WO2021029867A1 - Mécanisme de boîte de vitesses à came axiale - Google Patents

Mécanisme de boîte de vitesses à came axiale Download PDF

Info

Publication number
WO2021029867A1
WO2021029867A1 PCT/US2019/046183 US2019046183W WO2021029867A1 WO 2021029867 A1 WO2021029867 A1 WO 2021029867A1 US 2019046183 W US2019046183 W US 2019046183W WO 2021029867 A1 WO2021029867 A1 WO 2021029867A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
gear block
pathway
gear
rocker arm
Prior art date
Application number
PCT/US2019/046183
Other languages
English (en)
Inventor
Carlos A. Hoefken
Original Assignee
Motus Labs, LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US16/537,218 external-priority patent/US10626964B2/en
Application filed by Motus Labs, LLC filed Critical Motus Labs, LLC
Publication of WO2021029867A1 publication Critical patent/WO2021029867A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H31/00—Other gearings with freewheeling members or other intermittently driving members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
    • F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams

Definitions

  • the present invention relates to a universal gearbox mechanism featuring cam- actuated gear block assemblies that periodically engage the output gear causing power transfer. It has particular, but not exclusive, application for use in servomotor assemblies.
  • a transmission system may be defined as an assembly of parts including a speed-changing gear mechanism and an output shaft by which power is transmitted from the power source (e.g ., electric motor) to an output shaft.
  • power source e.g ., electric motor
  • transmission refers simply to the gearbox that uses gears and gear trains to provide speed and torque conversions from a power source to another device.
  • Gearboxes have been used for many years and they have many different applications.
  • conventional gearboxes comprise four main elements: power source; drive train; housing and output means.
  • the power source places force and motion into the drive train.
  • the power source may be a motor connected to the drive train through suitable gearing, such as a spur, bevel, helical or worm gear.
  • the drive train enables the manipulation of output motion and force with respect to the input motion and force provided by the power source.
  • the drive train typically comprises a plurality of gears of varying parameters such as different sizes, number of teeth, tooth type and usage, for example spur gears, helical gears, worm gears and/or internal or externally toothed gears.
  • the gearbox housing is the means which retains the internal workings of the gearbox in the correct manner. For example, it allows the power source, drive train and output means to be held in the correct relationship for the desired operation of the gearbox.
  • the output means is associated with the drive train and allows the force and motion from the drive train to be applied for an application. Usually, the output means exits the gearbox housing.
  • the output means typically can be connected to a body whereby the resultant output motion and force from the drive train is transmitted via the output means (e.g., an output shaft) to the body to impart the output mean’s motion and force upon the body.
  • the output means can impart the motion and force output from the drive train to the gearbox housing whereby the output means is held sufficiently as to allow the gearbox housing to rotate.
  • Rotating power sources typically operate at higher rotational speeds than the devices that will use that power. Consequently, gearboxes not only transmit power but also convert speed into torque.
  • the torque ratio of a gear train also known as its mechanical advantage, is determined by the gear ratio. The energy generated from any power source has to go through the internal components of the gearbox in the form of stresses or mechanical pressure on the gear elements.
  • a critical aspect in any gearbox design comprises engineering the proper contact between the intermeshing gear elements. These contacts are typically points or lines on the gear teeth where the force concentrates. Because the area of contact points or lines in conventional gear trains is typically very low and the amount of power transmitted is considerable, the resultant stress along the points or lines of contact is in all cases very high. For this reason, designers of gearbox devices typically concentrate a substantial portion of their engineering efforts in creating as large a line of contact as possible or create as many simultaneous points of contacts between the two intermeshed gears in order to reduce the resultant stress experienced by the respective teeth of each gear.
  • backlash is the striking back of connected wheels in a piece of mechanism when pressure is applied.
  • backlash (sometimes called lash or play) is clearance between mating components, or the amount of lost motion due to clearance or slackness when movement is reversed and contact is re-established.
  • backlash is the amount of clearance between mated gear teeth.
  • backlash should be zero, but in actual practice some backlash is typically allowed to prevent jamming. It is unavoidable for nearly all reversing mechanical couplings, although its effects can be negated. Depending on the application it may or may not be desirable. Typical reasons for requiring backlash include allowing for lubrication, manufacturing errors, deflection under load and thermal expansion. Nonetheless, low backlash or even zero backlash is required in many applications to increase precision and to avoid shocks or vibrations. Consequently, zero backlash gear train devices are in many cases expensive, short lived and relatively heavy. Weight and size are yet another consideration in the design of gearboxes. The concentration of the aforementioned stresses on points or lines of contact in the intermeshed gear trains necessitates the selection of materials that are able to resist those forces and stresses. However, those materials are oftentimes relatively heavy, hard and difficult to manufacture.
  • each gear block assembly includes a gear block having a surface that periodically interfaces with a secondary or output gear element.
  • the interface surface comprises a plurality of projections or teeth which correspond to complementary projections or gear teeth on the output gear element.
  • Each gear block assembly further includes a plurality of linkage assemblies, which connect or link the gear block to a cam assembly, which in turn is connected to a power source.
  • the cam assembly includes about its circumference a unique pathway or groove for each linkage assembly of a particular gear block assembly so that the movement of the gear block may be controlled in two dimensions in accordance with a certain design parameter.
  • the gear block assembly is designed to drive its respective gear block through a two-dimensional circuit in response to rotation of the cam assembly.
  • the two-dimensional circuit includes urging the gear block to engage a secondary or output gear element and move or rotate a specified quantum distance prior to disengaging from the output gear element, and returning back the specified quantum distance to again reengage the secondary or output gear element once again and repeat the process.
  • the travel path or circuit of each gear block is controlled by adjusting the length and configuration of the various linkage assemblies and altering the pathways or grooves formed in the cam assembly.
  • a plurality of gear block assemblies are configured about a central axis of the cam assembly.
  • the cam assembly is rotatively coupled with a power source.
  • the cam follower elements of the respective linkage assemblies of each gear block assembly maintain contact with a particular pathway or groove formed in the circumferential surface of the cam assembly.
  • the variance of distance from the center of rotation of the different pathways or grooves of the cam assembly causes the respective linkage assemblies to work in concert to move their respective gear block through a predetermined circuit of movement.
  • This predetermined circuit of movement of the gear block can be precisely calibrated to meet specific engineering requirements.
  • the torque ratio and speed reduction may be regulated and controlled by adjusting the circuit of movement of each gear block assembly.
  • a another embodiment of a gearbox mechanism of the present invention may include a main body, an output element, and a plurality of simplified gear block assemblies. Additionally, the gearbox mechanism may have a retainer that interfaces with the main body and the output element.
  • Each simplified gear block assembly includes a gear block, a torque lever, cam follower(s), and/or socket (or a portion of a socket).
  • the cam actuated gear block assemblies are configured about a central axis. The rotational force on the cam element allows for a driving or rotative force on the cam actuated gear block assemblies.
  • the torque lever also has a set of cam followers allowing for the following of a specified path formed along a planar surface of the cam element.
  • the cam element includes at least one unique pathway or groove that interfaces with the cam follower of gear block or torque lever so that as the cam element rotates, the movement of the gear block or torque lever is controlled in two dimensions in accordance with at least one certain design parameter.
  • the cam actuated gear block assemblies drive respective gear block(s) through a two-dimensional circuit in response to rotation of the cam element.
  • the two- dimensional circuit includes urging the gear block to engage the output element and move and/or rotate the output element a specified distance prior to disengaging from the output element, and returning back the specified distance to again reengage the output element once again, and repeat the process.
  • the travel path or circuit of each gear block is controlled by adjusting the length, width, height, and/or size of the respective gear block and/or torque lever and/or altering the pathways or grooves formed in the cam element.
  • Another embodiment of the gearbox mechanism of the present invention may include a cam element, a main body and output element and a plurality of simplified gear block assemblies.
  • the output element is retained within the main body by a retainer.
  • the gear block assemblies are placed within the main body and interface with the output element and cam element.
  • the gear block assemblies can include a rocker arm, a gear block, a cam follower, and a pathway tracker.
  • the cam follower and/or pathway tracker follow pathways in the cam element and/or an axial cam to generate forces on the rocker arm and/or the gear block(s) generating a pivoting motion for the both the rocker arm and the gear block(s).
  • the pivoting motion can be a generally square pivot path for the gear block(s). While in other versions, the pivot path of the gear block(s) will generally be oval or circular.
  • a central aperture aligned with a central axis may be a part of the gearbox mechanism.
  • Each gear block assembly includes a gear block, a rocker arm, and at least one cam follower, which connect the gear block to the planar surface of the cam element.
  • the rocker arm, and/or gear block can interact to be pivotally attached, and correspond to the interaction and/or engagement of the cam follower(s) with the cam element.
  • the rotation of the output element may also be controlled through a reverse or tension engagement (z.e., negative bias) of gear block(s) that are not in a driving or positive bias rotational engagement in order to reduce and/or element backlash.
  • the main body provides a housing for the gear assemblies.
  • the gear block assemblies rest and/or are supported by the main body retaining surface.
  • the gear block(s) may also be retained and/or supported by the main body gear block interface surface.
  • the rocker arm(s) may also be supported and/or retained by the main body interface surface, and/or the main body rocker arm void as defined by the main body.
  • the pivoting motion of the rocker arm can also coincide with a pivoting motion of the gear block that allows for the interfacing, engaging, and/or rotating of an output element.
  • the plurality of gear block assemblies configured about the central axis of the cam assembly can comprise either an odd or even number of gear block assemblies. At least two, and preferably three gear block assemblies are required for a gearbox mechanism of the present invention.
  • the movement of the gear block assemblies typically move in a rotational series to one another. At least one gear block assembly is always engaged with the output gear element at any particular instance in time. Preferably, only one gear block assembly is disengaged with the output gear element at any particular instance in time.
  • the plurality of gear block assemblies comprises four or more even-numbered gear block assemblies, the gear block assemblies configured on opposing sides of the cam assembly engage and disengage in unison from the secondary or output gear element.
  • the design of the gear block assemblies of the present invention enable a greater number of gear teeth to engage the output gear at any given time, thereby spreading the stresses associated therein across a greater area. By dramatically increasing the contact area between the gear block and the output gear at any given time the mechanical stress level is significantly decreased.
  • the gear block assemblies of the present invention reduce backlash to zero and even preloaded conditions to create a tight connection between the power source and the powered device. This is an extremely desirable feature especially for high vibration applications. By reducing backlash to zero or preloaded condition, the mechanical impedance may also be reduced at a broad range of high vibration frequencies.
  • the gear block mechanism may be manufactured of lighter weight, more flexible materials, which are less expensive and easier to manufacture, with no degradation in reliability. Indeed, using flexible materials further reduces the mechanical impedance at low frequencies. By reducing its weight and size, the gearbox mechanism of the present invention is adaptable to a broad range of applications that were previously impractical because of weight and space limitations.
  • FIG. 1A is a perspective view of a first embodiment of a gearbox mechanism attached to a power source as previously disclosed in co-pending application Ser.
  • FIG. IB is a side elevation view thereof
  • FIG. 2 is an end view thereof with the outer stationary plate removed
  • FIG. 3 is a perspective view of a second embodiment of a gearbox mechanism as previously disclosed in co-pending application Ser. No. 16/266,629, the disclosure of which is fully incorporated herein by reference;
  • FIG. 4 is an illustration of an exploded perspective view of a third embodiment of a gearbox mechanism of the present invention.
  • FIG. 5 is an illustration of a perspective view of an output element, cam element, and gear block assembly thereof
  • FIG. 6 is an illustration of an alternative perspective view of a hub, gear block assemblies, and output element thereof;
  • FIG. 7 is an illustration of a side view a hub, gear block assemblies, and output element thereof
  • FIG. 8 is a perspective view illustration of a main body of the gearbox mechanism shown in Fig. 4;
  • FIG. 9 is a perspective view illustration of an axial cam of the gearbox mechanism shown in Fig. 4;
  • FIG. 10 is an alternative perspective view of the axial cam thereof
  • FIG. 11 is an illustration in perspective view of an output element of the gearbox mechanism shown in Fig. 4;
  • FIG. 12 is a perspective view illustration of a cam element of the gearbox mechanism shown in Fig. 4;
  • FIG. 13 is a front perspective view of a gear block of the gearbox mechanism shown in Fig. 4.
  • FIG. 14 is a rear perspective view of the gear block thereof;
  • FIG. 15 is a top perspective view of a rocker arm of the gearbox mechanism shown in Fig. 4;
  • FIG. 16 is a bottom perspective view of the rocker arm thereof.
  • FIG. 17 is an illustration of an exploded perspective view of a fourth embodiment of a gearbox mechanism of the present invention.
  • FIG. 18 is a perspective view illustration of a cam element and gear block assembly of the gearbox mechanism shown in Fig. 17;
  • FIG. 19 is an illustration of a perspective view of the cam element therof;
  • FIG. 20 is an illustration of an alternative perspective view of the cam element thereof;
  • FIG. 21 is a sectional view illustration of the cam element and gear block assembly of the gearbox mechanism shown in Fig. 17;
  • FIG. 22 is another sectional view illustration of the cam element and gear block assembly of the gearbox mechanism shown in Fig. 17;
  • FIG. 23 is a perspective view illustration of a gear block assembly of the gearbox mechanism shown in Fig. 17;
  • FIG. 24 is a front perspective view of a gear block of the gear block assembly shown in Fig. 23;
  • FIG. 25 is a rear perspective view of the gear block thereof.
  • FIG. 26 is a front side view of a rocker arm of the gear block assembly shown in Fig. 23;
  • FIG. 27 is a rear side view of the rocker arm thereof;
  • FIG. 28 is a perspective view of a rocker block of the gear block assembly shown in Fig. 23;
  • FIG. 29 is a perspective view of a rocker pin of the gear block assembly shown in Fig. 23.
  • FIG. 30 is a perspective view of a main body of the gearbox mechanism shown in Fig. 17.
  • the machine 10 includes a power source or actuator 2, which includes an output device (not illustrated) that transmits the power generated by the power source 2. While the embodiment shown in the Figure generally depicts the power source 2 as an electric motor and the output device as an output shaft of the electric motor, it is understood that there are numerous possible embodiments. For example, output device need not be directly connected to the power source 2 but may be rotatively coupled by means of gears, chains, belts or magnetic fields. Likewise, the power source 2 may comprise an electric motor, an internal combustion engine, or any conventional power source that can be adapted to generate rotative power in an output device. Moreover, the power source 2 may also comprise the output gear of a preceding gear train mechanism.
  • each gear block assembly 60 includes a gear block 62 having an interface surface 63 (e.g ., a plurality of projections or teeth 66) which correspond to a complementary interface surface 54 (e.g., projections or gear teeth) configured on an inner circumferential surface 53 of the annular secondary or output gear element 50.
  • interface surface 63 e.g ., a plurality of projections or teeth 66
  • complementary interface surface 54 e.g., projections or gear teeth
  • the interface between the gear block 62 and the inner circumferential surface 53 of the output gear element 50 of the present invention comprises not only the preferred gear teeth as depicted, but also any complementary arrangement such as pins and holes or even friction fit surfaces.
  • annular output or power gear element 50 is depicted as two circular rings held apart by spacer elements 55, it is understood that the output or power gear element 50 may comprise a single circular ring.
  • the output or power gear element 50 includes apertures or holes 58 for attaching to an output shaft or power takeoff (not shown).
  • the outer circumference 51 of the output or power gear element 50 may also comprise a surface to interface with some other gear train mechanism.
  • the gear blocks 62 of the present invention are specifically designed to enable a greater surface area (e.g, greater number of gear teeth) to engage the output gear 50 at any given time, thereby spreading the stresses associated therein across a greater area.
  • a greater surface area e.g, greater number of gear teeth
  • the gear block 62 assemblies of the present invention reduce backlash to zero and even preloaded conditions 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.
  • the gear block 62 may be manufactured of lighter weight materials, which are typically less expensive and easier to manufacture, with no degradation in reliability.
  • the cam assembly 30 is coupled to the power source 2 by means of the output device or power shaft (not illustrated). Thus, power generated by the power source 2 is transferred to the power shaft, which causes the cam assembly 30 to rotate about the central axis 6.
  • the cam assembly 30 includes about its circumferential surface 34 a plurality of unique pathways or grooves which each interface with the cam follower element of a single linkage assembly of each gear block assembly 60 so that as the cam assembly 30 rotates, the movement of the gear block 62 is controlled in two dimensions in accordance with a certain design parameter. By varying the radius of the pathway or grooves on the cam assembly 30 the linkage assemblies of the gear block assembly 60 drive respective gear block 62 through a two-dimensional circuit in response to rotation of the cam assembly 30.
  • the two-dimensional circuit includes urging the gear block to engage the output gear element 50 and move or rotate the output gear element 50 a specified quantum distance prior to disengaging from the output gear element 50, and returning back the specified quantum distance to again reengage the output gear element 50 once again and repeat the process.
  • the travel path or circuit of each gear block 62 is controlled by adjusting the length and configuration of the various linkage assemblies and altering the pathways or grooves formed in the cam assembly 30.
  • each linkage mechanism includes two pivotally coupled connector arms.
  • An upper connector arm includes a first pivot point that is pivotally coupled to its respective gear block 62 and a second pivot point pivotally coupled to a lower connector arm.
  • the lower connector arm includes a cam follower element at its distal end that maintains contact with its respective pathway or groove formed in the cam assembly 30.
  • the lower connector arm further includes a pivot point having a fixed axis of rotation relative to the central axis 6 of rotation of the cam assembly 30.
  • Fig. 3 depicts a perspective view of the gear block assemblies 260 interfacing with an output element 250 of the gearbox mechanism.
  • the gear block assemblies 260 can include a gear block 262, a torque lever 299, a first cam follower 294A, and/or a second cam follower 294B.
  • the first cam follower 294A is coupled to the gear block 262
  • the second cam follower 294B is coupled to the torque lever 299.
  • a spacer 246 can be utilized to support and/or engage the torque lever 299.
  • the torque lever pivot post 288 and the gear block pivot void 297 interact to generate forces that cause the gear block 262 to engage and/or disengage from the output element 250.
  • the movement of a gear block 262, in at least one example, 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, design specified pattern of movement.
  • a gear block interface surface 263 can engage and/or disengage from an output element interface surface.
  • the gear block 262 will move in a cyclical manner as a result of the pivot movements of the torque lever 299 and cam followers 294A/294B.
  • the gear block can have four positions.
  • a first position 228 (or transitioning position) allows for the gear block to traverse or move to a new position to begin a new rotation of the output element 250.
  • the second position 226 (or engaged or positive bias movement position) allows for the gear block to generate a rotational or pulling force 228 on the output element 250.
  • the third position 225 may allow the gear block 262 to be in a position to engage, rotate, or disengage from the output element interface surface with no forces generated on the output element.
  • the fourth position 227 i.e ., reverse tension or negative bias configuration
  • the cam element guide 216 can be interfaced with the output element 250 through a rotational support, ball bearing assembly, and/or set of ball bearings (not illustrated) that can be placed between the cam element guide circumferential surface 217 and the output element circumferential surface 251.
  • each gear block assembly 260 transfers power from an input or rotating device (not illustrated) to an output element 250.
  • each gear block assembly 260 includes a gear block 262 having an interface surface 263 (e.g ., a plurality of projections or teeth 266) which correspond to a complementary output element interface surface 254 (e.g., projections or gear teeth) configured on an outer circumferential surface 251 of the output element 250.
  • the present invention comprises not only the preferred gear teeth as depicted, but also any complementary arrangement such as pins and holes or even friction fit surfaces.
  • the output element 250 is depicted as a single circular ring, it is understood that the output element 250 may comprise two circular rings held apart by spacer elements (not illustrated).
  • the output element 250 includes apertures or holes 258 for attaching to an output shaft or power takeoff (not illustrated).
  • the inner circumference 251 of the output element 250 may also comprise a surface to interface with some other gear train mechanism.
  • the gear block 262 may include a divider/alignment block (not illustrated) dividing the interface surface 263 into two separate sections.
  • the variant of the gear block 262 featuring the alignment block (not illustrated) is particularly suitable to embodiments which feature output elements 250 comprised of circular rings.
  • the gear block 262 can have a gear block post 264 that may interact with a torque lever aperture 297 to provide a pivot point for the gear block 262 and/or torque lever 299.
  • the gear blocks 262 of the present invention are specifically designed to enable a greater surface area (e.g ., greater number of gear teeth) to engage the output element 250 at any given time, thereby spreading the stresses associated therein across a greater area.
  • the gear block 262 assemblies 260 of the present invention reduce backlash to zero and even preloaded conditions to create a tight connection between the power source and/or the powered device (not illustrated). This is an extremely desirable feature especially for high vibration applications.
  • the gear block 262 may be manufactured of lighter-weight materials, which are typically less expensive and easier to manufacture, with no degradation in reliability.
  • the cam element 230 can be coupled to an input device, power source, or other rotating device (not illustrated) by means of a shaft, gears, belts, magnetic fields, friction fit, or other means of coupling. Power generated by an input device, power source, or other rotating device (not illustrated) can be transferred to a shaft, gears, belts, magnetic fields, friction fit, or other means of coupling, which causes the cam element 230 to rotate about the central axis 206.
  • the cam assembly 230 includes along its planar surface a plurality of unique pathways or grooves which each interface with the cam follower(s) 294 of a gear block assembly 260 so that as the cam element 230 rotates, the movement of the gear block 262 is controlled in two dimensions in accordance with a certain design parameter.
  • the gear block assemblies 260 drive respective gear block(s) 262 through a two-dimensional circuit in response to rotation of the cam element 230.
  • the two- dimensional circuit includes urging the gear block 262 to engage the output element 250 and move or rotate the output element 250 a specified distance prior to disengaging from the output element 250, and returning back the specified distance to again reengage the output element 250 once again and repeat the process.
  • the travel path or circuit of each gear block 262 is controlled by adjusting the size, height, length and configuration of the torque lever(s) 299, gear block(s) 262, and/or cam follower(s) 294 and altering the pathways or grooves formed in the cam element 230.
  • the pivotal connections may further include torsional spring elements (not shown) which bias the torque lever 299, and/or gear block 262 so that the cam follower 294 maintains contact with the surface of its respective pathway or groove 236, 237 formed in the planar surface 235 of the cam element 230 throughout the rotation cycle of the cam element 230.
  • the planar surface of the cam assembly 230 is substantially perpendicular to the axis of rotation of the cam assembly 230.
  • a ring spring connecting all of the gear blocks 262 in a gear train may be used as a biasing mechanism in accordance with the present invention.
  • each cam follower 294 maintains contact with the surface of its respective pathway or groove formed in the cam element 230 throughout the rotation cycle of the cam element 230.
  • cam follower 294A maintains contact with the surface of a first pathway 236, and cam follow 294B maintains contact with the surface of a second pathway 237.
  • Each pathway has a unique circumference, the radius of which varies over the course of the pathway.
  • each pathway or groove 236, 237 on the cam element 230 By varying the radius of each pathway or groove 236, 237 on the cam element 230, torque lever(s) 299 drive their respective gear block(s) 262 through a two- dimensional circuit in response to rotation of the cam element 230.
  • the two- dimensional circuit 239 includes urging the gear block 262 to engage the output element 250 and move or rotate the output element 250 a specified distance prior to disengaging form the output element 250, and returning back the same specified distance to again reengage the output element 250 once again and repeat the process.
  • the two-dimensional circuit 239 depicted in the drawings is not to scale and is somewhat exaggerated to illustrate the general principal of the invention. For example, the distance A-B would typically be much smaller than depicted.
  • the travel path or circuit 239 of each gear block 262 is controlled by adjusting the size and configuration of the torque lever(s) 299, gear block(s) 262, and/or altering the pathways or grooves 236, 237 formed in the cam element
  • a plurality of gear block assemblies 260 are configured about the central axis 206 of the cam element 230.
  • the cam element 230 in at least one version, may be coupled to a power source (not illustrated) by an output device (not illustrated).
  • the cam follower(s) 294 of the respective torque lever(s) 299 and/or gear block(s) 262 of each gear block assembly 260 maintain contact with a particular pathway or groove 236, 237 formed in the planar surface 235 of the cam element 230.
  • the variance of distance from the center of rotation of the different pathways or grooves 236, 237 of the cam element 230 causes the torque lever(s) 299 pivotally attached to a cam follower(s) 194 to work in concert to move their respective gear block(s) 262 through a predetermined circuit of movement 239.
  • This predetermined circuit of movement 239 of the gear block 260 can be precisely calibrated to meet specific engineering requirements.
  • the torque ratio and speed reduction may be regulated and controlled by adjusting the circuit of movement 239 of each gear block assembly 260.
  • a third embodiment of a gearbox mechanism 320 of the present invention is depicted.
  • the gearbox mechanism 320 may be powered and/or rotated by a power source or actuator (as shown in Figs. 1 A and IB), that is transmitted to an output device (not illustrated) by the gearbox mechanism 320.
  • the power source can be an electric motor, combustion engine, water activated source, wind turbine, or other possible embodiments.
  • the power source or actuator, as well as the output device (not illustrated) may be rotatively coupled by means of gears, chains, belts, or magnetic fields.
  • the gearbox mechanism 320 can be configured about a central axis 306.
  • the central axis 306 can pass through a central aperture of the main body 340, the output element 350, cam element 330, axial cam 331, and hub 314.
  • the main body 340 and the hub 314 may be coupled together through fasteners 347.
  • the fasteners 347 may be screws, bolts, all thread, compression fit devices, or other means for fastening two components together in a fixed or secure manner.
  • a cam assembly is created by coupling together the axial cam 331 and cam element 330 using fasteners like fasteners 302, wherein the axial cam 331 and cam element 330 interact with gear block assemblies.
  • the fasteners 302 may be screws, bolts, all thread, compression fit devices, or other means for fastening axial cam 331 and cam element 330 together in a fixed or secure manner.
  • the gearbox mechanism 320 further includes a plurality of gear block assemblies 360.
  • Each gear block assembly 360 can include a rocker arm 399 (rocker arms 399A, 399B, 399C, 399D, 399E, 399F, and 399G collectively referred to as rocker arm(s) 399) that are coupled with the gear block(s) 362 (gear blocks 362A, 362B, 362C, 362D, 362E, 362F, and 362G may be referred to collectively as gear block(s) 362).
  • the gear blocks 362 of the present invention are specifically designed to enable a greater surface area (e.g ., greater number of gear teeth) to engage the output element 350 at any given time, thereby spreading the stresses associated therein across a greater area.
  • the gear block(s) 362 may have a pathway tracker that can, individually or in combination with a pathway follower element, track and/or follow a pathway formed into the axial cam 331.
  • the pathway follower element can include a ball bearing, roller bearing, or other mechanism or means for reducing friction.
  • the gear block assemblies 360 of the present invention reduce backlash to zero and even preloaded conditions to create a tight connection between the power source and/or the powered device (not illustrated). This is an extremely desirable feature especially for high vibration applications.
  • the gear block 362 may be manufactured of lighter-weight materials, which are typically less expensive and easier to manufacture, with no degradation in reliability.
  • gearbox mechanism 320 of the present invention is adaptable to a broad range of applications that were previously impractical because of weight and space limitations.
  • the rocker arm 399 can also have a cam follower 394 allowing for the following of a specified pathway(s) formed in or along a planar surface 334 of the cam element 330. While the planar surface 334 in Figs. 4, 5, and 6, is depicted on the side of the cam element 330 facing the axial cam 331, it should be understood that the planar surface, into which pathway(s) 336 may be formed, may either face the axial cam 331 or face away from the axial cam 331.
  • the gearbox mechanism 320 can also include a hub 314 and/or a ball bearing assembly 307 that allows the cam element 330 to rotate freely based upon an input device such as a shaft or rotatable elements such as a set of other gearing, belts, levers, magnetic or electrical fields, etc.
  • an input device such as a shaft or rotatable elements such as a set of other gearing, belts, levers, magnetic or electrical fields, etc.
  • the interface surface 363 of each gear block 362 can engage with the output element interface surface 353 of the output element 350.
  • the gear blocks 362 are articulated by an associated movement of the rocker arm 399.
  • the cam element 330 includes at least one unique pathway or groove 336 that interfaces with the cam follower 394 of each rocker arm 399 so that as the cam element 330 rotates, the movement of the gear block 362 and/or rocker arm 399 is controlled in two dimensions in accordance with at least one certain design parameter.
  • the gear block assemblies 360 drive their respective gear block(s) 362 through a two-dimensional circuit in response to rotation of the cam element 330.
  • the two-dimensional circuit includes urging the gear block(s) 362 to engage the interface surface 353 of the output element 350 and move and/or rotate the output element 350 a specified distance prior to disengaging from the output element 350, and returning back the specified distance to again reengage the output element 350 once again, and repeat the process.
  • the travel path or circuit of each gear block 362 is controlled by adjusting the length, width, height, and/or size of the respective gear block and/or rocker arm and/or by altering the pathways or grooves 336 formed in the cam element 330.
  • the rocker arm 399 is pivoted around a specific pivot point by the cam follower 394, which traverses the pathway 336 formed in the cam element 330.
  • the gear blocks 362 may also have a pathway tracker and/or pathway cam follower that follows a separate path along the axial cam 331 that also triggers an actuation point for the gear block(s) 362.
  • the movement of a gear block 362, in at least one example, 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, design specified pattern of movement.
  • FIG. 5 a perspective view is depicted of the cam element 330, output element 350, along with the rocker arm 399, cam follower 394, and gear block 362.
  • the axial cam 331 is also depicted; however, in this view, it is not easily seen.
  • a central axis 306 can pass through the central aperture 332 at the center of the cam element 330, axial cam 331, and/or output element 350.
  • the cam element 330 interacts with the rocker arm 399 along with the gear block 362 to rotate and cause a movement of the gear block 362 to have a cyclical, annular or closed loop movement having a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, design specified pattern of movement based upon the pathways in the cam element 330 that may allow a cam follower 394 attached to the rocker arm 399 to traverse along the pathway 336 and generate movement of the gear block(s) 362.
  • Each of the cam followers 394 can each have a separate path or, in some embodiments, may have a single path that each follow at a different position simultaneously.
  • the gear block(s) 362 can be pivotally connected to the rocker arm 399.
  • a ring spring connecting all of the gear blocks 362 in a gear train may be used as a biasing mechanism in accordance with the present invention.
  • the cam element will have a single pathway, however there may be multiple pathways formed in the cam element 330 that can be in the same plane where they are parallel paths, or pathways of different distances from the central axis 306, or the pathways can be in separate planes stacked in the direction of the central axis 306.
  • the pathway 336 formed in cam element 330 allows for movement and rotation of the gear blocks 362 causing the interface surfaces of the gear blocks 362 to engage, interface and/or interact with the output element 350.
  • Cam follower(s) 394 maintain contact with the surface of their respective pathways or grooves formed in the cam element 330. While the cam element 330 depicted in the Figures, appears to be a single disc or unit having at least one pathway or groove 336 formed in the planar surface 334 of the cam element 330, it is understood that the cam element 330 may also comprise a plurality of separate discs, each having a unique pathway formed in its planar surface ( e.g ., 334), which are mechanically coupled to one another to assemble a single cam assembly 330.
  • the planar surface 334 of the cam assembly 330 is substantially perpendicular to the axis of rotation of the cam assembly 330. While the planar surface 334 depicted in Fig. 5 is shown as being on the side of the cam element 330 facing the axial cam 331, it should be understood that the planar surface, into which pathway(s) 336 is formed, may either face the axial cam 331 or face away from the axial cam 331.
  • rocker arm 399 pivots about its pivot point to compensate and maintain contact between rocker arm 399 and the main body (not illustrated). This pivoting or moving of the rocker arm 399 about its pivot point induces movement in the pivotal connection with the gear block 362.
  • Each rocker arm 399 acts independently of the other rocker arm(s) 399 due to the cam follower(s) 394 of each rocker arm 399 following and/or traversing the pathway 336 formed in the planar surface 334 of the cam element 330 at their respective distinct points.
  • the rocker arm 399 can pivot at a specific point causing the gear block to pivot and/or rotate around a specific point.
  • the pivot point of the rocker arm 399 will trigger a left, right, in or out, or a rotational motion to the gear block 362.
  • the three-dimensional circuit may have a first portion 339A includes urging the gear block 362 to biasing the output element 350 and move or rotate the output element 350 a specified distance prior to releasing the biasing of the output element 350.
  • a second portion 339B of the three-dimensional circuit i.e., collectively the first portion 339A and the second portion 339B create the three-dimensional circuit which will be referred to as 339.
  • a cyclical, annular or closed-loop movement or circuit 339 of the gear block and the interfacing surface that has a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, design specified pattern of movement.
  • the cyclical, annular or closed-loop movement or circuit 339 of the gear block 362 can allow for a positive biasing of the output interface surface by the gear block interface surface that is translated into a forward rotation of the output element 350. Additionally, the gear block 362 can negatively bias the output element interface surface with the gear block interface surface in a manner that reduces the backlash or possible backlash of the output element and/or gear block. In at least one embodiment, there can also be a neutral biasing or position that allows the gear block 362 to not bias the output element 350 in a positive and/or negative manner, it may also in some example allow for the gear block 362 to release outwardly from the central axis.
  • Figs. 5, 6, 7, 8, 9, 10, 11, and 12 additional illustrations of the third embodiment of a gearbox mechanism 320 of the present invention are depicted.
  • rocker arm(s) 399 drive their respective gear block(s) 362 through a two-dimensional circuit in response to rotation of the cam element 330.
  • the two-dimensional circuit 339A includes urging the gear block 362 to biasing the output element 350 and move or rotate the output element 350 a specified distance prior to releasing the biasing of the output element 350.
  • the gear block 362 When the gear block is disengaged from the output element 350, the gear block 362 can be rotated and pivoted in a manner to allow it to move the interface surface in a direction opposite of the rotational movement of the output element 350, allowing the gear block 362 to return back the same specified distance to again reengage the output element 350 once again and repeat the process.
  • the two-dimensional circuit 339 depicted in the drawings is not to scale and is exaggerated to illustrate the general principal of the invention. For example, the distance A-B would typically be much smaller than depicted.
  • the travel path or circuit 339A of each gear block 362 is controlled by adjusting the size and configuration of the rocker arm(s) 399, gear block(s) 362, and/or altering the pathway or groove 336 formed in the cam element 330.
  • a plurality of gear block assemblies 360 are configured about the central axis 306 that passes through the cam element 330.
  • the cam element 330 in at least one version, may be coupled to a power source (not illustrated) by an output device (not illustrated).
  • the cam follower(s) 394 of the respective rocker arms(s) 399 of each gear block assembly maintain contact with a particular pathway or groove 336 formed in the planar surface 334 of the cam element 330.
  • the planar surface 334 of the cam assembly 330 is substantially perpendicular to the axis of rotation of the cam assembly 330.
  • the variance of distance from the center of rotation to the different points along the pathway or groove 336 of the cam element 330 causes the rocker arm(s) 399, pivotally attached to a gear block(s) 362 to work in concert to move their respective gear block(s) 362 through a predetermined circuit of movement 339.
  • This predetermined circuit of movement 339 of the gear block 362 can be precisely calibrated to meet specific engineering requirements.
  • the torque ratio and speed reduction may be regulated and controlled by adjusting the circuit of movement 339 of each gear block 362.
  • An axial cam 331 rotates, in coordination with the cam element 330, and as they are rotated the pathway tracker 364 (see in particular Figs. 7, 13 and 14) of the gear block 362 tracks along the axial pathway or groove 337.
  • the axial pathway or groove 337 is formed in the circumferential surface 335 of the axial cam 331.
  • the variance of height of the pathway towards or away from the lower section 333A of the axial cam 331, causes the gear block 362 to be engaged or disengaged from the interface surface 353 of the output element 350 with a linear movement (may also be called a second portion 339B of the three-dimensional circuit for the gear block 362).
  • the movement of the gear block 362 may be created through two separate portions (339A/339B) that act in concert to generate a rotational (two dimensional movement in one plane (horizontal) a combination of left-right/in-out axial motions) movement and a linear movement in a vertical plane (up and down motions) that create the three dimensional circuit.
  • All embodiments of gearbox mechanisms constructed in accordance with the present invention feature a plurality of gear block assemblies configured about the central axis 306 of the cam element 330 and may comprise either an odd or even number of gear block assemblies. At least two, and preferably three or more, gear block assemblies are required for a gearbox mechanism of the present invention. The movement of the gear block assemblies typically moves in a rotational series to one another.
  • the gear block assemblies configured on opposing sides of the cam element 330 engage and disengage in unison from the secondary or output element 350.
  • an embodiment of the gearbox mechanism 320 may feature four gear block assemblies 360.
  • another embodiment of the gearbox mechanism 320 may feature six gear block assemblies 360. This is accomplished by ensuring that the individual pathways or grooves formed in the planar surface of the cam element are in phase with one another along the planar surface of the cam element 330.
  • the main body 340 in at least one version, can provide a housing for the gear block assemblies (not illustrated).
  • the gear block assemblies (not illustrated) can rest and/or be supported by the main body retaining surface 387.
  • the rocker arm(s) (not illustrated) may be supported and/or retained by the main body rocker arm void 377 as defined by the main body 340.
  • a rocker arm post 388 (see e.g ., Fig. 15) can be configured to be retained and/or supported by the main body rocker arm void 377 to allow for a pivoting motion of the rocker arm (see e.g., Fig. 15) to occur.
  • the main body rocker arm void 377 may be sized to retain and prevent the rocker arm(s) (not illustrated) from being removed except in a single direction that is perpendicular to the pivoting motion that the rocker arm(s), while the pivoting motion of the rocker arm(s) (not illustrated) can also coincide with a pivoting motion of the gear block (not illustrated) that allows for the interfacing, engaging, and/or rotating of an output element (not illustrated).
  • a cam interface surface 389 can support a cam element (not illustrated) as it engages with the gear assemblies (not illustrated).
  • the main body 340 can be coupled on the cam side 341 to an input hub, a retainer, or other securing devices via a fastener (not illustrated) sized to fit into a coupling aperture 344 defined by the main body 340.
  • the input hub, retainer, or other securing devices in at least one example, can be utilized to secure and/or support a cam element (not illustrated) in a manner to prevent vibration but allow free movement of the cam element.
  • the axial cam 331 can be coupled to a cam element 330 through an axial cam securing aperture 345.
  • the axial cam securing aperture 345 can be a threaded aperture that allows for a fastener 302 to be utilized in securing the axial cam 331 and the cam element 330 in a secure and/or fixed manner.
  • the axial cam 331 may comprise a lower section 333A and an upper section 333B.
  • the lower section 333A can be a tubular section having a smooth surface for interfacing with the output element (not illustrated) and/or bearings, roller bearing, or ball bearings.
  • the upper section 333B can comprise a flange section have one or more axial cam securing aperture(s) 345 traversing the portion of the upper section 333B that extends outwardly past the perimeter of the lower section 333A.
  • the circumferential surface 335 of the upper section 333B may have a pathway 337 formed into it and defined by the upper section 333B of the axial cam 331.
  • the axial cam pathway 337 is generally circular or annular, in a horizontal plane, while in other embodiments it will be shaped and/or configured to match the perimeter of the upper section 333B.
  • the axial pathway 337 is generally straight or flat with at least one inflection point and/or hump 329 formed therein.
  • the inflection point 329 and/or hump allows for an actuation or linear actuation of a gear block (not illustrated).
  • the inflection point 329 and/or hump can also when combined with the two dimensional rotational movement (also call a first portion of the three-dimensional circuit) of the gear block (not illustrated) caused by the pivoting and/or rotation of the rocker arm(s) by the cam pathway, generate the second portion of movement, which when combined with the first portion creates a three dimensional circuit of movement for the gear block.
  • the linear actuation of the gear block can allow for an engagement and disengagement of the gear block (not illustrated) from the output element (not illustrated).
  • the output element 350 is illustrated in a perspective view.
  • the output element 350 can have an output element circumferential surface 351.
  • the output element circumferential surface 351 can have an interface surface 353.
  • the interface surface 353 can be a set of gear teeth, while in other examples the interface surface 353 may include post and hole, tongue and groove, friction fit surface or other interfacing means.
  • the output element 350 may also be secured to an output device or system through a securing aperture 359.
  • the output element 350 has a central aperture 332 coaxially aligned with the center of the output element 350.
  • the output element 350 may also define a housing void 355 that allows for the output element 350 to receive the axial cam (not illustrated) and the cam element (not illustrated).
  • the cam element 330 can have one or more axial cam securing apertures 345 that allows for a securing of the cam element 330 with an output element guide and/or ball bearing assembly (or set of ball bearings) (not illustrated).
  • the axial cam securing aperture(s) 345 can be arranged coaxially around the central aperture 332.
  • the cam element 330 includes a planar surface 334 having at least one pathway 336 formed therein. In at least one example, the pathway 336 will have a single depth that is uniform along the entire pathway 336.
  • the planar surface 334 of the cam assembly 330 is substantially perpendicular to the axis of rotation of the cam assembly 330. While the planar surface 334 in Fig. 12 is depicted on the side of the cam element 330 facing the axial cam 331, it should be understood that the planar surface into which pathway(s) 336 is formed may be configured on either facing side of the cam element 330 (z.e., either a planar surface facing the axial cam 331 or a planar surface facing away from the axial cam 331). In other examples, the pathway 336 may vary in depth along the length of the pathway 336. The pathway 336 can allow a cam follower 394 (See Fig.
  • a rocker arm and/or gear block 362 (see Fig. 5).
  • the axial cam 331 (see Figs. 9 and 10) can rest and/or be secured via one or more fasteners to the cam element support surface 318.
  • Figs. 13 and 14 illustrate an embodiment of a gear block 362.
  • the gear block 362 is generally rectangular in shape and includes a gear block tracking post 364.
  • the gear block tracking post 364 can allow the gear block 362 to track a pathway 337 formed in the axial cam 331 (see Figs. 9-10).
  • the gear block 362 may further include an interface surface 363 for interfacing with the interface surface 353 of the output element 350 (see Fig. 11).
  • the interface surface 363 comprises a set of gear teeth, while in other examples the interface surface 363 may include post and hole, tongue and groove, friction fit surface or other interfacing means.
  • the gear block 362 further includes a void 311 formed in the opposing surface from the gear block interface surface 363.
  • the gear block rotation void 311 is utilized to connect the gear block 362 to a rocker arm 399 (see Figs. 6 and 15).
  • the gear block rotation void 311 can have shoulders or contact points 311A/311B.
  • the shoulder(s) or contact points 311A/311B can interact with receiving voids 397 on the rocker arm 399 to allow for pivoting and/or rotation to occur.
  • Figs. 15 and 16 are illustrations of one embodiment of a rocker arm 399.
  • the rocker arm 399 can be coupled to the gear block 362 (see Fig. 5) to generate a pivoting and/or rotational movement of the gear block 362.
  • the rocker arm 399 is generally L- shaped, with an upper arm 398A, a rotation arm 398B, and a rocker arm post or pivot point 388.
  • the upper arm 398A may have a cam follower aperture 386 formed through the upper arm portion 398A for receiving a cam follower device 394.
  • the upper arm 398A and/or rotation arm 398B can be manufactured with an angled offset 396 that allows for the gear block (not illustrated) to be rotated and/or pivoted in a designer specified pattern.
  • the upper arm 398A and the rotational arm 398B may have no offset angle 396 and create an approximate right or ninety degree angle with the pivot point portion 388 of the rocker arm 399.
  • the rotational arm portion 398B of the rocker arm 399 may have a pivot pin aperture 381 that traverses the rotational arm portion and aligns with one of the receiving voids 397A and/or 397B that are defined by the rocker arm post/pivot point 388.
  • the rocker arm post/pivot point 388 can be configured to allow a gear block 362 to be coupled to the rocker arm 399.
  • the rocker arm post/pivot point 388 can further include or define at least one receiving void 397.
  • the receiving void 397 can allow the rocker arm 399 to receive a shoulder or contact point of a gear block (not illustrated).
  • the receiving void(s) 397 can allow for the gear block 362 to be pivoted and/or rotated around a designer specified point in combination with other components of a gear block mechanism.
  • the pivot pin aperture 381 allows for a pivot pin to be placed in a manner that would prevent a gear block from pivoting and/or rotating a specified amount by preventing the shoulder or contact point from being able to be received by the receiving void 397. This allows the gear block to generate a driving force in a single direction, and/or prevent the gear block from rotating beyond a specified rotation amount.
  • a fourth embodiment of a gearbox mechanism 420 of the present invention is depicted.
  • the gearbox mechanism 420 may be powered and/or rotated by a power source or actuator (as shown in Figs. 1A and IB), that is translated to an output device.
  • the power source can be an electric motor, combustion engine, water activated source, wind turbine, or other possible embodiments.
  • the power source or actuator, as well as the output device may be rotatively coupled by means of gears, chains, belts, or magnetic fields.
  • the gearbox mechanism 420 can be configured about a central axis 406.
  • the central axis 406 can pass through a central aperture of the main body 440, the output element 450, cam element 430, and hub 414.
  • the hub 414 may include a ball bearing assembly (not illustrated) that allows the cam element 430 to rotate freely within the hub 414 based upon an input device such as a shaft or rotatable elements such as a set of other gearing, belts, levers, magnetic or electrical fields, etc.
  • the main body 440 and the hub 414 may be coupled together with fasteners (not illustrated).
  • the fasteners may be screws, bolts, all thread, compression fit devices, or other means for fastening two components together in a fixed or secure manner.
  • the gearbox mechanism 420 may further include bearings such as roller bearings 407 that may separate each of the output element 450, and cam element 430 from the main body 440 and/or the hub 414.
  • the gearbox mechanism 420 may also include a plurality of gear block assemblies 460.
  • Each gear block assembly can include a rocker arm 499 (rocker arms 499A, 499B, 499C, 499D, 499E, 499F, and 499G collectively referred to as rocker arm(s) 499) that are coupled with the gear block(s) 462 (gear blocks 462A, 462B, 462C, 462D, 462E, and 462F may be referred to collectively as gear block(s) 462).
  • the gear block(s) 462 may have a pathway tracker that can individually or in combination with a pathway follower element tracks and/or follows a pathway formed into the cam element 430.
  • the gear blocks 462 of the present invention are specifically designed to enable a greater surface area (e.g ., greater number of gear teeth) to engage the output element 450 at any given time, thereby spreading the stresses associated therein across a greater area.
  • a greater surface area e.g ., greater number of gear teeth
  • the gear block 462 of the present invention reduce backlash to zero and even preloaded conditions to create a tight connection between the power source and/or the powered device (not illustrated). This is an extremely desirable feature especially for high vibration applications.
  • the gear block 462 may be manufactured of lighter-weight materials, which are typically less expensive and easier to manufacture, with no degradation in reliability.
  • a typical stress result for spur gears are in the range from 450MPa to 600MPa.
  • High grade steels are the best fitted materials for handling such high stress levels.
  • Other materials like low grade steel or aluminum will deform under the similar conditions.
  • the levels of stress under the similar conditions can be reduced to about 20MPa.
  • These low stress levels allow the gearbox mechanism of the present invention to be manufactured using low grade steels, aluminums or even plastics for the same application.
  • the gearbox mechanism 420 of the present invention is adaptable to a broad range of applications that were previously impractical because of weight and space limitations.
  • the rocker arm 499 can also have a cam follower 494 allowing for the following of a specified pathway(s) formed along a circumferential surface of the cam element 430.
  • the interface surfaces 463 (see Fig.23) of the gear block 462 can engage with the interface surface 452 of the output element 450.
  • the gear blocks are rotated by an associated movement of the rocker arm 499.
  • the cam element 430 includes at least one unique pathway or groove that interfaces with the cam follower 494 of the rocker arm 499 so that, as the cam element 430 rotates, the movement of the gear block 462 and/or rocker arm 499 is controlled in two dimensions in accordance with at least one certain design parameter.
  • the gear block assemblies By varying the radius of the pathway or grooves on the cam element 430, the gear block assemblies drive respective gear block(s) 462 through a two-dimensional circuit in response to rotation of the cam element 430.
  • the two-dimensional circuit includes urging the gear block(s) 462 to engage the output element 450 and move and/or rotate the output element 450 a specified distance prior to disengaging from the output element 450, and returning back the specified distance to again reengage the output element 450 once again, and repeat the process.
  • the travel path or circuit of each gear block 462 is controlled by adjusting the length, width, height, and/or size of the respective gear block and/or rocker arm 499 and/or altering the pathways or grooves formed in the cam element 430.
  • the rocker arm 499 is pivoted around a specific pivot point by the cam follower 494, which traverses the path in the cam element 430 as the cam element 430 rotates.
  • the gear blocks 462 may also have a pathway tracker and/or pathway cam follower that follows a separate path along the cam element 430 that also triggers an actuation point for the gear block(s) 462.
  • a gear block 462 in at least one example, 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, design specified pattern of movement.
  • the main body 440 may be coupled with at least one hub 412A and/or 412B.
  • the hub(s) 412A and 412B may be coordinated
  • FIG. 18 a perspective view is depicted of the cam element 430, along with the rocker arm 499, cam followers 494, and gear block 462.
  • the central axis 406 passes through the central aperture 432 at the center of the cam element 430.
  • the cam element 430 interacts with the rocker arm 499 along with the gear block 462 to cause the gear block 462 to have a cyclical, annular or closed loop movement having a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, design specified pattern of movement based upon the pathways in the cam element 430 that may allow a cam follower 494 attached to the rocker arm 499 to traverse along the pathway and generate movement of the gear block(s) 462.
  • the cam follower(s) 494 may be coupled and/or attached to the rocker arm 499 through a rocker block 470 (see Figs. 23 & 28).
  • Each of the cam followers 494 can each have a separate path or, in some embodiments, may have a single path that each follow at a different position simultaneously.
  • the gear block(s) 462 can be pivotally connected to the rocker arm 499.
  • a ring spring connecting all of the gear blocks 462 in a gear train may be used as a biasing mechanism in accordance with the present invention.
  • the cam element will have a single pathway, however there maybe multiple paths formed in the cam element 430 that can be in the same plane where they are parallel paths, or paths of different distances from the central axis 406, or the paths can be in separate planes stacked in the direction of the central axis 406.
  • the pathways 436, 437 along cam element 430 allows for movement and rotation of the gear blocks 462 causing the interface surfaces of the gear blocks 462 to engage, interface and/or interact with the output element 450 (Fig 17).
  • cam follower(s) 494 maintain contact with the surface of their respective pathways or grooves formed in the cam element 430.
  • cam element 430 depicted in the Figures appears to be a single unit having at least one pathway or groove formed in the circumferential surface 434 of the cam element 430, it is understood that the cam element 430 may also comprise a plurality of separate discs or tubes, each having a unique pathway formed in its circumferential surface 434, which are mechanically coupled to one another to assemble a single cam assembly 430.
  • rocker arm 499 pivots about its pivot point to compensate and maintain contact between rocker arm 499/cam follower 494 and the pathway 436, 437.
  • This pivoting or moving of the rocker arm 499 about its pivot point induces movement in the pivotal connection with the gear block 462.
  • Each rocker arm 499 acts independently of the other rocker arm(s) 499 due to the cam follower(s) 494 of each rocker arm 499 following and/or traversing the pathway 436, 437 formed in the circumferential surface of the cam element 430 at their respective distinct points.
  • the rocker arm 499 can pivot at specific point causing the gear block to pivot and/or rotate around a specific point.
  • the pivot point of the rocker will trigger a left, right, in or out, or a rotational motion to the gear block 462.
  • Associated together they allow for a cyclical, annular or closed-loop movement of the gear block and the interfacing surface that has a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, design specified pattern of movement.
  • the pivot point of the rocker arm 499 will trigger a left, right, in or out, or a rotational motion to the gear block 462.
  • the two-dimensional circuit may have a first portion 439A includes urging the gear block 462 to biasing the output element (not illustrated) and move or rotate the output element (not illustrated) a specified distance prior to releasing the biasing of the output element. Additionally, there may be an engagement and/or disengagement actuation that allows for a second portion 439B of the two-dimensional circuit 439.
  • a cyclical, annular or closed-loop movement or circuit 439 of the gear block and the interfacing surface that has a generally rectangular, elliptical, circular, square, conical, oval, ovoid, truncated circular pattern, or any combination thereof, design specified pattern of movement.
  • the cyclical, annular or closed-loop movement or circuit 439 of the gear block 462 can allow for a positive biasing of the output interface surface by the gear block interface surface that is translated into a forward rotation of the output element 350. Additionally, the gear block 462 can negatively bias the output element interface surface with the gear block interface surface in a manner that reduces the backlash or possible backlash of the output element and/or gear block.
  • Figs. 19-20 provide illustrations of the cam element in alternative perspective views.
  • the cam pathways 436/437 allow for a biasing of the gear block (not illustrated) in both positive and negative directions.
  • a cam follower (not illustrated) follows the pathways formed along the circumferential surface 434 of the cam element the gear block is rotated and/or pivoted into and/or through a neutral position, a positively biased position, or a negatively biased position.
  • radiuses of the pathways 436/437 allow for the gear block (not illustrated) to be cycled through a neutral position at a first point along the interface surface of the output element (not illustrated) to a neutral position at a second point along the interface surface of the output element.
  • the neutral positions allow for an engagement and/or disengagement to occur and allow for the gear block to be cycled from a first engaged position to a second engaged position.
  • the cam element 430 may also have an actuation pathway 438 that may be tracked and/or followed by a gear block tracking post 464 (see Fig. 24) and/or a gear block tracking follower 474 (see Fig. 23).
  • the actuation pathway 438 allows the linearly actuated based on the position of the gear block tracker post 464 (see Fig. 24) along the actuation pathway 438.
  • the linear actuation in combination with the rotational actuation (two-dimensional actuation) of the gear block results in a three-dimensional actuation.
  • the three-dimensional combination of movements causes the cyclical and/or patterned movement of gear block that imparts a force on the output element (not illustrated) generating movement of said output element.
  • the actuation pathway 438 is generally straight or flat with at least one inflection point and/or hump 429 formed therein.
  • the inflection point 429 and/or hump allows for an actuation or linear actuation of a gear block (not illustrated).
  • the inflection point 429 and/or hump can also allow for, when combined with the two-dimensional circuit of the gear block (not illustrated) caused the pivoting and/or rotation of the rocker arm(s) by the cam pathway, causes a three-dimensional circuit for the gear block.
  • the linear actuation of the gear block can allow for an engagement and disengagement of the gear block from the output element.
  • the gear block assembly 460 may include a rocker block 470, a rocker pin 480, gear block 462, tracker follower 474, rocker arm 499, and cam follower(s) 494A/494B.
  • the rocker arm 499 is configured to allow the gear block 462 to be engaged and/or disengaged with an output element (not illustrated) as the tracker follower 474 follows an actuation pathway (not illustrated) the engagement/disengagement of the gear block 462 may be caused linear or actuation movement of the gear block 462.
  • the cam follower(s) 494A/494B can follow pathways that cause a two- dimensional movement of the gear block 462.
  • the rocker arm 499 defines a rocker block void 497B within the rocker arm 499.
  • the rocker block void 497B can be sized and shaped to allow it to receive a portion of the rocker block 470.
  • the rocker block 470 may have a rocker block extension 474 that allows for the cam follower arm(s) 472A/472B to be coupled to the rocker arm 499.
  • the cam follower arm(s) 472A/472B can have a cam follower aperture 471 A/471 B that is defined in the cam follower arm(s) 472A/472B and traverses through the body of each respective cam follower arm 472A/472B.
  • the rocker block 470 in at least one embodiment is manufactured of a resilient material that does not allow for any flexing of the cam follower arm(s) 472A/472B.
  • the cam follower arm(s) 472A/472B may be made of a flexible material that may have memory properties that prevent it from overextending and/or returning to a specific structure or form after a flexing has occurred.
  • the rocker arm 499 can also define a rocker pin void 497A within the rocker arm 499.
  • the rocker pin void 497A may also include a rocker securing pin void 498B that is sized to receive a fastener (not illustrated).
  • the fastener (not illustrated) may be utilized to prevent the rocker pin 480 from moving once placed within the rocker pin void 497A.
  • the fastener (not illustrated) may also couple the rocker pin 480 with the gear block 462.
  • the gear block 462 can have a pin slot 498 A that allows for a fastener, or other coupling device, mechanism or means to couple the gear block to the rocker arm 499 and/or the rocker pin 480.
  • the gear block 462 can include a gear block rotation void 411 that allows for a coupling device or mechanism to interface with the pin slot 498A. Additionally, the gear block rotation void 411 can also allow for the rotation and/or pivoting of the gear block 462 based on the actuation, rotation, and/or pivoting imposed on the rocker arm 499, rocker block 470 and/or rocker pin 480. As the gear block 462 is rotated and/or pivoted the gear block interface surface 463 can interact with other interface surfaces such as an output interface surface (not illustrated).
  • the gear block 462 can have a gear block post 464 that allows the gear block 462 to interface with a pathway and/or groove.
  • the gear block post 464 can also allow for a tracking element (not illustrated).
  • the tracking element may be a ball bearing, roller bearing, or other mechanism or means for reducing friction.
  • a gap or void 496A/496B that can be filed with a void or material to allow for compliance mechanics.
  • the material in some embodiments may have a memory or alloy like effect that allow it to transfer energy between the rocker arm 499 and the rocker pin 480 or the rocker block 470.
  • Compliance mechanics or compliance mechanisms allow for a force or energy to be transferred to another body or object through a deformation or elastic body.
  • Fig. 30 is a perspective view of the main body 440.
  • the main body 440 houses the gear block assembly when the gear block mechanism is assembled.
  • the main body 440 can have a rocker arm void 477 and a rotation or pivot void 479.
  • the rocker arm void 477 allows for the main body 440 to receive the rocker arm 499 and allow it to pivot and/or rotate about a fixed pivot point.
  • the rotation or pivot void 479 allows for the rotation and/or pivoting of the gear block assembly.
  • the rotation or pivot void 479 allows for the gear block assembly, and/or the rocker block (not illustrated) to rotate and/or pivot into the void with the wall of the void as defined by the main body 440, thereby preventing excessive rotation or pivoting.

Abstract

La présente invention concerne un mécanisme de boîte de vitesses amélioré qui comprend une pluralité d'ensembles blocs d'engrenages actionnés par came, qui transfèrent de la puissance d'un arbre de commande à un élément d'engrenage secondaire ou de sortie. Chaque ensemble bloc d'engrenages comprend un bloc d'engrenages ayant une surface qui a périodiquement une interface avec un élément d'engrenage secondaire ou de sortie. Selon un mode de réalisation préféré, la surface d'interface comprend une pluralité de saillies ou de dents correspondant à des saillies ou des dents d'engrenage complémentaires sur l'élément engrenage de sortie. Chaque ensemble bloc d'engrenages comprend en outre un bloc d'engrenages, un culbuteur, des suiveurs de came et/ou un montant de suivi de bloc d'engrenages, destinés à relier le bloc d'engrenages à un ensemble cames, lequel est relié à son tour à une source d'alimentation. L'ensemble came comprend, autour de sa circonférence, une voie ou une rainure unique pour chaque suiveur de came et/ou montant de suivi de bloc d'engrenages d'un ensemble bloc d'engrenages particulier de sorte que le mouvement du bloc d'engrenages puisse être commandé dans deux ou trois dimensions conformément à un certain paramètre de conception.
PCT/US2019/046183 2019-08-09 2019-08-12 Mécanisme de boîte de vitesses à came axiale WO2021029867A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16/537,218 US10626964B2 (en) 2013-03-12 2019-08-09 Axial cam gearbox mechanism
US16/537,218 2019-08-09

Publications (1)

Publication Number Publication Date
WO2021029867A1 true WO2021029867A1 (fr) 2021-02-18

Family

ID=74571172

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2019/046183 WO2021029867A1 (fr) 2019-08-09 2019-08-12 Mécanisme de boîte de vitesses à came axiale

Country Status (1)

Country Link
WO (1) WO2021029867A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11525502B2 (en) 2019-06-13 2022-12-13 Circular Wave Drive Partners Inc. Circular wave drive

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100206686A1 (en) * 2009-02-18 2010-08-19 Xerox Corporation Gearbox Output Switcher
CN102121511A (zh) * 2009-11-04 2011-07-13 中山大学 具间歇输出动作的传动机构
US20120291731A1 (en) * 2011-05-16 2012-11-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Device for varying the charge-changing valve lift in an internal combustion engine
US20180363745A1 (en) * 2013-03-12 2018-12-20 Motus Labs, LLC Simplified gearbox mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100206686A1 (en) * 2009-02-18 2010-08-19 Xerox Corporation Gearbox Output Switcher
CN102121511A (zh) * 2009-11-04 2011-07-13 中山大学 具间歇输出动作的传动机构
US20120291731A1 (en) * 2011-05-16 2012-11-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Device for varying the charge-changing valve lift in an internal combustion engine
US20180363745A1 (en) * 2013-03-12 2018-12-20 Motus Labs, LLC Simplified gearbox mechanism

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11525502B2 (en) 2019-06-13 2022-12-13 Circular Wave Drive Partners Inc. Circular wave drive

Similar Documents

Publication Publication Date Title
US10927932B2 (en) Axial cam gearbox mechanism
US10260606B2 (en) Gearbox mechanism
US10240666B2 (en) Simplified gearbox mechanism
US20210285528A1 (en) Axial cam gearbox mechanism
US11028910B2 (en) Spiral cam gearbox mechanism
US10151375B2 (en) Motorized gearbox mechanism
JP5133914B2 (ja) 連続可変比動力伝達装置に関する改良
WO2021029867A1 (fr) Mécanisme de boîte de vitesses à came axiale
US20080039268A1 (en) Ball Gearings for Rotation Transfer
WO2021183566A1 (fr) Mécanisme de boîte de vitesses à came axiale
CA3108694C (fr) Mecanisme simplifie de boite de vitesses
WO2020101716A1 (fr) Mécanisme de boîte de vitesses à came en spirale
WO2019231469A1 (fr) Mécanisme de boîte de vitesses motorisé
RU2761158C1 (ru) Механизм передачи вращения между параллельными валами
RU2590797C2 (ru) Планетарная передача
RU2725336C1 (ru) Двухскоростной ручной привод запорной арматуры
JPH0781589B2 (ja) 軸継手
JP2017048882A (ja) 無段変速機の変速機構

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19941284

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19941284

Country of ref document: EP

Kind code of ref document: A1