission 210 is arranged is operating in a self-propelled mode. While specific directions of input / output rotational forces are provided (e.g., indicated with clockwise and counterclockwise angular velocity vectors), the described operation applies to forward or reverse driving (but with the direction of the rotational forces reversed).

[0038] FIG. 2E The shown example illustrates operation in which a drive force is applied to the drive shaft 201 (e.g., a first clockwise input force), with the force transmitted through the clutch assembly 220 operating in the engaged mode to the driven shaft 202 to provide a drive force output (e.g., a second clockwise output force). As FIG. 2F ​As shown in the cross-sectional view of the clutch assembly 220, the rolling members 224a-224f can hit the rolling member holders 223a-223f of the override interface 221 when in their engaged position, where the rolling member holders 223a-223f operate to prevent the rolling members 224a-224f from moving from the engaged position to the disengaged position. In this case, the override interface 221 is caused to rotate according to the driving force applied to the driving shaft 201. Accordingly, the gear portion 222 of the override interface 221 transmits the force to the gear 234 of the override force feedback assembly 230 (e.g., causing a second counterclockwise force). In turn, the gear 234 transmits the force to the gear 233 of the override force feedback assembly 230 (e.g., causing a third clockwise force). Meanwhile, the gear 231 coupled to the driven shaft 202 is caused to rotate clockwise (e.g., a second clockwise output force) according to the driving force (e.g., a first clockwise input force) by the driving members 229a-229d of the outer ring 227 engaging the ends of the circumferential slots 239a-239d disposed in the gear 231 FIG. 2D ). Accordingly, the gear 231 transmits the force to the gear 232 of the override force feedback assembly 230 (e.g., causing a third counterclockwise force).

[0039] As can be seen in the illustration of FIG. 2E , when operating in the exemplary engaged mode, the gears 232 and 233 of the override force feedback assembly 230 rotate in opposite directions (e.g., gear 232 rotates in a counterclockwise direction while gear 233 rotates in a clockwise direction). Accordingly, the shaft 235 of the override force feedback assembly 230 preferably allows for at least some rotational slippage of the gears 232 and 233. According to some embodiments of the present application, the shaft 235 and the gear 233 interface via a slip mechanism, thereby facilitating limited slippage between the shaft 235 and the gear 233.

[0040] FIG. 2GAn exploded view of an embodiment including the removal of gear 233 from shaft 235 is shown, with a portion of the example slip mechanism being visible. In the example shown, shaft 235 includes tab elements 236a and 236b. For example, tab elements 236a and 236b can include spring-biased sliding members arranged within a hub of shaft 235. Accordingly, in addition to having an aperture for slidably receiving the body of shaft 235, gear 233 includes a contoured inner surface 237. Tab elements 236a and 236b engage contoured inner surface 237 to facilitate the slippage of rotation of gear 233 relative to shaft 235 when appropriate relative forces exist between the rotation of shaft 235 and gear 233. The embodiment of the slip mechanism described above is configured for slippage action in which overrunning does not interfere with the engagement state of the clutch in normal motoring operation. For example, the contoured depth of contoured inner surface 237, the extension and / or retraction length of tab elements 236a and 236b, and / or the spring-biasing force provided to tab elements 236a and 236b to urge their extension and protrusion from the hub 236 of the shaft can be configured to allow for the slippage of rotation of gear 233 relative to shaft 235 when the opposite direction of rotation associated with autonomous state transmission 210 when gear 232 and 233 are in the engaged mode of clutch assembly 220.

[0041] FIG. 2H An operation of autonomous state transmission 210 is shown according to examples of the present disclosure when clutch assembly 220 is in the disengaged mode, with the direction of rotational forces of the various components being indicated by the associated angular velocity vectors. As in the previous example, FIG. 2H The numbers provided in association with the angular vectors designate the order of force transmission of the gear components of the example autonomous state transmission.

[0042] FIG. 2HThe example could correspond, for instance, to a situation where a garden machine equipped with an autonomous state transmission 210 is manually propelled while the motor providing the motion force is deactivated. Although a specific direction of the rotational force (e.g., indicated by clockwise and counterclockwise angular velocity vectors) is provided (e.g., the pushing or pulling of the garden machine), the described operation applies to movement in either direction (but the direction of the rotational force is reversed). Additionally, the operational description of the example also applies to overspeed modes (e.g., where the user overspeeds the motion operation of the garden machine), but in this case, the clockwise and counterclockwise indications are relative rather than absolute. Accordingly, the illustrated configuration of the autonomous state transmission 210 provides a bidirectional autonomous state transmission configuration that can operate to disengage from other engaged states (e.g., providing forward or backward self-propelling motion forces) in response to both an overspeed force in the direction of motion (e.g., an overspeed force associated with overspeeding the motion operation) and an overspeed force in the opposite direction of motion (e.g., an underspeed force associated with underspeeding the motion operation). (e.g., terminating power transmission from the drive input to the driven output). Specifically, the bidirectional autonomous transmission 210 is configured to, in response to a user pushing a walk-behind garden machine equipped with the bidirectional autonomous transmission with sufficient force, manually push the garden machine with overdrive self-propelled motion operation (e.g., overdrive force) and at a rate faster than the self-propelled motion provided by the bidirectional autonomous transmission (e.g., causing the bidirectional autonomous transmission to overspeed), thereby changing from an engaged state to a disengaged state. Additionally, the bidirectional autonomous transmission 210 is configured to, in response to a user pushing a walk-behind garden machine equipped with the bidirectional autonomous transmission with sufficient force, push with overdrive self-propelled motion operation, thereby manually slowing down the movement of the garden machine at a rate slower than (or even the opposite of) the self-propelled motion provided by the bidirectional autonomous transmission (e.g., causing the bidirectional autonomous transmission to underspeed), thereby changing from an engaged state to a disengaged state.

[0043] FIG. 2H The example shown illustrates the following operation: applying a force (e.g., a first counterclockwise force) to the driven shaft 202 that is associated with a user manually pushing the garden machine or causing its self-propelled operation to overspeed. Before the aforementioned force is applied to the driven shaft 202, in the case where the clutch assembly 220 is operating in engaged mode, rotation of the shaft 202 can provide a corresponding rotation (e.g., a first counterclockwise force) to the gear 231 attached thereto, without initially causing rotation of the outer ring 227 of the clutch assembly 220. That is, the drive members 229a-229d of the outer ring 227 can be arranged to engage the circumferential slots 239a-239d arranged in the gear 231. FIG. 2D) until the drive members 229a-229d pass through the length of the circumferential slots 239a-239d and engage the second (opposite) end thereof. However, a force is transmitted by the gear 231 to the gear 232 (e.g., causing a second clockwise force) of the overrunning force feedback assembly 230. The gear 232 transmits the rotational force to the shaft 235 attached thereto.

[0044] As noted above, the shaft 235 of embodiments of the overrunning force feedback assembly 230 preferably permits rotational slippage of the gears 232 and 233 to at least some extent. For example, FIG. 2G The illustrated example provides a slippage mechanism to facilitate limited slippage between the shaft 235 and the gear 233. In the current example, the motor providing the motive force is deactivated so that rotational force cannot be transmitted through the gear portion 222 of the overrunning control interface 221 to the overrunning force feedback assembly 230. Similarly, when operating in the overrunning mode, the relative rotational force produces the same effect. Accordingly, in these situations, the gear 233 of the embodiment engages the shaft 235 in a non-slipping relationship so that the gear 232 transmits the rotational force to the gear 233 (e.g., causing a third clockwise force). That is, while the hub of the shaft 235 is configured to permit slippage of the gear 233 relative to the shaft 235 when the gears 232 and 233 rotate in opposite directions associated with the autonomous state transmission 210 when in the engaged mode of the clutch assembly 220, the hub is configured to engage the gear 233 without slippage relative to the rotation of the shaft 235 when the autonomous state transmission 210 receives an overrunning force via the shaft 202. Embodiments of the slippage mechanism described above are configured to perform a non-slipping action in response to an overrunning force (e.g., overrunning and / or under- running) transmitted via the shaft 202 to provide feedback control regarding the disengaged state of the clutch assembly 220. For example, the undulating depth of the undulating inner surface 237 FIG. 2G ), the extension and / or retraction length of the tab elements 236a and 236b FIG. 2G ), and / or the spring biasing force provided to the tab elements 236a and 236b to cause them to extend and protrude from the hub 236 of the shaft can be configured to permit the rotation of the gear 233 relative to the shaft 235 without slippage when there is an overrunning force with respect to the shaft 202 that is consistent with the operation of the clutch assembly 220 in the disengaged mode. In accordance with embodiments of the present application, one or more aspects of the slippage mechanism of the autonomous state transmission 210 are selected to perform a slipping action during self-propelled motion operation of the garden machine in which the autonomous state transmission is disposed, and a non-slipping action during overrunning and / or under- running of the motion operation of the garden machine.

[0045] In operation according to the illustrated example, force is transmitted by gear 233 to gear 234 of overrunning force feedback assembly 230 (e.g., resulting in a fourth counterclockwise force). Gear 234 interfaces with gear portion 222 of overrunning control interface 221, and thus transmits force (e.g., a fifth clockwise force) to overrunning control interface 221 of clutch assembly 220. Rotation of overrunning control interface 221 provides corresponding movement of its rolling member holders 223a-223f. As FIG. 2I illustrated, with clutch assembly 220 initially in the engaged mode (e.g., as FIG. 2F illustrated), rolling member holders 223a-223f can rotate (e.g., clockwise in this example) to move away from (e.g., rolling member holders 223a-223f can stop hitting) and cause or otherwise facilitate disengaged positioning of a corresponding one of rolling members 224a-224f.

[0046] According to embodiments of clutch assembly 220, with rolling member holders 223a-223f not in a position to cause engaged positioning of rolling members 224a-224f (e.g., rolling member holders 223a-223f do not hit rolling members 224a-224f to cause engaged positioning and / or rolling member holders 223a-223f hit rolling members 224a-224f in the opposite direction to cause disengaged positioning), rolling members can be released from simultaneous and / or firm contact with both corresponding rollerized surface 226a-226f and inner surface 228. For example, after gear 231 is sufficiently rotated to cause driving members 229a-229d of outer ring 227 to engage second ends of circumferential slots 239a-239d, outer ring 227 will be caused to rotate (e.g., a counterclockwise force). Thus, inner surface 228 can cause rolling members 224a-224f to rotate such that rolling members shift to central regions of their respective rollerized surfaces 226a-226f, as FIG. 2JThe sequence of force transmission and dampening implemented by the drive members 229a-229d disposed in the circumferential slots 239a-239d, for example, facilitates achieving a short time period in which, for example, in response to an overrunning force, the outer ring 227 rotates at a faster rate than the inner ring 225 while the drive members 229a-229d of the outer ring 227 pass through the circumferential slots 239a-239d disposed in the gear 231, and then the inner and outer rings again remain stationary relative to one another when the drive members 229a-229d engage the other end of the slots 23a-239d, facilitates achieving the disengaged mode of the clutch assembly 220, and avoids any premature engagement of the clutch assembly, in operation in accordance with the present application. Accordingly, the rolling members 224a-224f can be disposed in the disengaged position, and the clutch assembly 220 is disengaged. The rolling member retainers 223a-223f of the embodiments preferably maintain the relative positioning to facilitate the rolling members 224a-224f remaining in the disengaged position during the application of an overrunning force to the shaft 202.

[0047] Having described embodiments of the autonomous state transmission 210 in accordance with some examples of the present application, attention is now directed to FIG. 3A to FIG. 3F wherein an illustrated embodiment of the autonomous state transmission 310 will be described. It should be appreciated that while a particular configuration of the autonomous state transmission 310 is shown and described, numerous changes, substitutions, and modifications can be made in relation to one or more components of the example of the autonomous state transmission 310 without departing from the spirit and scope of the present application.

[0048] As FIG. 3A illustrated, the autonomous state transmission 310 includes a drive input member, shown as a drive shaft 301, and a driven output member, shown as a driven gear 302. The motion power of the drive input member can be provided relative to the garden machine by one or more motors of the self-propelled garden machine. The autonomous state transmission 310 autonomously engages and disengages the power transmission from the drive shaft 301 to the driven gear 302. The driven gear 302 can be in communication with one or more motion members of the self-propelled garden machine (e.g., wheels, tracks, etc.) to facilitate self-propelled motion operation of the garden machine. It should be appreciated that the drive shaft 301 and / or the driven gear 302 of the autonomous state transmission 310 can be configured differently than shown, such as to provide an input gear and / or an output gear, a universal joint, etc.

[0049] FIG. 3AThe autonomous state transmission 310 of the illustrated embodiment is configured in a configuration in which its external interfaces include only a drive input member (drive shaft 301) and a driven output member (driven gear 302), with the remainder of the autonomous state transmission 310 disposed within an enclosure or housing formed by the cover 311 and the outer ring 327. Accordingly, overrunning force (e.g., manual force sufficient to overtake the self-propelled motion operation of the grounds maintenance machine) detection and overrunning control of the force transmission state of the autonomous state transmission 310 is conducted with motion of the drive shaft 301 (e.g., drive input) and / or the driven gear 302 (e.g., driven output) of the autonomous state transmission 310.

[0050] FIGS. 3B and 3C illustrate the autonomous state transmission 310 in exploded view, with the cover 311 removed to thereby expose its internal components. The autonomous state transmission 310 implements a clutch and associated overrunning control configuration. Accordingly, the illustrated embodiment of the autonomous state transmission 310 includes a clutch assembly 320 including an overrunning control interface 321, rolling members 324a-324f, an inner ring 325, and an outer ring 327, configured to selectively transmit motion force provided via the drive shaft 301 to the driven gear 302. Accordingly, the illustrated embodiment of the autonomous state transmission 310 further includes an overrunning force feedback assembly 330 (including gears 331-333) configured to selectively communicate overrunning force provided via the driven shaft 302 to the clutch assembly 320, thereby facilitating overrunning control of the autonomous state transmission 310.

[0051] The illustrated embodiment of the clutch assembly 320 includes a roller clutch configuration in communication with the overrunning force feedback assembly 330, thereby facilitating control to disengage the roller clutch. The exemplary roller clutch configuration of the clutch assembly 320 includes the inner ring 325 coupled to the drive shaft 301 (e.g., via a double D-slit configuration to allow for some hysteresis in the movement of the inner ring 325 caused by the drive shaft 301) and the outer ring 327 coupled to the driven gear 302. The inner ring 325 is preferably coupled to the drive shaft 301 such that rotation of the drive shaft is transmitted to the inner ring 325. The overrunning control interface 321 is preferably configured in a slip-facilitating relationship with the drive shaft 301 such that rotation of the drive shaft 301 allows for at least some rotational slippage of the overrunning control interface 321.

[0052] Similar to the above FIG. 2DThe inner ring 325 of the roller clutch configuration of the clutch assembly 320 includes eccentric outer surfaces comprising roller surfaces 326a-326f, wherein the apexes disposed at the junctions of the roller surfaces are arranged closer to the inner surface 328 of the outer ring 327 than the rest of the roller surfaces. Rolling members 324a-324f (e.g., cylindrical pins) of the clutch assembly 320 are arranged in the regions between the corresponding one of the roller surfaces 326a-326f and the opposing surface of the inner surface 328. The space or gap between the apexes of the roller surfaces 326a-326f and the inner surface 328 is preferably less than the diameter of the rolling members 324a-324f. The roller surfaces 326a-326f of the inner ring 325, the rolling members 324a-324f, and the inner surface 328 of the outer ring 327 of the embodiment cooperate to achieve the engaged and disengaged modes of the clutch assembly 320. The cooperative interfacing of the roller surfaces 326a-326f of the inner ring 325, the rolling members 324a-324f, and the inner surface 328 of the outer ring 327 of the exemplary roller clutch configuration of the clutch assembly 320 can be seen in FIGS. 3A-3B, and described above with reference to FIGS. 1A-1B. FIG. 4A to FIG. 4D

[0053] The roller configuration of the clutch assembly 320 is engaged to transmit the motion force provided via the drive shaft 301 to the driven gear 302 when one or more of the rolling members 324a-324f are simultaneously and firmly in contact with their corresponding inner ring 325 roller surface and outer ring 327 inner surface 328 (e.g., pinched to prevent it from rolling). Accordingly, when the driven shaft 302 is turned clockwise or counterclockwise, the inner ring 325 can be correspondingly turned such that the driven shaft 302 and the inner ring 325 are turned with sufficient speed and force to apply a centrifugal force sufficient to urge the rolling members 324a-324f toward their corresponding apexes of the roller and into engagement with the inner surface 328 and captured in a non-rolling relationship between the outer ring 327 and the inner ring 325. Conversely, the roller configuration of the clutch assembly 320 is disengaged to impede the transmission of the motion force from the drive shaft 301 to the driven gear 302 when the rolling members 324a-324f are in a rolling relationship with their corresponding inner ring 325 roller surface and / or outer ring 327 inner surface 328 (e.g., rolling within the region between one of the roller surfaces 326a-326f and the inner surface 328).

[0054] ​The exemplary roller clutch configuration of clutch assembly 320 shown in FIGS. 3B and 3C includes an override control interface 321 that operates in cooperation with an override force feedback assembly 330 to cause the roller clutch to disengage in response to an override force provided to clutch assembly 320 via driven gear 302. Override control interface 321 of the illustrated embodiment includes a hub portion 322 and rolling member holders 323a-323f attached to or formed as part of hub portion 322. Depending on the embodiment of clutch assembly 320, override control interface 321 is arranged in a nested relationship with outer ring 327 and inner ring 225. The nested implementation of override control interface 321 arranges rolling member holders 323a-323f within the area between inner surface 328 and the opposing surfaces of roller surfaces 326a-326f, with rolling member holders 323a-323f interleaved with rolling members 324a-324f. That is, in the nested implementation embodiment, rolling member 324a is arranged between rolling member holders 323a and 323b, rolling member 324b is arranged between rolling member holders 323b and 323c, and so on including rolling member 324f arranged between rolling member holders 323f and 323a.

[0055] In operation according to embodiments of the present application, rolling member holders 323a-323f of override control interface 321 can be used to cause or otherwise facilitate achieving engaged and / or disengaged positions of rolling members 324a-324f. Rolling member holders 323a-323f of the embodiment can be controlled to facilitate achieving engaged and / or disengaged positions relative to rolling members 324a-324f via force transmitted through hub portion 322 by override force feedback assembly 330. For example, an override force provided to driven gear 302 can be transmitted through hub portion 322 to override control interface 321 by override force feedback assembly 330, which can cause rolling member holders 323a-323f to move relative to rolling members 324a-324f and cause and / or hinder their engaged and / or disengaged positions. However, when no override force is provided to driven gear 302, override force feedback assembly 330 is configured to enable override control interface 321 to facilitate rolling members 324a-324f engaging and / or remaining in engaged positions.

[0056] FIG. 3D Operation of autonomous state transmission 310 when clutch assembly 320 is in engaged mode is shown according to examples of the present disclosure, with the direction of rotational forces of individual components indicated by the associated angular velocity vectors. The angular vectors shown are associated with the sequence of force transmission by the gear components of the exemplary autonomous state transmission. FIG. 3D The numbers provided in association with the shown angular vectors designate the sequence of force transmission by the gear components of the exemplary autonomous state transmission.

[0057] FIG. 3D The example of FIG. 3B can correspond, for example, to a situation in which the lawn care machine in which the autonomous transmission 310 is disposed is operating in a self-propel mode. Although specific directions of input / output rotational forces are provided (e.g., indicated with clockwise and counterclockwise angular velocity vectors), the described operations apply to forward drive or reverse drive (but with the direction of rotational force reversed).

[0058] FIG. 3D The illustrated example shows the following operation: a drive force (e.g., a first clockwise input force) is applied to the drive shaft 301, which is transmitted through the clutch assembly 320 to the outer ring 327 and thus to the driven gear 302 in an engaged mode to provide a drive force output (e.g., a second clockwise force). Rotation of the outer ring 327 includes rotation of the ring gear 331 of the overrunning force feedback assembly 330 (e.g., a second clockwise force) defined within a portion of the outer ring 327. The gears 332a-332c of the overrunning force feedback assembly 330 are arranged as planetary gears within the ring gear 331 of the illustrated embodiment (e.g., arranged on pins affixed to or formed as part of the hub portion 322). Accordingly, rotation of the ring gear 331 (e.g., a second clockwise force) causes rotation of the gears 332a-332c (e.g., a third clockwise force). The gear 333 of the overrunning force feedback assembly 330 is arranged as a sun gear relative to the planetary gears 332a-332c of the illustrated embodiment. Thus, rotation of the gears 332a-332c (e.g., a third clockwise force) causes rotation of the gear 333 (e.g., a fourth counterclockwise force).

[0059] The overrunning control interface 321 is caused to rotate in accordance with the drive force applied to the drive shaft 301. For example, as shown in the exploded view of FIG. 3B, in which an embodiment is shown in which the overrunning control interface 321 is removed from the drive shaft 301, the overrunning control interface 321 is coupled to the drive shaft 301 via a double-D slot configuration, allowing a degree of hysteresis in movement of the overrunning control interface 321 relative to the drive shaft 301. Accordingly, the rolling member retainers 323a-323f are implemented to move at least to some degree relative to the rolling members 324a-324f. The rolling members 324a-324f of the clutch assembly 320, when in their engaged position, can impinge upon the rolling member retainers 323a-323f of the overrunning control interface 321, which operate to prevent movement of the rolling members 324a-324f from the engaged position to the disengaged position (e.g., similar to the operation of the rolling member retainers 323a-323f of the overrunning control interface 321 in the engaged position of the clutch assembly 320). FIG. 3E FIG. 2F ​The hub portion 322 of the override control interface 321 is correspondingly rotated (e.g., a second clockwise force) by the force (e.g., a first clockwise force) applied to the drive shaft 301 during continued engagement operation of the clutch assembly 320.

[0060] As can be seen in the illustration of FIG. 3D As can be seen in the illustration of

[0061] FIG. 3E A portion of an example slip mechanism is shown, which can be used with the override control interface 321 and the override force feedback assembly 330. In the illustrated example, the biasing elements 335a and 335b are provided with tab elements 336a and 336b, respectively. The gear 333 of the illustrated example is adapted to retain the biasing elements 335a and 335b to engage the hub portion 322. For example, the biasing elements 335a and 335b can include spring biasing members to place the tab elements 336a and 336b in communication with a surface of the hub portion 322. Accordingly, in addition to having an aperture for receiving the body of the shaft 301, the hub portion 322 includes a contoured outer surface 337. The tab elements 336a and 336b engage the contoured outer surface 337 to facilitate slippage of the hub portion 322, and in response to the rotation of the override control interface 321 relative to the gear 333, when appropriate relative forces exist between the rotation of the override control interface 321 and the gear 322. The above-described embodiment of the slip mechanism is configured to perform a slip action in which the override control does not interfere with the engagement state of the clutch during normal motoring operation. For example, the contoured depth of the contoured outer surface 337, the length of the tab elements 336a and 336b, and / or the spring biasing force provided by the biasing elements 335a and 335b can be configured to allow the rotation of the hub portion 322 relative to the shaft 333 to slip when the hub portion 322 and the gear 333 are rotated in opposite directions associated with the autonomous state transmission 310 when the clutch assembly 320 is in the engaged mode.

[0062] FIG. 3F An operation of the autonomous state transmission 310 when the clutch assembly 320 is in the disengaged mode is shown in accordance with examples of the present disclosure. As with the previous example,FIG. 3F The numbers provided in association with the angle vectors shown designate the order in which the gear components of the example autonomous state transmission transmit force.

[0063] FIG. 3F Examples of the above can correspond, for example, to situations in which the motor for providing motive force is deactivated, in which the lawn care machine in which the autonomous state transmission 310 is disposed is being manually pushed. While the specific direction of rotational force (e.g., indicated with clockwise and counterclockwise angular velocity vectors) is provided (e.g., pushing or pulling of the lawn care machine), the described operation applies to movement in either direction (but with the direction of rotational force reversed). Additionally, the operation description of the example also applies to an over-speed mode (e.g., in the event that a user over-speeds the motive operation of the lawn care machine), but in that case, the clockwise and counterclockwise indications are relative rather than absolute. Accordingly, the illustrated configuration of the autonomous state transmission 310 provides a bidirectional autonomous state transmission configuration that is operable to disengage (e.g., cease power transmission from the drive input to the driven output) from other engaged states (e.g., providing forward or reverse self-propelled motive force) in response to both an overrunning force in the direction of motive (e.g., an over-speed force associated with over-speeding the motive operation) and an overrunning force opposite the direction of motive (e.g., an under-speed force associated with under-speeding the motive operation). In particular, the bidirectional autonomous state transmission 310 is configured to transition from the engaged state to the disengaged state in response to a user pushing the walk-behind lawn care machine equipped with the bidirectional autonomous state transmission with sufficient force to over-run the self-propelled motive operation (e.g., an overrunning force) and manually propel the lawn care machine at a faster rate than the self-propulsion provided by the bidirectional autonomous state transmission (e.g., over-speeding the bidirectional autonomous state transmission). Additionally, the bidirectional autonomous state transmission 310 is configured to transition from the engaged state to the disengaged state in response to a user pushing the walk-behind lawn care machine equipped with the bidirectional autonomous state transmission with sufficient force to over-run the self-propelled motive operation, thereby manually slowing the movement of the lawn care machine at a slower rate than the self-propulsion provided by the bidirectional autonomous state transmission (or even in the opposite direction) (e.g., under-speeding the bidirectional autonomous state transmission).

[0064] FIG. 3FThe illustrated example shows the following operation: a force associated with a user manually pushing the garden machine or causing it to operate over-speed (e.g., a first clockwise force) is applied to the driven gear 302. In the case where the clutch assembly 320 is operating in the engaged mode prior to the mentioned force being applied to the driven gear 302, rotation of the gear 302 can provide corresponding rotation of the outer ring 327 attached thereto (e.g., a first clockwise force). Rotation of the outer ring 327 (e.g., a first clockwise force) correspondingly causes rotation of the ring gear 331 of the over-ride force feedback assembly 330 (e.g., a first clockwise force). The gears 332a-332c of the over-ride force feedback assembly 330 are arranged as planetary gears within the ring gear 331 of the illustrated example. Accordingly, rotation of the ring gear 331 (e.g., a first clockwise force) causes rotation of the gears 332a-332c (e.g., a second clockwise force). The gear 333 of the over-ride force feedback assembly 330 is arranged as a sun gear relative to the planetary gears 332a-332c of the illustrated example. Thus, rotation of the gears 332a-332c (e.g., a second clockwise force) causes rotation of the gear 333 (e.g., a third counterclockwise force).

[0065] As mentioned above, the gear 333 and the hub portion 332 of the embodiment allow for at least some rotational slippage of the gear 333 and the hub portion 332. For example, FIG. 3E The illustrated example provides a slippage mechanism to facilitate limited slippage between the gear 333 and the hub portion 322. In the current example, the motor providing the motive force is deactivated such that rotational force cannot be transmitted to the over-ride control interface 321. Similarly, the same effect occurs with respect rotational force when operating in over-speed mode. Accordingly, in these cases, the hub portion 322 of the embodiment engages the gear 333 in a non-slipping relationship such that the gear 333 transmits rotational force to the hub portion 322 (e.g., causing a fourth clockwise force). That is, while the hub portion 322 is configured to allow slippage of the gear 333 relative to rotation of the gear 333 when the gear 333 and the hub portion 322 are rotating in opposite directions associated with the autonomous state transmission 310 when the clutch assembly 320 is in the engaged mode, the hub portion 322 is configured to engage the gear 333 without slippage relative to rotation of the gear 333 when the autonomous state transmission 310 receives over-ride force via the gear 302. The embodiment of the slippage mechanism described above is configured to act in a non-slipping manner in response to over-ride force transmitted via the gear 302 (e.g., over-speed and / or under-speed) to provide feedback control with respect to a disengaged state of the clutch assembly 320. For example, the undulating inner surface 337 FIG. 3EThe wave depth of the wave, the length of the tab elements 336a and 336b, and / or the spring biasing force provided by the biasing elements 335a and 335b can be configured to permit the rotation of the hub portion 322 relative to the gear 333 without slippage when there is an override force present with respect to the gear 302 that is consistent with the operation of the clutch assembly 320 in the disengaged mode. According to embodiments of the present application, one or more aspects of the slippage mechanism of the autonomous state transmission 310 are selected to perform a slippage action during self-propelled motion operation of the garden machine in which the autonomous state transmission is disposed, and a non-slippage action during over-speed and / or under-speed operation of the motion of the garden machine.

[0066] In operation according to the illustrated example, the hub portion 322 provides a force (e.g., a fourth clockwise force) to the override control interface 321 of the clutch assembly 320. The rotation of the override control interface 321 provides corresponding movement of its rolling member holders 323a-323f without initially also causing the rotation of the inner ring 325 of the clutch assembly 320. That is, the double-D circumference of the override control interface 321 coupling to the gear 333 aperture 329 of the drive shaft 301 allows for a degree of hysteresis in the movement of the override control interface 321 relative to the drive shaft 301 and, correspondingly, the inner ring 325. The rotation of the override control interface 321 proceeds without causing the rotation of the inner ring 325 until the flat surfaces 311a and 311b of the driven shaft 301 pass through the double-D circumference of the aperture 329 and engage the second (opposite) side thereof (e.g., thereafter causing a fifth counterclockwise force of the drive shaft 301). In the case where the clutch assembly 320 is initially in the engaged mode (e.g., similar to the illustration of FIG. 2F , the rolling member holders 323a-323f can rotate to move away from the corresponding one of the rolling members 324a-324f (e.g., the rolling member holders 323a-323f can stop hitting the rolling members 324a-324f, similar to the illustration of FIG. 2I ) and cause or otherwise facilitate the disengaged positioning of the rolling members 324a-324f.

[0067] The dampening resulting from the interaction of the double-D circumference of the aperture 329 of the gear 333 interfacing with the flat surfaces 311a and 311b of the drive shaft 301 disposed within the aperture 329 facilitates the disengagement mode of the clutch assembly 320 according to some embodiments of the application. In the example of disengaging the roller clutch configuration, an overrunning force can cause the outer ring 327 to rotate at a faster rate than the inner ring 325 for at least a short period of time. The sequence of force transmission and dampening implemented by the flat surfaces 311a and 311b disposed in the double-D circumference of the aperture 329 (e.g., facilitating the attainment of the following short period of time: such as in response to an overrunning force, the outer ring 327 can rotate at a faster rate than the inner ring 325, while the flat surfaces 311a and 311b of the drive shaft 301 rotate within the double-D circumference of the aperture 329, then the inner and outer rings again remain stationary relative to one another when the flat surfaces 311a and 311b engage the other side of the double-D circumference of the aperture 329) facilitates the realization of the disengagement mode of the clutch assembly 320. Accordingly, the rolling members 324a-324f can be disposed in the disengaged position, and the clutch assembly 320 is disengaged. The rolling member retainers 323a-323f of the embodiments preferably maintain the relative positioning to cause the rolling members 324a-324f to remain in the disengaged position during the application of the overrunning force to the driven gear 302.

[0068] According to embodiments of the clutch assembly 320, in the event that the rolling member retainers 323a-323f are not in a position to cause the rolling members 324a-324f to engage (e.g., the rolling member retainers 323a-323f do not strike the rolling members 324a-324f to cause the engaged position and / or the rolling member retainers 323a-323f strike the rolling members 324a-324f in the opposite manner to cause the disengaged position), the rolling members can be released from simultaneous and / or firm contact with both the corresponding roller surface 326a-326f and the inner surface 328. For example, upon sufficient rotation of the hub portion 322, the inner surface 328 can cause the rolling members 324a-324f to rotate such that the rolling members shift to the central region of their roller surface 326a-326f (e.g., similar to the illustration of FIG. 2J According to embodiments of the clutch assembly 320, in the event that the rolling member retainers 323a-323f are not in a position to cause the rolling members 324a-324f to engage (e.g., the rolling member retainers 323a-323f do not strike the rolling members 324a-324f to cause the engaged position and / or the rolling member retainers 323a-323f strike the rolling members 324a-324f in the opposite manner to cause the disengaged position), the rolling members can be released from simultaneous and / or firm contact with both the corresponding roller surface 326a-326f and the inner surface 328. For example, upon sufficient rotation of the hub portion 322, the inner surface 328 can cause the rolling members 324a-324f to rotate such that the rolling members shift to the central region of their roller surface 326a-326f (e.g., similar to the illustration of

[0069] While the above examples have been described with reference to specific directions of applied forces to provide details for understanding the concepts herein, it should be appreciated that the autonomous state transmission of embodiments can also operate bidirectionally to autonomously engage and disengage power transmission from the drive input member to the driven output member. The bidirectional autonomous state transmissions of embodiments of the present application can, for example, operate to disengage from other engaged states (e.g., providing forward or rearward self-propelled motive forces) in response to both overrunning forces in the direction of motion (e.g., overrunning the motion operation) and overrunning forces opposite the direction of motion (e.g., underrunning the motion operation).

[0070] As can be seen from the above examples, the autonomous state transmissions of embodiments of the present application include a transmission unit configured for autonomously engaging and disengaging power transmission from the drive input member to the driven output member without the need for utilizing gearing devices external to the transmission unit or additional mechanical feedback, the transmission unit being entirely contained within a single package or continuous housing (e.g., having only the drive input and driven output as external interfaces). In operation of the autonomous state transmissions 210 and 310 according to the examples herein, the autonomous state transmissions can rely solely on motion of the drive input member and / or the driven output member to engage / disengage power transmission from the drive input member to the driven output member.

[0071] While the present application and its advantages have been described in detail, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the application as defined by the appended claims. Moreover, the scope of the present application is not intended to be limited to the particular embodiments of the process, machine, manufacture, composition of matter, means, methods and steps described in the specification. As one of ordinary skill in the art will readily appreciate from the disclosure of the present application, processes, machines, manufacture, compositions of matter, means, methods, or steps, presently existing or later to be developed, that perform substantially the same function or achieve substantially the same result as the corresponding embodiments described herein can be utilized according to the present application. Accordingly, the appended claims are intended to include within their scope such processes, machines, manufacture, compositions of matter, means, methods, or steps.

[0072] Furthermore, the scope of the application is not intended to be limited to particular embodiments of the process, machine, manufacture, composition of matter, means, methods and steps described in the specification.

Claims

1. A bidirectional autonomous state transmission configured to provide self-propelled motion operation for garden machinery, the bidirectional autonomous state transmission comprising: Drive input components; Driven output component; A clutch assembly coupled to the drive input member and the driven output member and providing controlled rotational force transmission between the drive input member and the driven output member, wherein the clutch assembly includes an override control interface; as well as An override force feedback component is directly connected to both the override control interface of the driven output member and the clutch assembly, and transmits the override force from the driven output member to the clutch assembly when an override force exists at the driven output member, so as to autonomously control the force transmission state in multiple force transmission states of the bidirectional autonomous state transmission.

2. The bidirectional autonomous transmission as described in claim 1, wherein, The clutch assembly and the overdrive force feedback assembly are each fully housed within a continuous housing, which has only the drive input member and the driven output member as external interfaces for force input and force output.

3. The bidirectional autonomous transmission as described in claim 1, wherein, The overdrive force feedback component is configured to convey both the overspeed force and the underspeed force that constitute the overdrive force, thereby providing a bidirectional autonomous transmission configuration.

4. The bidirectional autonomous transmission as described in claim 1, further comprising: A sliding mechanism, wherein the oversight force feedback component transmits the oversight force to the oversight control interface via the sliding mechanism.

5. The bidirectional autonomous state transmission as described in claim 4, wherein, The sliding mechanism operates to provide sliding action, whereby the override force feedback component and the override control interface do not interfere with the first force transmission state of the bidirectional autonomous transmission during motion operation, and wherein the sliding mechanism operates to provide non-sliding action in response to the override force, whereby the override control of the force feedback component and the override control interface controls the second force transmission state of the bidirectional autonomous transmission.

6. The bidirectional autonomous transmission as described in claim 5, wherein, The first force transmission state includes an engaged state, and the second force transmission state includes an unengaged state, wherein the overdrive force includes an overspeed force, thereby allowing the motion operation provided by the bidirectional autonomous transmission to be manually overspeeded.

7. The bidirectional autonomous transmission as described in claim 5, wherein, The first force transmission state includes an engaged state, and the second force transmission state includes an unengaged state, wherein the overdrive force includes an underdrive force, thereby manually underdriveing ​​the motion operation provided by the bidirectional autonomous transmission.

8. The bidirectional autonomous transmission as described in claim 4, wherein, The sliding mechanism includes: One or more biasing tab elements impact the wavy surface of the rotating component of the bidirectional autonomous transmission.

9. The bidirectional autonomous transmission as described in claim 8, wherein, The sliding mechanism includes: The gear of the overdrive force feedback assembly has the wavy surface as its inner surface; and The hub of the overdrive force feedback assembly is connected to the gear interface and has one or more bias tab elements thereon.

10. The bidirectional autonomous state transmission as described in claim 8, wherein, The sliding mechanism includes: The gear of the overdrive force feedback assembly having the one or more bias contact elements thereon; and The hub with the overdrive control interface and the wavy surface as its outer surface.

11. The bidirectional autonomous transmission as described in claim 1, wherein, A buffer is implemented at the interface between the clutch assembly and the driven output member. The buffer is configured to facilitate the disengagement state transitioning to the plurality of force transmission states and to prevent premature engagement of the clutch assembly.

12. The bidirectional autonomous transmission as described in claim 11, wherein, The buffer is implemented by one or more drive members engaging the corresponding circumferential slots of one or more circumferential slots.

13. A method for operating a garden machine, the method comprising: When motion force is input to the drive input component of the bidirectional autonomous state transmission of the garden machine, the garden machine operates in a self-propulsion mode corresponding to the engagement state of the bidirectional autonomous state transmission. An overdrive force is input to the driven output component of the bidirectional autonomous transmission; The overrun force present at the driven output member is transmitted to the clutch assembly of the bidirectional autonomous transmission to provide overrun control of the bidirectional autonomous transmission from the engaged state to the disengaged state, wherein the overrun force is transmitted from the driven output member to the clutch assembly via an overrun force feedback assembly directly connected to the driven output member, and to the overrun control interface of the clutch assembly.

14. The method of claim 13, wherein, The clutch assembly and the overdrive force feedback assembly are each fully housed within a continuous housing, which has only the drive input member and the driven output member as external interfaces for force input and force output.

15. The method of claim 13, wherein, The overdrive force includes overspeed force, thereby allowing the self-propelled mode to be manually overspeeded.

16. The method of claim 13, wherein, The overdrive force includes underdrive force, thereby manually underdriveing ​​the self-propelled mode.

17. The method of claim 13, wherein, The overrun force present at the driven output member is transmitted to the clutch assembly via the slip mechanism.

18. The method of claim 17, wherein, The transmission of the overdrive force present at the driven output member to the clutch assembly includes: The non-sliding action of the sliding mechanism.

19. The method of claim 18, wherein, The sliding mechanism operates to provide sliding action in the engaged state of the bidirectional autonomous transmission when there is no overdrive force at the driven output member.

20. The method of claim 17, wherein, The sliding mechanism includes one or more biasing tab elements that impact the wavy surface of the rotating component of the bidirectional autonomous transmission.

21. The method of claim 13, wherein, A buffer is implemented at the interface between the clutch assembly and the driven output member, the buffer being configured to facilitate the transition to the disengaged state and to prevent premature engagement of the clutch assembly.

22. A bidirectional autonomous state transmission configured to provide self-propelled motion operation for a garden machine, the bidirectional autonomous state transmission comprising: Drive input components; Driven output component; A clutch assembly, coupled to the drive input member and the driven output member and providing controlled rotational force transmission between the drive input member and the driven output member, wherein the clutch assembly includes an override control interface; and An overdrive force feedback component is connected to the overdrive control interface of the driven output member and the clutch assembly, and transmits the overdrive force from the driven output member to the clutch assembly when an overdrive force exists at the driven output member, so as to autonomously control the force transmission state in multiple force transmission states of the bidirectional autonomous transmission. The overdrive force feedback component transmits the overdrive force to the overdrive control interface via a slip mechanism, and the overdrive force feedback component is configured to transmit both the overspeed force and the underspeed force as the overdrive force.

23. The bidirectional autonomous transmission as described in claim 22, wherein, The sliding mechanism operates to provide sliding action, whereby the override force feedback component and the override control interface do not interfere with the first force transmission state of the bidirectional autonomous transmission during motion operation, and wherein the sliding mechanism operates to provide non-sliding action in response to the override force, whereby the override control of the force feedback component and the override control interface controls the second force transmission state of the bidirectional autonomous transmission.

24. The bidirectional autonomous transmission as described in claim 22, wherein, The sliding mechanism includes: One or more biasing tab elements impact the wavy surface of the rotating component of the bidirectional autonomous transmission.

25. The bidirectional autonomous transmission as described in claim 22, wherein, A buffer is implemented at the interface between the clutch assembly and the driven output member. The buffer is configured to facilitate the disengagement state transitioning to the plurality of force transmission states and to prevent premature engagement of the clutch assembly.

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