CN113056626B

CN113056626B - Simplified gear box mechanism

Info

Publication number: CN113056626B
Application number: CN201880098595.5A
Authority: CN
Inventors: C·A·赫夫肯
Original assignee: Motus Labs LLC
Current assignee: Motus Labs LLC
Priority date: 2018-08-24
Filing date: 2018-08-27
Publication date: 2022-08-30
Anticipated expiration: 2038-08-27
Also published as: EP3841315A4; CA3108694C; JP2021524565A; KR20210049839A; WO2020040793A1; CA3108694A1; CN113056626A; EP3841315A1

Abstract

The present invention relates to an improved gearbox mechanism comprising a plurality of cam actuated simplified gear block assemblies that transfer power from a power shaft to an auxiliary or output gear element. Each gear block assembly includes a gear block having a surface that periodically abuts the auxiliary or output gear element. In a preferred embodiment, the abutment surface comprises a plurality of projections or teeth corresponding to complementary projections or gear teeth on the output gear element. Each gear block assembly further includes a gear block, a torque lever arm, a cam follower, and/or a sleeve connecting or linking the gear block to a cam assembly, which in turn is connected to a power source. The cam assembly includes a unique path or groove around its circumference for each link assembly of a particular gear block assembly so that the movement of the gear block can be controlled in two dimensions according to particular design parameters.

Description

Simplified gear box mechanism

Background

1. Cross reference to related applications

This application is a partial continuation of U.S. patent application serial No.14/995,094 filed on day 13/1/2016, a continuation of U.S. patent application serial No.13/795,488 filed on day 12/3/2013 (now U.S. patent No.9,261,176), the technical disclosures of both of which are hereby incorporated by reference.

2. Field of the invention

The present invention relates to a universal gearbox mechanism featuring a cam actuated gear block assembly that periodically engages an output gear causing power transfer. The invention has particular, but not exclusive, application to applications in servo motor assemblies.

3. Description of the related Art

Conventional machines typically consist of a power source and a drivetrain that provides a controllable application of power. In the field of power transmission systems, various proposals have been made previously. The simplest transmission systems, often referred to as gearboxes to reflect their simplicity (although complex systems are also referred to as gearboxes in white language), provide a gear reduction (or, more rarely, a speed increase), sometimes in combination with a change in direction of the power shaft. A transmission system may be defined as a component assembly that includes a speed change gear mechanism and an output shaft through which power is transmitted from a power source (e.g., an electric motor) to the output shaft. In general, a transmission simply refers to a gearbox that utilizes gears and a gear train to provide speed and torque conversion from a power source to another device.

Gearboxes have been in use for many years and they have many different applications. Generally, conventional gearboxes include four main elements: power source, drive train, shell and output utensil. The power source applies force and motion to the drive train. The power source may be an electric motor connected to the drive train by suitable gears, such as spur, bevel, helical or worm gears.

The drive train allows manipulation of output motions and forces relative to input motions and forces provided by the power source. The drive train typically comprises a number of gears of different parameters, such as different sizes, numbers of teeth, tooth types and uses, e.g. spur, helical, worm and/or internal or external toothed gears.

The gearbox housing is an implement that holds the internal workings of the gearbox in the correct manner. For example, the gearbox housing allows the power source, drive train, and output implement to be held in the correct relationship for the desired operation of the gearbox. The output implement is associated with the drive train and allows the application of force and motion from the drive train for application. Typically, the output device exits from the gearbox housing.

The output implement is typically connectable to a body, whereby the resulting output motion and force of the drive train is transmitted to the body via the output implement (e.g., output shaft) to impart motion and force of the output implement on the body. Alternatively, the output means may apply the motion and force output of the drive train to the gearbox housing, the output means thereby being sufficiently retained to allow the gearbox housing to rotate.

Rotating a power source typically operates at a higher rotational speed than the device that will utilize the power. Thus, the gearbox not only transmits power, but also converts speed into torque. The torque ratio of the gear train (also known as its mechanical advantage) is determined by the gear ratio. The energy generated by any power source must pass through the internal components of the gearbox in the form of stress or mechanical stress on the gear elements. Thus, a key aspect in any gearbox design involves engineering the proper contact between intermeshing gear elements. These contacts are typically points or lines on the gear teeth where forces are concentrated. Because the area of the point or line of contact in a conventional gear train is typically very small and the amount of power transmitted is considerable, the resulting stress along the point or line of contact is extremely high in all cases. To this end, designers of gearbox devices typically focus a significant portion of their engineering efforts on creating as large contact points as possible or as many simultaneous contact points between two intermeshing gears to reduce the resulting stresses experienced by the respective teeth of each gear.

Another important consideration in gearbox design is minimizing backlash between intermeshing gears. Backlash is the blow back of the connected wheel in the machine member when pressure is applied. In the case of gears, when the movement is reversed and contact is reestablished, backlash (sometimes referred to as backlash or play) is the amount of play between the mating parts, or lost motion due to play or slack. For example, in a pair of gears, backlash is the amount of clearance between the meshing gear teeth.

Theoretically, the backlash should be zero, but in practice some backlash is usually allowed to prevent bouncing. Backlash is unavoidable for almost all reverse mechanical couplings, although its effect can be cancelled out. Depending on the application, backlash may or may not be desired. Typical reasons for the need for backlash include allowance for lubrication, manufacturing tolerances, deflection under load, and thermal expansion. However, in many applications, low or even zero backlash is required for increased accuracy and to avoid shock or vibration. Therefore, zero backlash gear drives are expensive, short lived, and heavy in many cases.

Weight and size are another consideration for gearbox design. The aforementioned concentration of stress at the contact points or lines in the intermeshing gear train requires the selection of materials that are capable of resisting these forces and stresses. However, these materials are generally heavier, harder, and more difficult to manufacture.

Accordingly, there is a need for an improved and lighter weight gearbox mechanism that is capable of handling high stress loads in the contact points or lines between its intermeshing gears. Furthermore, there is a need for an improved and lighter weight gearbox mechanism with low or zero backlash that is inexpensive to manufacture, more reliable and durable.

Disclosure of Invention

The present invention overcomes many of the disadvantages of prior art gearbox mechanisms by utilizing a plurality of cam actuated gear block assemblies to transfer power from a power shaft to an auxiliary or output gear element. In a first embodiment, each gear block assembly includes a gear block having a surface that periodically engages an auxiliary or output gear element. In a preferred embodiment, the abutment surface comprises a plurality of projections or teeth corresponding to complementary projections or gear teeth on the output gear element. Each gear block assembly also includes a plurality of linkage assemblies that connect or link the gear blocks to a cam assembly, which in turn is connected to a power source. The cam assembly includes a unique path or groove around its circumference for each link assembly of a particular gear block assembly so that movement of the gear blocks can be controlled in two dimensions according to particular design parameters.

Each link assembly includes a link mechanism pivotally attached at its proximal end to its respective gear block and maintained at its distal end in contact with its respective pathway or groove formed in the cam assembly. In a preferred embodiment, each link mechanism comprises two pivotally coupled connector arms. The upper connector arm includes a first pivot point pivotally coupled to its respective gear block element and a second pivot point pivotally coupled to the lower connector arm. The lower connector arm includes at its distal end a cam follower element that maintains contact with its corresponding pathway or groove formed in the cam assembly. The lower connector arm also includes a pivot point having a fixed axis of rotation relative to the central axis of rotation of the cam assembly.

In a preferred embodiment, each gear block assembly includes three link assemblies pivotally coupled to the gear block and in constant contact with the cam assembly. The gear block includes pivot links disposed on opposite ends for pivotally coupling the link assembly to the gear block. Two link assemblies are coupled to the pivot rod at one end, while a single link assembly is coupled to the pivot rod at an opposite end. Each of the link assemblies includes a pivot point rotationally coupled to the fixed axis of rotation relative to the central axis of rotation of the cam assembly. In one embodiment, the present fixed pivot point comprises a pivot link fixedly included between two stationary plates. Each of the coupling assemblies is biased such that its respective cam follower element maintains contact with a surface of its respective path or groove formed in the cam assembly throughout the cam assembly's period of rotation.

The gear block assemblies are designed to drive their respective gear blocks through a two-dimensional circuit in response to rotation of the cam assembly. Broadly, the two-dimensional circuit includes causing the gear block to engage the auxiliary or output gear element and move or rotate a specified amount of distance before disengaging from the output gear element, and returning the specified amount of distance to re-engage the auxiliary or output gear element again and repeating the process. The path or line of travel of each gear block is controlled by adjusting the length and configuration of the various link assemblies and altering the path or groove formed in the cam assembly.

When adapted for use in a gearbox mechanism, a plurality of gear block assemblies are arranged about a central axis of the cam assembly. The cam assembly is rotationally coupled to the power source. As the cam assembly rotates, the cam follower elements of the respective link assemblies of each gear block assembly maintain contact with specific paths or grooves formed in the circumferential surface of the cam assembly. Variations in the distance from the center of rotation of the different paths or grooves of the cam assembly cause the respective link assemblies to act in unison to move their respective gear blocks through the predetermined line of travel. Such a predetermined line of movement of the gear block can be precisely calibrated to meet specific engineering requirements. For example, torque ratios and speed reductions may be adjusted and controlled by adjusting the line of travel of each gear block assembly.

A second embodiment of the gearbox mechanism of the present invention may comprise a main body, an output element and a plurality of simplified gear block assemblies. Further, the gearbox mechanism may have a retainer that interfaces the body and the output element. Each simplified gear block assembly includes a gear block, a torque rod, a cam follower, and/or a sleeve (or a portion of a sleeve). The cam actuated gear block assembly may be configured about a central axis. The rotational force on the cam element allows for a driving or rotational force on the cam actuated gear block assembly.

In a preferred embodiment, the torque rod also has a set of cam followers allowing a prescribed path to be followed, the prescribed path being formed along a flat surface of the cam member. The cam member includes at least one unique path or groove that interfaces with a cam follower of the gear block or torque rod such that as the cam member rotates, movement of the gear block or torque rod is controlled in two dimensions according to at least one particular design parameter.

By varying the radius of the path or groove on the cam element, the cam actuated gear block assembly drives the respective gear block through a two dimensional line in response to rotation of the cam element. Broadly speaking, the two-dimensional circuit includes causing the gear block to engage the output member and move and/or rotate the output member a specified distance before disengaging from the output member, and returning the specified distance to reengage the output member and repeat the process. The path or line of travel of each gear block is controlled by adjusting the length, width, height and/or size of the respective gear block and/or torque rod and/or altering the path or groove formed in the cam element. In a preferred embodiment, for both the gear block and the torque rod, there is at least one pivot point that allows the gear block and the torque rod to each pivot independently of each other.

A third embodiment of the gearbox mechanism of the present invention may comprise a cam element, a body, an output element and a plurality of simplified gear block assemblies. In at least one example, the output element is retained within the body by a retainer. The gear block assembly is disposed within the body and interfaces the output element and the cam element. The gear block assembly may include a torque rod, a gear block, a first cam follower, and a second cam follower. In at least one version, the cam follower follows a path in the cam element to generate a force on the torque rod and/or the gear block to generate a pivoting motion of both the torque rod and the gear block, which may be a substantially square pivoting path of the gear block. However, in other versions, the pivot path of the gear block will generally be oval or circular.

In at least one version, the central aperture aligned with the central axis may be part of a gearbox mechanism. Each gear block assembly includes a gear block, a torque rod, and at least one cam follower connecting the gear block to a planar surface of a cam member. The torque rod and/or gear block may interact to pivotally attach and correspond to the intersection and/or engagement of the cam follower with the cam element. Rotation of the output member may also be controlled by reverse or tensioning engagement (i.e., negative bias) of a gear block that is not in driving or positively biased rotational engagement to reduce and/or eliminate backlash.

In at least one version, the body provides a housing for a gear assembly. The gear block assembly rests and/or is supported by the body retaining surface. The gear block may also be retained and/or supported by the body gear block abutment surface. The torque rod is also supported and/or retained by the body torque rod abutment surface and/or the body torque rod void, as defined by the body. The pivotal movement of the torque rod may also coincide with the pivotal movement of the gear block (which allows for docking, engagement and/or rotation of the output element).

With the gear block assembly of the present invention, multiple embodiments of a gearbox mechanism are possible. The plurality of gear block assemblies disposed about the central axis of the cam assembly may include an odd or even number of gear block assemblies. At least two, preferably three, gear block assemblies are required for the gearbox mechanism of the present invention. The movement of the gear block assemblies typically moves in a rotational series with each other. At least one gear block assembly always engages the output gear element at any particular time. Preferably, only one gear block assembly is disengaged from the output gear element at any particular time. However, in another preferred embodiment wherein the plurality of gear block assemblies comprises four or more even gear block assemblies, the gear block assemblies disposed on opposite sides of the cam assembly cooperatively engage and disengage the auxiliary or output gear element.

The design of the gear block assembly of the present invention allows a greater number of gear teeth to engage the output gear at any given time, thereby spreading the stresses associated therewith over a larger area. By substantially increasing the contact area between the gear block and the output gear at any given time, the level of mechanical stress is significantly reduced. In addition, the gear block assembly of the present invention reduces backlash to zero and reduces the preload condition to create a tight connection between the power source 2 and the powered device. This is an extremely desirable feature, especially for high vibration applications. By reducing the backlash to zero or reducing the preload condition, the mechanical impedance can also be reduced over a wide range of high vibration frequencies. Furthermore, because the stress distribution associated with the engagement of the gear block to the output gear traverses a larger area, the gear block mechanism may be manufactured from lighter, more flexible materials that are less expensive and easier to manufacture, with no reduction in reliability. In fact, using a flexible material also reduces the mechanical impedance at low frequencies. By reducing its weight and size, the gearbox mechanism of the present invention is suitable for a wide range of applications that were previously impractical due to weight and space limitations.

Drawings

A more complete understanding of the method and apparatus of the present invention may be obtained by reference to the following detailed description when considered in conjunction with the accompanying drawings wherein:

FIG. 1A is a perspective view of a first embodiment of a gearbox mechanism of the present invention attached to a power source;

FIG. 1B is a side elevational view thereof;

FIG. 2 is an exploded perspective view thereof;

FIG. 3 is an end view thereof with the outer stationary plate removed;

FIG. 4A is a close-up side elevational view of the gear block assembly illustrated in FIG. 3;

FIG. 4B is a perspective view of the gear block assembly shown in FIG. 3;

FIG. 4C is an exploded perspective view thereof;

FIG. 4D is a close-up cross-sectional view of the gear block assembly shown in FIG. 4A, engaging an output gear;

FIG. 5 is a perspective view of an embodiment of the gearbox mechanism shown in FIG. 3;

FIG. 6 is a close-up perspective view of the gear block assembly shown in FIG. 5;

FIGS. 7A-7C are end views with the outer stationary plate of the different variant embodiment of the gearbox mechanism of the present invention shown in FIG. 1 removed;

FIG. 8 is an exploded view of a second embodiment of the gearbox mechanism of the present invention;

FIG. 9A is a perspective view of a cam member of the gearbox mechanism shown in FIG. 8, along with a torque rod, sleeve, and gear block;

FIG. 9B is a partially cut-away perspective view of the cam member, torque rod and cam follower of the gearbox mechanism shown in FIG. 8;

FIG. 10A is a close-up side view of a gear block and output member of the gearbox mechanism shown in FIG. 8;

FIG. 10B is a close-up side view of the gear block and output member of the gearbox mechanism shown in FIG. 8;

FIG. 10C is a side view of a gear block and an output member of the gearbox mechanism shown in FIG. 8;

FIG. 11 is an exploded view of a third embodiment of the gearbox mechanism of the present invention;

FIG. 12A is an exploded view of the body, output member and retainer of the gearbox mechanism shown in FIG. 11.

Fig. 12B is a perspective view of the main body of the gear box mechanism shown in fig. 11.

FIG. 12C is an exploded perspective view of the main body and gear block assembly of the gearbox mechanism shown in FIG. 11.

FIG. 13 is a perspective view of a cam member of the gearbox mechanism shown in FIG. 11; and

FIG. 14 is a perspective view of a gear block assembly of the gearbox mechanism shown in FIG. 11.

In the case of the figures used in the drawings, the same reference numbers designate the same or similar parts. Further, when the terms "top," "bottom," "first," "second," "upper," "lower," "height," "width," "length," "end," "side," "horizontal," "vertical," and the like are used herein, it is to be understood that such terms refer only to the structures shown in the drawings and are used merely to facilitate the description of the invention.

All drawings are drawn for the purpose of illustrating the general teachings of the invention only; the drawings are to be interpreted, or are to be within the skill of the art, after reading and understanding the following teachings of the present invention with regard to the number, location, relationship, and extension of the parts to form the preferred embodiments. Further, the exact dimensions and dimensional proportions to conform to specific force, weight, strength and similar requirements will likewise be within the skill of the art after the following teachings of the present invention have been read and understood.

Detailed Description

Referring to the drawings, and in particular to fig. 1A, 1B and 2, one embodiment of a machine 10 utilizing the gearbox mechanism 20 of the present disclosure is shown. Machine 10 includes a power source or actuator 2, with power source or actuator 2 including an output device 4, with output device 4 transmitting power generated by power source 2. Although the embodiments shown in the figures generally show the power source 2 as an electric motor and the output device 4 as an output shaft of the electric motor, it should be understood that there are a variety of possible embodiments. For example, the output device 4 need not be directly connected to the power source 2, but may be rotationally coupled by gears, chains, belts, or magnetic fields. Likewise, power source 2 may include an electric motor, an internal combustion engine, or any conventional power source suitable for generating rotational power in output device 4. Furthermore, the power source 2 may also include an output gear of a coil gear transmission.

The output device 4 includes a central shaft that connects to the gearbox mechanism 20 through a central aperture 32 in the cam assembly 30 of the gearbox mechanism 20. The gearbox mechanism 20 is arranged about the central axis 6 of the central shaft of the output and comprises two stationary plates 40, between which stationary plates 40 an output or power gear 50, a cam assembly 30 and a plurality of cam actuating gear block assemblies 60 are arranged, the plurality of cam actuating gear block assemblies 60 transferring power from the cam assembly 30 to the output or power gear element 50. The two bearing assemblies 22 separate the cam assembly 30 from the stationary plate 40 so that the cam assembly 30 can freely rotate between the two stationary plates 40. Also, the spacing element 46 disposed between the two stationary plates 40 ensures that movement of the power gear element 50 is not impeded by the stationary plates 40. The gear block assemblies 60 are evenly spaced around the circumference of the cam assembly 30. Each gear block assembly 60 includes a gear block 62 and a plurality of link assemblies that connect the gear block 62 to the outer circumferential surface of the cam assembly 30. Each link assembly includes a link mechanism pivotally attached at its proximal end to its respective gear block and including at its distal end a cam follower element that remains in contact with its respective path or groove formed in the circumferential surface of cam assembly 30. Each link assembly includes a fixed axis pivot point connected to two stationary plates 40. Although each link assembly may pivot about its respective fixed axis pivot point 48, the alignment and configuration of the pivot points remains fixed relative to the two stationary plates 40.

As shown in the embodiment illustrated in the drawings, a plurality of cam actuated gear block assemblies 60 transmit power from the power shaft 4 to the annular auxiliary or output gear element 50. In a preferred embodiment, each gear block assembly 60 includes a gear block 62 having an interface surface 63 (e.g., a plurality of projections or teeth 66), the interface surface 63 corresponding to a complementary interface surface 54 (e.g., projections or gear teeth) configured on the inner circumferential surface 53 of the annular auxiliary or output gear element 50. It should be understood that the interface between the gear block 62 and the inner circumferential surface 53 of the output gear element 50 of the present invention includes not only the preferred gear teeth shown, but also any complementary arrangement, such as pins and holes or even friction fit surfaces.

While the annular output or power gear element 50 is shown as two circular rings separated by a spacing element 55, it should be understood that the output or power gear element 50 may comprise a single circular ring. The output or power gear element 50 includes an aperture or bore 58 for attachment to an output shaft or power output (not shown). Further, it should be understood that the outer circumference 51 of the output or power gear element 50 may also include a surface to interface with some other gear train.

Further, it should be understood that the gear block 62 may include a divider/alignment block 68 that divides the interface surface 63 into two separate sections. The variation of gear block 62 that characterizes alignment block 68 is particularly suited for characterizing embodiments of output or power gear element 50 that include two circular rings.

The gear block 62 of the present invention is specifically designed to allow a larger surface area (e.g., a larger number of gear teeth) to engage the output gear 50 at any given time, thereby spreading the stresses associated therewith over a larger area. By substantially increasing the contact area between the gear block 62 and the output gear 50 at any given time, the level of mechanical stress is significantly reduced. In addition, the gear block 62 assembly of the present invention reduces backlash to zero and reduces the preload condition to create a tight connection between the power source 2 and the powered device. This is an extremely desirable feature, especially for high vibration applications. Furthermore, because the stress distribution associated with the engagement of the gear block 62 against the output gear 50 traverses a larger area, the gear block 62 may be manufactured from lighter materials, which are generally less expensive and easier to manufacture, with no reduction in reliability. For example, typical stress results for spur gears are in the range of 450MPa to 600MPa, according to Hertz's contact theory. High grade steel is the most suitable material for handling such high stress levels. Other materials, such as low grade steel or aluminum, will deform under similar conditions. However, by distributing the stress across a large contact area by means of the gearbox mechanism according to the invention, the stress level under similar conditions can be reduced to about 20 MPa. These low stress levels allow the gearbox mechanism of the present invention to be manufactured from low grade steel, aluminum, or even plastic for the same application. By reducing its weight and size, the gearbox mechanism of the present invention is suitable for a wide range of applications that were previously impractical due to weight and space limitations.

The cam assembly 30 is coupled to the power source 2 by an output or power shaft 4. Thus, power generated by the power source 2 is transmitted to the power shaft 4, which causes the cam assembly 30 to rotate about the central axis 6. The cam assembly 30 includes a plurality of unique paths or grooves about its circumferential surface 34 that each interface with the cam follower elements of the individual link assemblies of each gear block assembly 60 such that as the cam assembly 30 rotates, the movement of the gear blocks 62 is controlled in two dimensions according to particular design parameters. By varying the radius of the path or groove on the cam assembly 30, the linked assembly of the gear block assemblies 60 drives the respective gear block 62 through a two-dimensional circuit in response to rotation of the cam assembly 30. Broadly speaking, the two-dimensional circuit includes causing the gear block to engage the output gear member 50 and move or rotate the output gear member 50a specified amount of distance before disengaging from the output gear member 50, and returning the specified amount of distance to re-engage the output gear member 50 again and repeating the process. The path or line of travel of each gear block 62 is controlled by adjusting the length and configuration of the various link assemblies and modifying the path or groove formed in the cam assembly 30.

In a preferred embodiment, each link mechanism comprises two pivotally coupled connector arms. The upper connector arm includes a first pivot point pivotally coupled to its respective gear block 62 and a second pivot point pivotally coupled to the lower connector arm. The lower connector arm includes a cam follower element at its distal end that maintains contact with its corresponding pathway or groove formed in the cam assembly 30. The lower connector arm also includes a pivot point having a fixed axis of rotation relative to the central axis 6 of rotation of the cam assembly 30.

Referring now to fig. 4A-4D, a preferred embodiment of the gear block assembly 60 is shown. In the preferred embodiment shown, each gear block assembly 60 includes three

link assemblies

70,80,90, each pivotally coupled to a gear block 62 and each including a

cam follower member

74,84,94, the

cam follower members

74,84,94 maintaining constant contact with the cam assembly 30. The gear block 62 includes pivot links disposed on opposite ends for pivotally coupling the

link assemblies

70,80,90 to the gear block 62. For example, two

link assemblies

70,80 are pivotally coupled at one end to pivot link 64a, while a single link assembly 90 is pivotally coupled at an opposite end to pivot link 64 b. Each of the

link assemblies

70,80,90 includes a

pivot point

78,88,98, respectively, that

pivot point

78,88,98 is rotationally coupled to the fixed axis of rotation relative to the central axis 6 of rotation of the cam assembly 30. As shown, each fixed axis of rotation includes a pivot pin 48, the pivot pins 48 being fixed in matching aligned holes 44 disposed in the two stationary plates 40. Although each of the

link assemblies

70,80,90 may pivot about their respective fixed axis pivot points 78,88,98, respectively, the alignment and configuration of these pivot points remains fixed relative to the two stationary plates 40. Each of the

link assemblies

70,80,90 is biased such that its respective

cam follower element

74,84,94, respectively, maintains contact with the surface of its respective path or groove formed in the cam assembly 30 throughout the entire cam assembly 30 rotation cycle.

In the preferred embodiment shown, each of the link assemblies may also include at least two connector arms. For example, the first link assembly 70 may include a lower connector arm 72, the lower connector arm 72 pivotally connected to an upper connector arm 74, the upper connector arm 74 also pivotally connected to the gear block 62. A pivot pin 71 is used to pivotally connect the lower connector arm 72 to the upper connector arm 74. The lower connector arm 72 includes a cam follower element 74 at a distal end thereof. In a preferred embodiment, the cam follower element 74 comprises a support wheel 75, the support wheel 75 being rotationally coupled to the distal end of the lower connector arm by an axle 76. The lower connector arm 72 further includes a pivot point 78, the pivot point 78 being rotationally coupled to the fixed axis of rotation relative to the central axis of rotation 6 of the cam assembly 30. For example, the pivot pin 48a secured in the mating alignment holes 44 (disposed in the two stationary plates 40) serves as a fixed axis of rotation relative to the central axis 6 of rotation of the cam assembly 30. While the lower connector arm 72 may pivot about its fixed axis pivot point 78, the alignment and configuration of the pivot point 78 remains fixed relative to the two stationary plates 40. Each of the pivotal connections in the first link assembly 70 is biased such that the cam follower elements 74 maintain contact with the surface of their respective paths or grooves 36, the paths or grooves 36 being formed in the circumferential surface 34 of the cam assembly 30 throughout the entire rotation cycle of the cam assembly 30. For example, the pivotal connection may further include a torsion spring element (not shown) that biases the first link assembly 70 such that the cam follower elements 74 maintain contact with the surface of their respective paths or grooves 38, the paths or grooves 38 being formed in the circumferential surface 34 of the cam assembly 30 throughout the rotational cycle of the cam assembly 30. Alternatively, the cam follower element of each link assembly may comprise a conjugate cam to bias the pivotal connections in the link assembly. Alternatively or additionally, an annular spring connecting all gear blocks 82 in the gear train may be used as a biasing mechanism according to the present invention.

Similarly, the second link assembly 80 may include a lower connector arm 82, the lower connector arm 72 pivotally connected to an upper connector arm 84, the upper connector arm 84 also pivotally connected to the gear block 62. The upper connector arm 84 is pivotally connected to the gear block 82 by the same pivot link 84a, the pivot link 84a being used to pivotally connect the upper connector arm 74 of the first link assembly 70. A pivot pin 81 is used to pivotally connect the lower connector arm 82 to the upper connector arm 84. The lower connector arm 82 includes a cam follower element 84 at a distal end thereof. In a preferred embodiment, the cam follower element 84 comprises a support wheel 85, the support wheel 85 being rotationally coupled to the distal end of the lower connector arm by an axle 86. The lower connector arm 82 further includes a pivot point 88, the pivot point 88 being rotationally coupled to the fixed axis of rotation relative to the central axis of rotation 6 of the cam assembly 30. For example, the pivot pin 48b secured in the mating alignment holes 44 (disposed in the two stationary plates 40) serves as a fixed axis of rotation with respect to the central axis 6 of rotation of the cam assembly 30. While the lower connector arm 82 may pivot about its fixed axis pivot point 88, the alignment and configuration of the pivot point 88 remains fixed relative to the two stationary plates 40. Each of the pivotal connections in the second link assembly 80 is biased such that the cam follower elements 84 maintain contact with the surface of their respective paths or grooves 37, the paths or grooves 37 being formed in the circumferential surface 34 of the cam assembly 30 throughout the entire rotation cycle of the cam assembly 30. For example, the pivotal connection may further include a torsion spring element (not shown) that biases the second link assembly 80 such that the cam follower elements 84 maintain contact with the surface of their respective paths or grooves 37, the paths or grooves 37 being formed in the circumferential surface 34 of the cam assembly 30 throughout the entire rotational cycle of the cam assembly 30. Alternatively or additionally, an annular spring connecting all gear blocks 62 in the gear train may be used as a biasing mechanism according to the present invention.

Likewise, the third link assembly 90 may include a lower connector arm 92, the lower connector arm 92 pivotally connected to an upper connector arm 94, the upper connector arm 94 also pivotally connected to the gear block 62. The upper connector arm 94 of the third link assembly 90 is pivotally coupled to the pivot link 64b, the pivot link 64b is configured on the opposite end of the gear block 62 as the pivot link 64a, and the

upper connector arms

74,84 of the first and

second link assemblies

70,80 are rotationally coupled to the pivot link 64 a. A pivot pin 91 is used to pivotally connect the lower connector arm 92 to the upper connector arm 94. The lower connector arm 92 includes a cam follower element 94 at a distal end thereof. In a preferred embodiment, the cam follower element 94 includes a support wheel 95, the support wheel 95 being rotationally coupled to the distal end of the lower connector arm by an axle 96. The lower connector arm 92 further includes a pivot point 98, the pivot point 98 being rotationally coupled to the fixed axis of rotation relative to the central axis of rotation 6 of the cam assembly 30. For example, the pivot pin 48c secured in the mating alignment holes 44 (disposed in the two stationary plates 40) serves as a fixed axis of rotation relative to the central axis 6 of rotation of the cam assembly 30. While the lower connector arm 92 may pivot about its fixed axis pivot point 98, the alignment and configuration of the pivot point 98 remains fixed relative to the two stationary plates 40. Each of the pivotal connections in the second link assembly 90 is biased such that the cam follower elements 94 maintain contact with the surface of their respective paths or grooves 38, the paths or grooves 38 being formed in the circumferential surface 34 of the cam assembly 30 throughout the entire rotation cycle of the cam assembly 30. For example, the pivotal connection may further include a torsion spring element (not shown) that biases the second link assembly 90 such that the cam follower elements 94 maintain contact with the surface of their respective paths or grooves 38, the paths or grooves 38 being formed in the circumferential surface 34 of the cam assembly 30 throughout the rotational cycle of the cam assembly 30. Alternatively or additionally, an annular spring connecting all gear blocks 82 in the gear train may be used as a biasing mechanism according to the present invention.

Each of the

link assemblies

70,80,90 is biased such that its respective

cam follower element

74,84,94 maintains contact with the surface of its respective path or groove formed in the cam assembly 30 throughout the entire rotation cycle of the cam assembly 30. For example, the cam follower elements 74 maintain contact with the surface of the first path 36, the cam follower elements 84 maintain contact with the surface of the second path 37, and the cam follower elements 94 maintain contact with the surface of the third path 38. Each path has a unique circumference whose radius changes during the course of the path. Thus, for example, as shown in fig. 5 and 6, the first path 36 has a first radius r1 at one portion of its circumference, the first radius r1 being greater than a second radius r2 at another portion of its circumference. This creates a unique undulating path for each path as the cam assembly 30 rotates. While the cam assembly 30 shown in the drawings appears to be a single disc or unit having a plurality of pathways or grooves formed in the circumferential surface 34 of the cam assembly 30, it should be understood that the cam assembly 30 can also include a plurality of individual discs, each having a unique pathway formed in its circumferential surface that are mechanically coupled to one another to assemble a single cam assembly 30.

As the cam assembly 30 rotates, the cam follower elements follow their respective paths, maintaining contact with the circumferential surfaces of the respective paths. As the radius of the path changes, the respective link assembly pivots about its fixed axis pivot point to compensate. This pivoting of the link assembly about its fixed axis pivot point induces a similar movement of the pivotal connection and gear block 62 that results in movement of the gear block 62. Thus, as the cam assembly 30 rotates, the movement of the gear block 62 is controlled by the induced pivoting of the plurality of link assemblies. For example, by changing the radius of the first path or groove 38 on the cam assembly 30, the first link assembly 70 pivots about its fixed axis pivot point 78 to compensate for and maintain contact between the first cam follower 74 and the surface of the first path or groove 36. This pivoting of the first link assembly 70 about its fixed axis pivot point 78 induces movement of the pivotal connection and gear block 62. Each link assembly functions independently of the other link assemblies as the cam follower element of each link assembly follows a different path formed in the circumferential surface of the cam assembly.

By varying the radius of each path or

groove

36,37,38 on the cam assembly 30, the

link assemblies

70,80,90 drive their respective gear blocks 62 through a two-dimensional circuit in response to rotation of the cam assembly 30. Generally, as shown in FIG. 4A, the two-dimensional circuit 65 includes causing the gear block to engage the output gear member 50 and move or rotate the output gear member 50a specified quantitative distance before disengaging from the output gear member 50, and returning the specified quantitative distance to re-engage the output gear member 50 again and repeating the process. It is to be understood that the two-dimensional lines 65 shown in the figures are not to scale and are somewhat exaggerated to illustrate the general principles of the present invention. For example, the distance A-B will typically be much less than the distance shown. The travel path or line 65 of each gear block 62 is controlled by adjusting the length and configuration of the various link assemblies and altering the path or groove formed in the cam assembly 30.

When adapted for use with the gearbox mechanism 20, a plurality of gear block assemblies 60 are arranged about the central axis 6 of the cam assembly 30. The cam assembly 30 is coupled to the power source 2 through the output 6. As the cam assembly 30 rotates, the cam follower elements (e.g., 74,84, 94) of the respective link assemblies (e.g., 70,80, 90) of each gear block assembly 60 maintain contact with a particular path or groove (e.g., 36,37, 38) formed in the circumferential surface 34 of the cam assembly 30. Variations in the distance from the center of rotation of the different paths or grooves (e.g., 36,37, 38) of the cam assembly 30 cause the link assemblies pivotally attached to their respective gear blocks 60 to act in unison to move their respective gear blocks through the predetermined line of travel 85. Such a predetermined line of movement 85 of the gear block 60 can be precisely calibrated to meet specific engineering requirements. For example, the torque ratio and speed reduction may be adjusted and controlled by adjusting the travel line 65 for each gear block assembly 80.

With the gear block assembly 60 of the present invention, multiple embodiments of the gearbox mechanism are possible. All embodiments of the gearbox mechanism constructed in accordance with the present invention feature a plurality of gear block assemblies 60 arranged about the central axis 8 of the cam assembly 30, and may include an odd or even number of gear block assemblies 60. At least two, and preferably three, gear block assemblies are required for the gearbox mechanism of the present invention. For example, as shown in FIG. 7A, a variant embodiment of a gearbox mechanism 100 featuring three gear block assemblies 60 is shown. Fig. 7B illustrates a variant embodiment of a gearbox mechanism 110 featuring five gear block assemblies 60. The movement of the gear block assemblies 80 typically move in a rotational series with one another.

However, in a preferred embodiment of the present invention in which the plurality of gear block assemblies comprises four or more even gear block assemblies 80, the gear block assemblies 60 disposed on opposite sides of the cam assembly 30 cooperatively engage and disengage the auxiliary or output gear element 50. For example, as shown in FIG. 3, one embodiment of a gearbox mechanism 20 featuring four gear block assemblies 60 is shown. Similarly, fig. 7C illustrates a variant embodiment of the gearbox mechanism 120 featuring six gear block assemblies 60. This can be achieved by ensuring that the individual paths or grooves formed in the circumferential surface of the cam member are in phase with each other on opposite sides of the cam member circumference.

Referring now to FIG. 8, a second embodiment of the gearbox mechanism 120 of the present invention is shown. The gearbox mechanism 120 may include a body 140, an output member 150, and a plurality of simplified gear block assemblies 160. Further, the gearbox mechanism 120 may have a retainer 112, the retainer 112 interfacing the body 140 and the output member 150. Such an interface allows the output member 150 to be connected to an output device and/or a rotatable device that is part of the gearbox mechanism. The output device and/or rotatable device may be an electric motor, an internal combustion engine, or any conventional power source that may be adapted to generate or receive rotational power. Furthermore, the output device and/or the rotatable device may be rotationally coupled by a gear, a chain, a belt, or a magnetic field. The output member 150 interfaces with the gear block 162 via an interface surface, wherein the output member 150 may have an internal interface surface or an external interface surface. The internal or external abutment surfaces may include gear teeth, friction-based geometric engagement, friction wedges, or any other form of mating surface (including but not limited to posts and holes).

Referring now to fig. 8 and 9, the cam actuating gear block assembly 160 may include the gear block 162, the torque rod 199, the cam follower 194, and/or the sleeve 189 (or a portion of the sleeve 189). The cam actuation gear block assembly 160 is configurable about the central axis 106. A shaft, gear, belt, or magnetic field (not shown) may be utilized along the central axis 106 to couple the input device and/or the rotating device with the cam element 130 to generate a force or rotational force on the cam element 130. The rotational force on the cam member 130 allows for a driving or rotational force on the cam actuated gear block assembly 160. In a preferred embodiment, the body 140 is stationary, or a stationary plate relative to the cam actuated gear block assembly 160 and/or the output member 150.

While the output member 150 is shown as a single circular annulus, it should be understood that the output member or power gear member 150 may include two circular annuli separated by a spacer member (not shown). The output element 150 includes an aperture or bore 158 for attachment to an output shaft or power take-off (not shown), the aperture or bore 158 being defined along an outer surface and/or within the output element 150. Further, it should be understood that the outer circumference 151 of the output member 150 may also include a surface to interface with some other gear train or other output device via a belt or gear.

The gear block 162 of the present invention is specifically designed to allow a larger surface area (e.g., a larger number of gear teeth) to engage the output member 150 at any given time, thereby spreading the stresses associated therewith over a larger area. By substantially increasing the contact area between the gear block 162 and the output member 150 at any given time, the level of mechanical stress is significantly reduced. In addition, the gear block 162 assembly of the present invention reduces backlash to zero and reduces the preload condition to create a tight connection between the power source and/or powered devices (not shown). This is an extremely desirable feature, especially for high vibration applications. Furthermore, because the stress distribution associated with the engagement of the gear block 162 against the output member 150 traverses a larger area, the gear block 162 may be manufactured from lighter materials, which are generally less expensive and easier to manufacture, with no reduction in reliability.

For example, typical stress results for spur gears are in the range of 450MPa to 600MPa, according to Hertz's contact theory. High grade steel is the most suitable material for handling such high stress levels. Other materials, such as low grade steel or aluminum, will deform under similar conditions. However, by distributing the stress across a large contact area by means of the gearbox mechanism according to the invention, the stress level under similar conditions can be reduced to about 20 MPa. These low stress levels allow the gearbox mechanism of the present invention to be manufactured from low grade steel, aluminum, or even plastic for the same application. By reducing its weight and size, the gearbox mechanism 120 of the present invention is suitable for a wide range of applications that were previously impractical due to weight and space limitations.

In at least one embodiment of the present disclosure, the gear block 162 may also rest inside the sleeve 180 or be surrounded by the sleeve 189. The sleeve 189 may be associated with or coupled to the torque rod 199. In some embodiments, the torque rod 199 may also have a set of cam followers 194, allowing a prescribed path to be followed, formed in or along the flat surface of the cam element 130. The cam member 130 may also have an input hub 114 or ball bearing assembly 116, the input hub 114 or ball bearing assembly 116 allowing the cam member 130 to rotate freely based on an input device (such as a shaft or rotatable member, such as a set of other bearings, belts, rods, magnetic or electric fields, etc.). The sleeve 189 may also have a stationary center guide 124, the center guide 124 allowing the shaft and/or rotatable element to pass through the output element, body, retainer, gear block, torque rod, and/or cam element along the central axis 106. The gear block 162, cam follower 194, center guide 124, sleeve 189, torque rod 199, and cam element 130 may notch the gear block assembly 160. The gear block assembly 160 allows the gear block 160 to rotate in a manner that engages the output member 150 through the intersection of the cam follower 194 and the cam member 130. An abutment surface of the gear block 162 may engage an output member abutment surface (not shown) of the output member 150. In some embodiments, the gear block is rotated by the relative movement of the torque rod 199 and the sleeve.

The cam member 130 includes at least one unique path or groove that abuts the cam follower 194 of the gear block 162 or torque rod 199 such that as the cam member 130 rotates, the movement of the gear block 162 or torque rod 199 is controlled in two dimensions according to at least one particular design parameter. By varying the radius of the path or groove on the cam element 130, the cam actuated gear block assembly 160 drives the respective gear block 162 through a two dimensional line in response to rotation of the cam element 130. Broadly speaking, the two-dimensional circuit includes causing the gear block 162 to engage the output member 150 and move and/or rotate the output member 150a specified distance before disengaging from the output member 150, and returning the specified distance to reengage the output member 150 and repeat the process. The path or line of travel of each gear block 160 is controlled by adjusting the length, width, height and/or size of the respective gear block and/or torque rod and/or altering the path or groove formed in the cam element 130.

The torque rod is pivoted about a particular pivot point by a cam follower 199, the cam follower 199 traversing a path in the cam member 130. In addition, the sleeve and/or the H-even gear block may also have a cam follower 199, the cam follower 199 following the same or a separate path along the cam element 130, the cam element 130 also triggering the pivot point of the sleeve or gear block. In at least one embodiment, there is at least one pivot point for both the gear block and the torque rod that allows each to pivot independently of the other while also being at a movement junction to form a particular movement pattern of the gear block. In at least one example, the movement of the gear piece is a cyclical, annular, or closed-loop movement that may have a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, the designated movement pattern being designed.

Referring now to FIG. 9A, a perspective view of the cam member 130 is shown along with the torque rod 199, the sleeve 189, and the gear block 182. The central axis 106 may pass through the sleeve 189, the cam member 130, and/or the center guide 124 at the center of the output member 150. The sleeve 189 may comprise separate pieces that also correspond to each of the separate gear blocks 182. In at least one embodiment of the present disclosure, the sleeve 189 interacts with the torque rod 199 in conjunction with the gear block 162 based on a path in the cam element 150 that can allow a cam follower (not shown) attached to the torque rod 199 to traverse along the path to generate movement of the gear block to have cyclical, annular, or closed-loop movement with a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, designing a specified movement pattern.

Cam followers (not shown) may also be attached to the gear block and/or the sleeve, thereby also allowing force to be generated against them. Each of the cam followers may have an independent path, or in some embodiments, may have a single path. The gear block 162 is pivotally connected to the torque rod 199 and/or the sleeve 189. Alternatively or additionally, an annular spring connecting all gear blocks 182 in the gear train may be used as a biasing mechanism according to the present invention. In at least one embodiment of the present disclosure, the paths in the cam element 130 may be in the same plane, where they are parallel paths, or paths of different distances from the central axis 106; or the paths may be in separate planes stacked in the direction of the central axis 106.

Referring now to fig. 9B, a perspective view of the cam member 130, the torque rod 199, the cam follower 194 (coupled to the torque rod 199), and the cam follower 194 (coupled to the gear block 162) is shown. In at least one embodiment, the first path 136 along the cam member 130 and the second path 137 along the cam member 130 allow for movement and rotation of the gear block, thereby allowing the interfacing surfaces of the gear block 162 to engage, interface and/or interact with an output member (not shown). The cam followers 194 maintain contact with the surfaces of their respective paths or grooves formed in the cam member 130. The first path 136 has a first radius r1 at one portion of its plane, the first radius r1 being greater than a second radius r2 at another portion of its plane. This creates a unique undulating path for each path as the cam member 130 rotates. While the cam member 130 shown in the drawings appears to be a single disc or unit having a plurality of pathways or grooves formed in the planar surface 134 of the cam member 130, it should be understood that the cam member 130 may also include a plurality of individual discs, each having a unique pathway formed in its circumferential surface that are mechanically coupled to one another to assemble a single cam assembly 130.

As the cam member 130 rotates, the cam followers 194 follow their respective paths, maintaining contact with the flat surfaces of the respective paths or grooves 136/137. As the radius of the path changes, the respective gear block 162 and/or torque rod 199 pivots or moves about its pivot point to compensate for the change in the path or groove. In at least one version, the torque rod 199 can pivot about its pivot point, thereby inducing movement or pivoting of the sleeve (not shown) and/or the gear block 182 (to which the torque rod 199 is pivotally coupled) and causing movement of the gear block 162. Thus, as the cam member 130 rotates, movement of the gear block 162 is controlled by induced pivoting of the torque rod 199 and/or the sleeve (not shown). For example, by changing the radius of the first path or groove 136 on the cam member 130, the torque rod 199 pivots about its pivot point to compensate for and maintain contact between the torque rod 199 and the bushing (not shown). This pivoting or movement of the torque rod 199 about its pivot point induces movement of the pivotal connection and the sleeve (not shown) and/or the gear block 162. Each torque rod 199 because the cam follower 194 of each torque rod 199 acts independently of the other torque rods 199, the cam follower 194 follows and/or traverses the first path 136 formed in the planar surface of the cam element 130 at its respective different point.

With respect to the cam element 130, the first path 136 and the second path 137 may be in the same plane and may sometimes be parallel and/or non-parallel to each other, with the first path being on an outer radius of the cam element 130 and the second path 137 being along an inner radius and closer to a central axis of the cam element 130. It should be understood that in some embodiments, the paths may be stacked in separate planes such that the first and second planes are stacked on top of one another in the Z-direction or central axis 106. As the cam followers of the gear block and the torque rod follow their respective paths, the torque rod may pivot at a particular point, causing the sleeve and/or the gear block itself to rotate about the particular point. The cam follower of the gear block also allows the gear block to transition in a particular current and/or predetermined direction. For example, the pivot point of the torque element will trigger a left, right or linear motion or a lateral motion, while a cam follower following a second path coupled to the gear block 162 may allow longitudinal movement of the gear block. Taken together, they allow for cyclic, circular, or closed-loop movement of the gear piece and the abutment surface with a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, designing a specified movement pattern.

Referring now to FIG. 10A, a graphical representation of the gear block 162 interfacing the output member 150 is shown illustrating a variable offset that may be programmed or designed to the intersection between the gear block 162 and the output member 150. The intersection of the gear block 162 and the output member 150 may be biased positively (i.e., in the direction of rotation), negatively (i.e., in the opposite direction of rotation), or neutrally. While applicable to all interfacing surfaces, the variable bias is particularly important when the interfacing surfaces are gear teeth. The gear block 162 is shown in fig. 10A as having a forward bias such that the urging surface 164a of each interfacing element (e.g., gear teeth) is biased to positively engage the respective urging surface 150A of the interfacing element (e.g., gear teeth) of the output element 150 to transfer rotational movement from the gear block to the output element 150. In fig. 10B, the gear block 162 is shown with a negative bias such that the following face 164B of each interfacing element (e.g., gear teeth) is biased to engage the corresponding following face 150B of the interfacing element (e.g., gear teeth) of the output element 150. The negative bias induced by the gear block 162 may impart a slight tension on the output member 150 to reduce and/or eliminate backlash along the output member as the gear block 162 rotates the output member 150. For example, a gear block on one side of the output member may be in a positively biased configuration 126, while a gear block that is docked on the opposite side or offset from the positively biased gear block may be in a negatively biased configuration 127.

The gear block may also be configured in a neutral or balanced configuration 125 (fig. 10C) in which the gear block abutment elements (e.g., gear teeth) are neither positively nor negatively biased toward the abutment elements or surfaces of the output element 150. For example, when the gear block 162 is moved from the positively-biased configuration 126 (fig. 10A) to the negatively-biased configuration 127 (fig. 10B), the gear block 162 may be in an equilibrium and/or neutral configuration that reduces rotational tension or engagement of the gear block abutment surface with the output member abutment surface. Further, as the gear block transitions from the negative-biased configuration 127, repositions and/or returns to the positive-biased configuration 126, or vice versa, the gear block 162 may unload and/or disengage from the output member interfacing surface such that the gear block 162 may smoothly disengage (i.e., pull away and/or drop) from the output member 150.

The gear blocks 162 may be arranged such that they extend outwardly, e.g., an abutment surface 163 (e.g., a plurality of projections or teeth 166), the abutment surface 163 corresponds to a complementary abutment surface 154 (e.g., projections or gear teeth) configured on the abutment surface 153 of the output element 150, the abutment surface 153 extends outwardly from the central guide or central axis 106, or the abutment surface 163 may extend inwardly toward the central axis 106. The gear block 162 may also include a set of cam followers 194, the cam followers 194 may allow for traversal of the path of the cam member 130. The cam follower 194 may maintain contact with a path or groove formed in the planar surface of the cam member 130. It should be understood that the interface between the gear block 162 and the output member abutment surface 153 of the output member 150 of the present invention includes not only the preferred gear teeth shown, but also any complementary arrangement, such as pins and holes or even friction fit surfaces.

Referring now to fig. 10C, a side elevation view of the output member 150, gear block 162, torque rod 199 in the central bore 132 is shown. A shaft and/or other rotatable device may pass through the central aperture 132, the central aperture 132 being attached to an output element and/or cam element (not shown). The cam follower 194 may be coupled to the gear block 162 and the torque rod 199. The cam follower 194 may follow a particular path of both the torque rod and the gear block, generating forces to move them through their various positions, traveling from a path along the outer path of the cam element or the inner path of the gear block.

The illustrated gear block 162 is shown in various positions, beginning with the topmost gear block 162A shown in the transition/repositioning position 128, wherein the gear block 162A is fully disengaged from the abutment surface of the output member 150 and the abutment surface of the gear block 162A is fully disengaged. (note that the illustrated spacing of the gear block teeth is exaggerated to better illustrate the different offset configurations involved). Shown to gear block 162B in a reverse tension or negative bias arrangement 127. There may also be positions such as the positions of gear blocks 162C and/or 162D when they are in a neutral biased configuration. The gear block 162E is shown in a positively biased or engaged configuration 128, the configuration 128 may result in rotation of the output member 150. The gear block 162F is also shown in the forward biased or engaged configuration 126. Gear block 162G is also shown in one of the neutral offset configurations. There may also be three engaged positions that the gear block will be in: an engaged or positively biased position 126, a reverse tension or negatively biased position 127, and/or a center biased or equilibrium position 125. Further, the gear block may be in the transition/repositioning position 128, the transition/repositioning position 128 allowing the gear block 162 to disengage from the output member 150 and/or move away from the output member 150 to return to one of the engaged positions.

Further, it should be appreciated that the annular or closed loop cyclical movement of each gear block and cam element may be specifically programmed or designed to change the biasing configuration during a single cycle to enhance the efficiency of the gear block assembly. Furthermore, the amount or strength of the bias (whether positive, negative, or balanced) can be calibrated and changed throughout the cycle. For example, in one embodiment, when the gear block first engages the interfacing surface of the output element, the gear block is designed to engage the neutral bias to maximize the efficiency of the engagement process, then quickly transition to the forward bias to maximize power transfer, and then return to the neutral bias immediately prior to disengagement to assist in effective disengagement prior to transition/repositioning. A negative bias arrangement can be programmed into the cycle to minimize backlash.

As the cam followers coupled to the gear blocks follow the first or second path of the cam element, they allow the gear blocks to move in a radial direction or may be referred to as an up-down motion. The associated pivoting of the torque rods allows for rotational or angular movement of the gear block, which may be referred to as side-to-side movement. These movements may be corresponded or calculated together to generate a cyclic, circular, or closed-loop movement of the gear piece, which may have a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, which designs a specified movement pattern. In at least one embodiment of the present disclosure, the torque rods and/or gear blocks are coupled together in such a way that: the pivot points of the gear block and torque rod are allowed to produce movement of the gear block as caused by the cam follower traversing the path. In at least one example, angular movement of the gear block applies a torque to the output member 150.

Referring to fig. 9A, 9B, 10A, 10B and 10C, by varying the radius of each path or groove 136,137 on the cam member 130, the torque rod 199 drives its respective gear block 162 through a two-dimensional line in response to rotation of the cam member 130. Generally, the two-dimensional circuit 139 includes causing the gear block 162 to engage the output member 150 and move or rotate the output member 150a specified distance before disengaging from the output member 150, and returning the same specified distance to reengage the output member 150 and repeat the process. It should be understood that the two-dimensional line 139 shown in the drawings is not to scale and is somewhat enlarged to illustrate the general principles of the invention. For example, the distance A-B will typically be much less than the distance shown. The travel path or line 139 of each gear block 162 is controlled by adjusting the size and configuration of the torque rod 199, sleeve 189, gear block 162, and modifying the paths or grooves 136,137 formed in the cam member 130.

When adapted for use with the gearbox mechanism 120, a plurality of gear block assemblies 160 are arranged about the central axis 106 of the cam element 130. In at least one version, the cam member 130 may be coupled to a power source (not shown) via an output device (not shown). As the cam member 130 rotates, the respective torque rod 199 of each gear block assembly 160 and/or the cam follower member 194 of the gear block 162 maintain contact with the particular path or groove 136,137 formed in the planar surface 135 of the cam member 130. The variation in distance from the center of rotation of the different paths or grooves 136,137 of the cam member 130 causes the torque rod 199 and/or the sleeve 189 pivotally attached to the gear block 162 to act in unison to move its respective gear block 162 through the predetermined line of travel 139. Such a predetermined line of movement 139 of the gear block 160 may be precisely calibrated to meet specific engineering requirements. For example, torque ratios and speed reductions may be adjusted and controlled by adjusting the travel lines 139 of each gear block assembly 160.

With the gear block assembly 160 of the present invention, multiple embodiments of a gearbox mechanism are possible. All embodiments of a gearbox mechanism constructed in accordance with the present invention feature a plurality of gear block assemblies 160 arranged about the central axis 106 of the cam element 130, and may include an odd or even number of gear block assemblies 160. At least two, preferably three or more gear block assemblies are required for the gearbox mechanism of the present invention. The movement of the gear block assemblies 160 generally move in a rotational series with each other.

However, in a preferred embodiment of the present invention in which the plurality of gear block assemblies includes four or more even gear block assemblies 160, the gear block assemblies 160 disposed on opposite sides of the cam element 130 cooperatively engage and disengage the auxiliary or output gear element 150. For example, one embodiment of the gearbox mechanism 120 may feature four gear block assemblies 160. Similarly, another embodiment of the gearbox mechanism 120 may feature six gear block assemblies 160. This can be achieved by ensuring that the individual paths or grooves formed in the planar surface of the cam member are in phase with each other along the planar surface of the cam member.

Referring now to FIG. 11, a third embodiment of the gearbox mechanism 220 of the present invention is shown. In at least one version, the gearbox mechanism 220 can include a cam element 230, a main body 240, an output element 250, and a plurality of simplified gear block assemblies 260. In at least one example, output element 250 is retained within body 240 by retainer 212 (or retainer ring) via fasteners and/or couplings. The gear block assembly 280 may be disposed within the body 240 and interface the output member 250 and the cam member 230. In some examples, the cam member 230 interfaces the input hub and/or the ball bearing assembly 216 (which may also include a set of ball bearings, roller bearings, or ball bearing rings) through a friction or geometric fit. The central axis 206 may traverse the retainer 212, the output member 250, the body 240, the gear block assembly 260, the cam member 230, the input hub 214, and/or the ball bearing assembly 216.

The simplified gear block assembly 260 may include a torque rod 299, a gear block 262, a first cam follower 294A, and a second cam follower 294B. The cam followers 294A/294B follow a path (not shown) in the cam member 230 to generate a force on the torque rod 299 and/or the gear block 262 to generate pivotal movement of both the torque rod 299 and the gear block 262. In at least one version, the pivoting motion can be a generally square pivot path of the gear block 262. However, in other versions, the pivot path of the gear block 262 will generally be oval or circular.

The gearbox mechanism 220 may be coupled to an input or rotating device (not shown), such as an electric motor, an internal combustion engine, or any conventional power source that may be adapted to generate rotational power. The input or rotation device (not shown) may be rotationally coupled by gears, chains, belts, or magnetic fields. An output device (not shown) may be coupled to output element 250.

In at least one version, the central aperture 232 having the central axis 206 transverse thereto may be part of the gearbox mechanism 220. The gearbox mechanism 220 is configured about the central axis 206 and may include a body 240, the body 240 being stationary relative to the cam element 230, the output element 250, and/or the cam actuating gear block assembly 260. In at least one example, a spacer element (not shown) may also be used to ensure that movement of the output element 250, cam element 230, and/or cam actuation gear block assembly 260 is not impeded by the body 240 and/or

retainers

212, 214. The cam actuating gear block assemblies 260 are evenly spaced around the circumference of the output member 250. Each gear block assembly 260 includes a gear block 262, a torque rod 299, and at least one cam follower 294 that connects the gear block 262 to a planar surface of the cam element 230. The torque rod 299 and/or the gear block 262 may interact to pivotally attach and correspond to the intersection and/or engagement of the cam follower 294 with the cam element 230.

Referring now to fig. 12A, an exploded view of the body 240, output element 250 and retainer 212 is shown. In a preferred embodiment, the body 240 serves as a housing for a gear block assembly (not shown) and a cam member (not shown). The body 240 may be coupled to an input hub, rotating device, holder, plate, or other protective or fixed device on the cam side 241 via fasteners or coupling apertures 245. On the output side 243, the body 240 may be coupled to the retainer 212 via a retainer fastener or coupling aperture 245.

The retainer 212 may also interface the output member 250 and/or the output member outer circumferential surface via a retainer inner circumferential surface 257. In at least one version, the output member 250 can have an output member lip 259, and the output member lip 259 can support and/or engage the retainer 212 and/or the retainer inner circumferential surface 257. A portion of retainer 212 may interface output element 250 while the remainder of the retainer may interface body 240. Fasteners (not shown) may be coupled, fastened, and/or pass through the retainer fastener apertures 259 for fastening and/or coupling of the retainer 212 and the body 240.

In at least one version, the output member 250 may include a roller race 261 (or ball bearing track) to allow and/or assist in the rotation of the output member 250. Rotation of the output member 250 is achieved wherein the gear block 262 engages the output member abutment surface 253. In at least one example, rotation of the output member 250 can also be controlled by a reverse or tensioning engagement of the gear block 262 (i.e., a negatively biased configuration) to reduce and/or eliminate backlash, the gear block 262 not being in a driving or positively biased rotational engagement.

Referring now to fig. 12B, a perspective view of the body 240 is shown. In at least one version, the body 240 can provide a housing for a gear assembly (not shown). The gear block assembly (not shown) may rest and/or may be supported by the body retention surface 267. A gear block (not shown) may also be held and/or supported by body gear block abutment surface 269. A torque rod (not shown) may be supported and/or retained by the body torque rod abutment surface and/or the body torque rod void 277, the body torque rod void 277 being defined by the body 240. A torque rod post (not shown) may be configured to be retained and/or supported by the body torque rod void 277 to allow pivotal movement of the torque rod (not shown) to occur. The pivotal movement of the torque rod (not shown) may also coincide with the pivotal movement of the gear block (not shown) which allows for interfacing, engagement and/or rotation of the output member (not shown).

In at least one version, the body 240 may also have a spacer (not shown) of a gear assembly that may be secured to the body 240 via a spacer aperture 279 defined by the body 240. The spacer aperture 279 may be surrounded by a body spacer abutment surface 287. The cam abutment surface 289 may support a cam element (not shown) as the cam element engages a gear assembly (not shown), a rotatable or rotating device, and/or an input device. The body 240 may be coupled to an input hub, rotating device, holder, plate, or other protective or fixed device on the cam side 241 via fasteners or coupling apertures 244. In at least one example, an input hub, rotating device, holder, plate, or other protective or securing device may be used to secure and/or support a cam element (not shown).

Referring now to FIG. 12C, an exploded perspective view of the main body 240 and the gear block assembly 260 is shown. The output member 250 may rest and/or may be supported by the body 240 and may have a ball bearing assembly 207 (which may also include a set of ball bearings, roller bearings, or ball bearing rings), the ball bearing assembly 207 may be coaxial with a guide of the cam member (not shown) to allow freedom of movement of the cam member. Gear block 262 may have a gear block post 264, and gear block post 264 may interact with a torque rod aperture 297 to provide a pivot point for gear block 262 and/or torque rod 299. The torque rod 299 may also have a torque post 288, the torque post 288 interacting and/or engaging with the body torque rod void 277 and/or the gear block opening 211 to provide a pivot point for the torque rod 299 and/or the gear block 262. Cam follower 294 is also rotatably coupled to gear block post 264, and cam follower 294B is rotatably coupled to cam follower post 286 of torque rod 299. In at least one version, the torque rod 299, the gear block 262, and the

cam followers

294A,294B can be a cam actuated gear block assembly 260. In at least one example, spacers 246 can also be added to support and/or secure the torque rod 299 and/or the gear block 262.

Referring now to fig. 13, a perspective view of the cam member 230 is shown. The cam member 230 may have at least one flat 215A along the central axis 206. In at least one version, the cam member 230 can have two flat surfaces 215A/215B. In other versions, however, the cam member 230 may have three flat surfaces 215A/215B/215C. The cam element 230 may have a cam element guide 216, the cam element guide 216 allowing interaction of the cam element 230 with an output element guide and/or a ball bearing assembly (or set of ball bearings) (not shown). The cam element guide 216 may be coaxial with the output element guide and/or a ball bearing assembly (or set of ball bearings) (not shown), allowing for centered positioning along the central axis 206 via the cam element central aperture 232. An output element guide and/or ball bearing assembly (or ball bearing set) (not shown) may abut cam element guide circumferential surface 217 along the outside of cam element guide 216.

In at least one example, the first plane 215A can correspond to and/or include the first path 236. The first path 236 may allow traversal of a cam follower (not shown) to generate a pivoting or pivoting force on a torque rod and/or a gear block (not shown). As the cam follower (not shown) traverses the first path 236, the path may change direction to move a torque rod and/or gear block (not shown) coupled to the cam follower. Similarly, the second plane 215B may correspond to and/or include the second path 237. The second path 237 may allow traversal of a cam follower (not shown) to generate a pivoting or pivoting force on a torque rod and/or a gear block (not shown). As the cam follower (not shown) traverses the second path 237, the path may change direction to move a torque rod and/or gear block (not shown) coupled to the cam follower.

The gear block assembly (not shown) may rest and/or may be supported by the cam element support surface 218. In at least one example, the vertical or depth surface 219 of the cam element support surface 218 can also provide a surface of the gear block assembly to interface and/or engage therewith. Cam element spacer 221 may also be included in and/or coupled to cam element guide 216. In some examples, the cam element spacer 221 may be in the third plane 215C of the cam element 230.

Referring now to FIG. 14, a perspective view of the gear block assembly 260 interfacing the output member 250 is shown. The gear block assembly 260 may include a gear block 262, a torque rod 299, a first cam follower 294A, and/or a second cam follower 294B. In at least one version, the first cam follower 294A is coupled to the gear block 262 and the second cam follower 294B is coupled to the torque rod 299. As the cam followers 294A/294B traverse the first and second paths 236/237, they generate radial and angular movement of the torque rod 299 and/or the gear block 262. These longitudinal and lateral movements of the torque rod 299 and/or the gear block 262 allow and/or generate pivotal movements of the torque rod 299 and/or the gear block 262. In at least one example, the spacer 246 can be used to support and/or engage the torque rod 299.

The torque rod pivot post 288 and the gear block pivot void 297 interact to generate a force that causes the gear block 262 to engage and/or disengage the output member 250. In at least one example, the movement of the gear block 262 is a cyclical, annular, or closed-loop movement that may have a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, which designs a specified movement pattern.

For example, gear block abutment surface 283 may engage and/or disengage an output member abutment surface. The gear block 262 will move in a cyclic manner due to the pivotal movement of the torque rod 299 and the cam followers 294A/294B. In at least one version, the gear block can have four positions. The first position 228 (or transition position) allows the gear block to traverse or move to a new position to initiate a new selection of the output member 250. The second position 226 (or an engaged or positively biased moved position) allows the gear block to generate a rotational or pulling force 228 on the output member 250. The third position 225 (or neutral or equilibrium position) may allow the gear block 262 to be in a position to engage, rotate, or disengage an output element abutment surface, wherein no force is generated on the output element. The fourth position 227 (i.e., a reverse tension or negative bias configuration) allows tension to be applied to the output element 250 to assist in the prevention and/or elimination of backlash of the output element 250.

Cam element guide 216 may interface output element 250 via a rotational support, ball bearing assembly, and/or ball bearing set (not shown) that may be interposed between cam element guide circumferential surface 217 and output element circumferential surface 251.

As shown in the embodiment illustrated in the figures, a plurality of cam actuated gear block assemblies 260 transmit power from an input or rotating device (not shown) to the output member 250. In a preferred embodiment, each gear block assembly 280 includes a gear block 262 having an abutment surface 263 (e.g., a plurality of projections or teeth 266), the abutment surface 263 corresponding to a complementary output element abutment surface 254 (e.g., a projection or gear tooth) disposed on the outer circumferential surface 251 of the output element 250. The present invention includes not only the preferred gear teeth shown, but also any complementary arrangement, such as a pin and hole or even a friction fit surface.

Although output element 250 is shown as a single circular annulus, it should be understood that output element 250 may include two circular annuli separated by a spacer element (not shown). The output element 250 includes an aperture or bore 258 for attachment to an output shaft or power take off (not shown). Further, it should be understood that the inner circumference 251 of the output member 250 may also include a surface to interface with some other gear train.

Further, it should be appreciated that the gear block 282 may include a divider/alignment block (not shown) that divides the interface surface 263 into two separate sections. Variations of gear block 262 that characterize the alignment block (not shown) are particularly suitable for characterizing embodiments of output element 250 that include a circular annulus.

The gear block 262 of the present invention is specifically designed to allow a larger surface area (e.g., a larger number of gear teeth) to engage the output member 250 at any given time, thereby spreading the stresses associated therewith over a larger area. By substantially increasing the contact area between the gear block 282 and the output member 250 at any given time, the level of mechanical stress is significantly reduced. In addition, the gear block 262 assembly 260 of the present invention reduces backlash to zero and reduces the preload condition to create a tight connection between the power source and/or powered devices (not shown). This is an extremely desirable feature, especially for high vibration applications. Furthermore, because the stress distribution associated with the engagement of the gear block 262 with the output element 250 traverses a larger area, the gear block 282 may be manufactured from lighter materials, which are generally less expensive and easier to manufacture, with no reduction in reliability.

For example, typical stress results for spur gears are in the range of 450MPa to 600MPa, according to Hertz's contact theory. High grade steel is the most suitable material for handling such high stress levels. Other materials, such as low grade steel or aluminum, will deform under similar conditions. However, by distributing the stress across a large contact area by means of the gearbox mechanism according to the invention, the stress level under similar conditions can be reduced to about 20 MPa. These low stress levels allow the gearbox mechanism of the present invention to be manufactured from low grade steel, aluminum, or even plastic for the same application. By reducing its weight and size, the gearbox mechanism of the present invention is suitable for a wide range of applications that were previously impractical due to weight and space limitations.

The cam member 230 may be coupled to an input device, power source, or other rotating device (not shown) by a shaft, gears, belts, magnetic field, friction fit, or other coupling means. Power generated by an output device, power source, or other rotating device (not shown) may be transmitted to a shaft, gear, belt, magnetic field, friction fit, or other coupling means, which may cause the cam element 230 to rotate about the central axis 208. The cam assembly 230 includes a plurality of unique paths or grooves about its planar surface that each interface with the cam follower elements 294 of the gear block assembly 260 such that as the cam element 230 rotates, the movement of the gear block 282 is controlled in two dimensions according to particular design parameters. By varying the radius of the path or groove on the cam element 230, the gear block assembly 280 drives the respective gear block 262 through a two-dimensional line in response to rotation of the cam element 230. Broadly speaking, the two-dimensional circuit includes causing the gear block 262 to engage the output member 250 and move or rotate the output member 250 a specified distance before disengaging from the output member 250, and returning the specified distance to reengage the output member 150 and repeat the process. The path or path of travel of each gear block 262 is controlled by adjusting the size, height, length, and configuration of the torque rod 299, the gear block 262, and/or the cam follower 294, and/or altering the path or groove formed in the cam member 230.

For example, the pivotal connection may further include a torsion spring element (not shown) that biases the torsion bar 299 and/or the gear block 282 such that the cam follower element 294 maintains contact with the surfaces of its respective paths or grooves 236,237, the paths or grooves 136,137 being formed in the flat surface 235 of the cam element 230 throughout the rotational cycle of the cam element 230. Alternatively or additionally, an annular spring connecting all gear blocks 262 in the gear train may be used as a biasing mechanism according to the present invention.

The gear block assembly 260 is biased and/or fixed such that each cam follower 294 maintains contact with a surface of its respective path or groove formed in the cam element 230 throughout the rotational cycle of the cam element 230. For example, the cam follower 294A maintains contact with a surface of the first path 236 and the cam follower 294B maintains contact with a surface of the second path 237. Each path has a unique circumference whose radius changes during the course of the path.

The first path 236 has a first radius r1 at one portion of its course, the first radius r1 being greater than a second radius r2 at another portion of its course. This creates a unique undulating path for each path as the cam member 230 rotates. While the cam member 230 shown in the figures appears to be a single disc or unit having a plurality of pathways or grooves formed in the planar surface 235 of the cam member 230, it should be understood that the cam member 230 may also include a plurality of individual discs, each having a unique pathway formed in its planar or circumferential surface, which are mechanically coupled to one another to assemble the single cam assembly 230.

Referring to fig. 12A, 12B, 12C, 13 and 14, by varying the radius of each path or groove 236,237 on the cam member 230, the torque rod 299 drives its respective gear piece 262 through a two-dimensional line in response to rotation of the cam member 230. Generally, the two-dimensional line 239 includes causing the gear block 262 to engage the output member 250 and move or rotate the output member 250 a specified distance before disengaging the output member 250, and returning to the same specified distance to reengage the output member 250 and repeat the process. It should be understood that the two-dimensional line 239 shown in the drawings is not to scale and is somewhat exaggerated to illustrate the general principles of the invention. For example, the distance A-B will typically be much less than the distance shown. The travel path or track 239 of each gear block 262 is controlled by adjusting the size and configuration of the torque rod 299, gear block 262, and modifying the paths or grooves 236,237 formed in the cam member 230.

When adapted for use with the gearbox mechanism 220, a plurality of gear block assemblies 260 are arranged about the central axis 206 of the cam element 230. In at least one version, the cam member 230 may be coupled to a power source (not shown) via an output device (not shown). As the cam element 230 rotates, the respective torque rod 299 of each gear block assembly 260 and/or the cam follower element 294 of the gear block 262 maintains contact with the particular paths or grooves 236,237 formed in the planar surface 235 of the cam element 230. Variations in distance from the centers of rotation of the different paths or grooves 236,237 of the cam member 230 cause the torque rods 299 pivotally attached to the cam followers 194 to act in unison to move their respective gear blocks 262 through the predetermined line of movement 239. Such predetermined movement path 239 of the gear block 260 may be precisely calibrated to meet specific engineering requirements. For example, torque ratios and speed reductions may be adjusted and controlled by adjusting the travel line 239 for each gear block assembly 260.

With the gear block assembly 260 of the present invention, multiple embodiments of the gearbox mechanism are possible. All embodiments of a gearbox mechanism constructed in accordance with the present invention feature a plurality of gear block assemblies 260 arranged about the central axis 206 of the cam element 230, and may include an odd or even number of gear block assemblies 260. At least two, preferably three, gear block assemblies are required for the gearbox mechanism of the present invention. The movement of the gear block assemblies 260 typically move in a rotational series with one another.

However, in a preferred embodiment of the present invention in which the plurality of gear block assemblies includes four or more even gear block assemblies 260, the gear block assemblies 260 disposed on opposite sides of the cam element 230 cooperatively engage and disengage the auxiliary or output gear element 250. For example, one embodiment of the gearbox mechanism 220 may feature four gear block assemblies 260. Similarly, another embodiment of the gearbox mechanism 220 may feature six gear block assemblies 260. This can be achieved by ensuring that the individual paths or grooves formed in the planar surface of the cam member are in phase with each other along the planar surface of the cam member.

It will be apparent to those skilled in the art that an improved gearbox mechanism has been described herein. While the invention has been described by way of preferred embodiments, it will be apparent that other adaptations and modifications may be employed without departing from the spirit and scope thereof. The terms and expressions which have been employed herein are used as terms of description and not of limitation; and thus, it is not intended to exclude equivalents, but on the contrary, it is intended to cover any and all equivalents that may be employed without departing from the spirit and scope of the invention.

Claims

1. A gearbox mechanism comprising:

a cam assembly removably coupled to a rotating device, the cam assembly having a first pathway and a second pathway, the first pathway and the second pathway formed in a planar surface of the cam assembly and rotatable about a central axis when rotated by the rotating device;

an output element coaxially configured with the cam assembly removably coupled to an output device, the output element having an output element interface surface on a circumferential surface of the output element; and

at least one cam actuated gear block assembly comprising:

a gear block having a gear block interface surface;

a torque rod pivotally coupled to the gear block;

a first cam follower rotatably coupled to the gear block; and

a second cam follower rotatably coupled to the torque rod.

2. The gearbox mechanism of claim 1, wherein the cam assembly is removably coupled to the rotating device with a fastener.

3. The gearbox mechanism of claim 1, wherein the cam assembly is removably coupled to the rotating device via a friction or geometric connection.

4. A gearbox mechanism according to claim 1 wherein the rotating means is an electric motor.

5. A gearbox mechanism according to claim 1 wherein the rotational device is an energy generating device.

6. A gearbox mechanism according to claim 1 wherein the first path and the second path lie in the same plane.

7. The gearbox mechanism of claim 1 wherein the first path and the second path are in separate planes along the central axis.

8. The gearbox mechanism of claim 1 wherein the output element interface surface is a set of gear teeth.

9. The gearbox mechanism of claim 1 wherein the output element interface surface extends inwardly toward the central axis.

10. The gearbox mechanism of claim 1 wherein the output element interface surface extends outwardly away from the central axis.

11. A cam actuated gear block assembly comprising:

a gear block having a gear block interface surface;

a torque rod pivotally coupled to the gear block;

a first cam follower rotatably coupled to the gear block; and

a second cam follower rotatably coupled to the torque rod;

wherein the gear block has at least one pivot point;

wherein the torque rod has at least one pivot point.

12. The cam actuated gear block assembly of claim 11 wherein the gear block interface surface extends toward the central axis.

13. The cam actuated gear block assembly of claim 11 wherein the gear block interface surface extends outwardly from a central axis.

14. The cam actuated gear block assembly of claim 11, wherein the first cam follower follows a first path of the cam assembly.

15. The cam actuated gear block assembly of claim 11, wherein the second cam follower follows a second path of the cam assembly.

16. The cam actuated gear block assembly of claim 11 wherein the gear block pivots along the at least one pivot point based on the position of the first cam follower.

17. The cam actuated gear block assembly of claim 11, wherein the torque rod pivots along the at least one pivot point based on a position of the second cam follower.

18. The cam actuated gear block assembly of claim 11 wherein the gear block moves through a two dimensional line based on pivoting of the gear block and the torque rod.

19. The cam actuated gear block assembly of claim 18, wherein the two dimensional line is a cyclical movement having a rectangular, elliptical, circular, square, conical, oval, truncated circular pattern, or any combination thereof, designing a specified movement pattern.

20. The cam actuated gear block assembly of claim 11, wherein the gear block interface surface engages an output element interface surface during a rotational mode to generate movement of an output element.

21. A method of operating a gearbox mechanism, the method comprising:

rotating a cam assembly, the cam assembly having a first pathway and a second pathway;

a first cam follower coupled to a gear block along the first path;

a second cam follower coupled to a torque rod along the second path;

pivoting the gear block based on movement of the first cam follower;

pivoting the torque rod based on movement of the second cam follower;

moving the gear block in relation to pivoting of the torque rod and the gear block;

abutting an abutment surface of the gear block with an abutment surface of an output member; and

causing rotational movement of the output member based on the interfacing of the gear block and the output member.

22. The method of operation of claim 21, wherein the cam assembly is rotated by a rotating device.

23. The method of operation of claim 21, wherein the first path is generally circular.

24. The method of operation of claim 21, wherein the second path is generally circular.

25. The method of operation of claim 21, wherein the first path is closer to a central axis than the second path.

26. The method of operation of claim 21, wherein pivoting of the gear block and pivoting of the torque rod generates a pattern of movement of the gear block.

27. The method of operation of claim 21, wherein the docking occurs when the gear block moves generally outward from a central axis during pivoting thereof.

28. The method of operation of claim 21, wherein the docking occurs when the gear block moves generally toward a central axis during pivoting thereof.

29. The method of operation of claim 21, wherein causing rotational movement further comprises pushing the output element based on an interface of the gear block and the output element.

30. The operating method of claim 21, wherein causing rotational movement further comprises pulling the output element based on the interfacing of the gear block and the output element.