WO2021176304A1 - Engrenage hélicoïdal et son procédé de fabrication - Google Patents

Engrenage hélicoïdal et son procédé de fabrication Download PDF

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Publication number
WO2021176304A1
WO2021176304A1 PCT/IB2021/051548 IB2021051548W WO2021176304A1 WO 2021176304 A1 WO2021176304 A1 WO 2021176304A1 IB 2021051548 W IB2021051548 W IB 2021051548W WO 2021176304 A1 WO2021176304 A1 WO 2021176304A1
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WO
WIPO (PCT)
Prior art keywords
gear
helical
compound
gearbox
tapered
Prior art date
Application number
PCT/IB2021/051548
Other languages
English (en)
Inventor
Richard Bos
Original Assignee
Genesis Advanced Technology Inc.
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
Application filed by Genesis Advanced Technology Inc. filed Critical Genesis Advanced Technology Inc.
Priority to DE112021001392.0T priority Critical patent/DE112021001392T5/de
Publication of WO2021176304A1 publication Critical patent/WO2021176304A1/fr

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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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2854—Toothed gearings for conveying rotary motion with gears having orbital motion involving conical gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29D—PRODUCING PARTICULAR ARTICLES FROM PLASTICS OR FROM SUBSTANCES IN A PLASTIC STATE
    • B29D15/00—Producing gear wheels or similar articles with grooves or projections, e.g. control knobs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29D—PRODUCING PARTICULAR ARTICLES FROM PLASTICS OR FROM SUBSTANCES IN A PLASTIC STATE
    • B29D99/00—Subject matter not provided for in other groups of this subclass
    • B29D99/0032—Producing rolling bodies, e.g. rollers, wheels, pulleys or pinions
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2863—Arrangements for adjusting or for taking-up backlash
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • Typical injection molding requires that compound gear components having concentric, cylindrical helical gears of different pitch diameters on the same part have a constant lead in order to be injection moldable (specifically, in order to enable the part to be released from a mold). This means that the helix angle must be different for helical gears of different diameters.
  • a tapered gear tooth profile as used in a gearbox would have to have a constantly changing helix angle across the tooth width to follow this principle, greatly increasing the complexity of the gear design.
  • Injection molded compound helical gears are provided with a constant helix angle along the length of the compound helical gear.
  • the compound helical gears comprise at least two gear section, including a first gear section and a second gear section.
  • Each of the first gear section and the second gear section are tapered such that each of the first gear section and the second gear section extends from a small diameter section end to a large diameter section end.
  • the large diameter section end of the first gear section is connected to the small diameter section end of the second gear section.
  • the small diameter section end of the second gear section may be larger than the large diameter section end of the first gear section.
  • Certain embodiments are directed to a method of manufacturing a helical compound gear, the method comprising: providing an injection mold corresponding to the helical compound gear and having a tapered interior surface, wherein the tapered interior surface defines gear teeth having a constant helix angle between a first end of the tapered interior surface and a second end of the tapered interior surface; injection molding a material into the injection mold; curing the injection molded material to generate an injection molded helical compound gear; and extracting the injection molded helical compound gear by twisting the injection molded helical compound gear out of the injection mold while following the constant helix angle.
  • the tapered interior surface of the injection mold extends between the first end of the tapered interior surface and the second end of the tapered interior surface, wherein the first end has a diameter larger than a diameter of the second end; and wherein extracting the injection molded helical compound gear comprises twisting the injection molded helical compound gear out of the first end of the injection mold.
  • injection molding a material into the injection mold comprises injection molding a nylon material into the injection mold.
  • injection molding a material into the injection mold comprises filling an interior of the injection mold defined by the tapered interior surface and filling the gear teeth of the injection mold with the material.
  • Certain embodiments are directed to a helical compound gear comprising: an injection molded tapered body extending between a first end and a second end, wherein the second end has a diameter larger than a diameter of the first end; injection-molded helical gear teeth extending at least partially along a length of the injection molded tapered body; and wherein the helical gear teeth have a constant helix angle.
  • the constant helix angle is between 0°-45° In certain embodiments, the constant helix angle is between 0°-30° In various embodiments, the constant helix angle is between 0°-15° In various embodiments, the constant helix angle is between 0°-10° In certain embodiments, the constant helix angle is between 0°-5° In various embodiments, the constant helix angle is between 3°-5°. Moreover, in certain embodiments, the constant helix angle is between 15°-25°. [0009] In certain embodiments, the helical gear teeth define a constantly changing lead. In various embodiments, the injection molded tapered body comprises injection molded nylon.
  • the injection-molded helical gear teeth may be defined on an outer tapered surface of the injection molded tapered body.
  • the injection molded tapered body defines a first gear surface adjacent the first end and a second gear surface adjacent the second end.
  • the first gear surface extends between a first small end and a first large end and the second gear surface extends between a second small end and a second large end; the second small end is adjacent the first large end; and the first large end has a smaller diameter than the second small end.
  • the second small end is in contact with the first large end at a transition plane.
  • the second small end is spaced apart from the first large end to form a gap therebetween.
  • the first gear surface is spaced apart from the second gear surface to define a gap between the first gear surface and the second gear surface.
  • the first geared surface may be in contact with the second gear surface at a transition plane.
  • the first gear surface and the second gear surface have at least substantially identical helix angles.
  • the helical compound gear further defines an axial hole extending at least partially through a length of the helical compound gear between the first end and the second end.
  • the helical compound gear is defined as a planetary gear component.
  • Certain embodiments are directed to a gearbox comprising: a plurality of planetary gears, wherein each of the plurality of planetary gears comprise: an injection molded tapered body extending between a first end and a second end, wherein the second end has a diameter larger than a diameter of the first end; helical gear teeth along a length of the planetary gear between the first end to the second end, wherein the helical gear teeth have a constant helix angle between the first end and the second end; at least one sun gear in geared contact with a first portion of each of the plurality of planetary gears; and at least one ring gear surrounding the plurality of planetary gears and the at least one sun gear and in geared contact with a second portion of each of the plurality of planetary gears.
  • the gearbox further comprises at least one shim located adjacent to one of the first end or the second end of the plurality of planetary gears, wherein the at least one shim is configured to axially adjust a positioning of each of the plurality of planetary gears relative to the at least one sun gear or the at least one ring gear.
  • the injection molded tapered body defines a first gear surface adjacent the first end and a second gear surface adjacent the second end.
  • the first gear surface of each planetary gear extends between a first small end and a first large end and the second gear surface extends between a second small end and a second large end; the second small end is adjacent the first large end; and the first large end has a smaller diameter than the second small end.
  • the second small end is in contact with the first large end at a transition plane.
  • the second small end is spaced apart from the first large end to form a gap therebetween.
  • the at least one sun gear is in contact with the first gear surface and the at least one ring gear is in contact with the second gear surface.
  • a helix angle of the first gear surface at least substantially matches a helix angle of the second gear surface.
  • the gearbox may further comprise a planet carrier maintaining a desired axial position of the plurality of planetary gears relative to the at least one sun gear and the at least one ring gear.
  • each of the plurality of planetary gears comprise injection molded nylon.
  • the at least one sun gear comprises at least one input sun gear.
  • the at least one ring gear comprises at least one output ring gear.
  • the at least one ring gear comprises at least one input ring gear.
  • the at least one sun gear comprises at least one output sun gear.
  • each of the plurality of planetary gears comprise two compound gears, each compound gear extending between a small first end and a large second end, and wherein large second end of the two compound gears of each planetary gear are secured relative to one another.
  • the two compound gears are secured relative to one another with a fastener.
  • the at least one sun gear comprises at least two sun gears.
  • the at least one ring gear comprises at least two ring gears.
  • Figure 1 schematically illustrates a compound gear having a plurality of gears of differing diameters
  • Figure 2 schematically illustrates a tapered compound gear having a plurality of gears defined in accordance with various embodiments
  • Figure 3 schematically illustrates a compound gear having a plurality of gears of differing diameters and having a constant lead;
  • Figure 4 schematically illustrates a tapered compound gear having a constant helix angle
  • Figure 5 is a perspective view of a tapered compound gear according to one embodiment
  • Figure 6A is a side view of the tapered compound gear shown in Figure 5;
  • Figure 6B is an axial view of the tapered compound gear shown in Figure 5;
  • Figure 7 is a perspective view of an example gearbox according to one embodiment.
  • a tapered helical gear tooth design allows for the helix angle of two helical tapered gears to be held constant and still have the compound gear be injection moldable, which greatly simplifies the design effort when compared to the standard position of having to hold the lead constant.
  • the tapered design allows the helix angle to be held constant while still enabling the gear to be injection moldable, which greatly simplifies the design effort. This reduced design effort reduces design cost and complexity of a gearbox incorporating one or more gears, and allows beveloid gears in general more flexibility in manufacturing methods.
  • This tooth design allows a compound gear to be simpler in geometry, reducing the design effort to design and manufacture a gear, while still allowing the compound gear to be injection moldable.
  • the constant helix angle allows outer rings to be shimmed to take up backlash.
  • a tapered compound gear design allows the helix angle to be held constant while still enabling the compound gear design to be injection moldable in accordance with traditional mold designs, which greatly simplifies the design effort. This reduced design effort reduces design cost and complexity of gearboxes encompassing the compound gears and enables the use of beveloid gears in general more flexibility in manufacturing methods.
  • Typical knowledge would suggest that the taper would require a changing helix angle across the gear tooth in order to maintain a constant lead along the length of the taper and the entirety of the compound gear, which increases complexity substantially. Instead, with a taper, the helix angle can be kept constant along a length of the compound gear. This simplifies the design substantially.
  • a constant helix angle allows the axial position of the mating gear to be adjusted along the length of the taper (e.g., by the use of shims), which would not be possible with a gear tooth design having a varying helix angle.
  • Certain embodiments are directed to a compound gear defining a combination of two or more geared surfaces of different diameters positioned coaxially on a single compound part.
  • the two or more geared surfaces may be discrete and separate from one another (e.g., with a gap therebetween) or continuous with one another such that a first portion of a continuous surface defines a first geared surface and a second portion of the same continuous surface defines a second geared surface.
  • the constant helix angle continues along the length of the compound gear and across each of the geared surfaces.
  • compound gears are not tapered and are instead cylindrical (see, for example, Figures 1 and 3).
  • the two gears of different diameters cannot use the same helix angle (shown as a and b ) if the part is to be removed from an injection mold.
  • the helix angle must be different such that the lead (Lead A) is held constant between the two gears in the same part.
  • This allows the mold or the part to be twisted as they are separated from each other in order to clear both gear helixes.
  • twisting the mold or part by a single complete rotation to follow the helical gear teeth results in a linear translation by a constant distance for both gears, regardless of their diameter due to the constant lead. If the helical angle were held constant, a single rotation of the part would result in a different linear translation of the part, thereby causing cross-threading and/or binding of the mold to the injection molded part.
  • helical compound gears having a tapered profile may maintain a constant helix angle g and have a constantly changing lead (illustrated by Lead B and Lead C) between a first (wide) end and an opposite second (narrow) end of the tapered profile.
  • the gear can be physically removed from a mold by twisting the gear out of the mold while using a constant helix angle g across the gears included on the compound part. It has been found that increasing the taper angle s increases the ease with which the gear may be released from a mold, however decreasing the taper angle s increases the functionality of the compound gear.
  • the ratio between the axial length of the compound gear (measured along the length of the central axis of the compound gear) and the central diameter of the compound gear may be relevant in determining a usable lower limit for the taper angle s while maintaining releasability of the gear from a mold.
  • the taper angle s may be an angle selected between 0-90°; an angle selected between 0-45°; an angle selected between 0-15°; an angle selected between 0-10°; an angle selected between 0-5°; an angle selected between 3-5°; and/or the like.
  • a tapered gear need not follow the traditional principle by which the small end of the taper has one helix angle and the large end of the tapered gear has a different helix angle to maintain a constant localized lead across the length of the gear. Such a configuration would result in a helix angle changing constantly across the width of the tooth, which would greatly increase the design complexity and cost of such a part.
  • a constant helix angle not only decreases design complexity, but allows a planetary gearbox including the tapered gear to enable an adjustable backlash (e.g., through the integration of a shim with the compound gear). Without a constant helix angle, the axial position of the meshing gears must match perfectly, or the gears will not mesh properly.
  • a helical compound gear 500 is provided, such as that shown in Figure 5.
  • the helical compound gear is an injection-molded plastic material.
  • the helical compound gear comprises an injection-molded tapered body extending between a small-diameter first end 501 and a large-diameter second end 502.
  • the helical compound gear defines at least two gear sections, with each gear section being tapered.
  • the first gear section 510 extends between the first end 501 and a transition plane 503 located perpendicular to an axis A of the compound gear
  • the second gear section 520 extends between the transition plane 503 and the second end 502.
  • the transition plane 503 may be located at a mid-point between the first end 501 and the second end 502, although other placements of the transition plane 503 (to adjust the relative length of the first gear section 510 and the second gear section 520) are possible.
  • the first gear section 510 may be spaced apart from the second gear section 520, such that the first gear section 510 is not in contact with the second gear section 520. In such embodiments, a gap is formed between the first gear section 510 and the second gear section 520.
  • the compound gear 500 remains a single, integrally formed (molded) component, and therefore a connecting feature extends from the first gear section 510 to the second gear section 520.
  • the connecting component having an outer diameter smaller than the outer diameter of the first gear section 510 and the second gear section 520.
  • gear surfaces, gear teeth, and/or other surface features of the first gear section 510 need not align with the second gear section 520.
  • the diameter of the first gear section 510 at the transition plane 503 may be smaller than the diameter of the second gear section 520 at the transition plane 503 so as to define a stepped relation between the first gear section 510 and the second gear section 520.
  • the outer-most diameter of the first gear section 510 (measured at the tips of the gear teeth 511) may be smaller than the inner-most diameter of the second gear section 520 (measured at the bottom of troughs between gear teeth 521).
  • Each of the first gear section 510 and the second gear section 520 are defined by gear teeth 511, 521 surrounding an exterior surface thereof.
  • the gear teeth 511, 521 are helical gear teeth having a constant helix angle.
  • the helix angle of the gear teeth 511 of the first gear section 510 matches the helix angle of the gear teeth 521 of the second gear section 520.
  • each gear section (the first gear section 510 and the second gear section 520) has a constant helix angle along their respective lengths, the axial positioning of the compound gear 500 can be adjusted relative to a separate gear that is in geared contact with the first gear section or the second gear section without binding or cross-threading the gear teeth after axially moving the compound gear 500 relative to the separate gear.
  • the compound gear 500 may be hollow, with a hole 530 extending axially at least partially through the compound gear 500.
  • the hole 530 may serve to lighten the compound gear 500 and/or may be utilized to assist in securing the gear within a gearbox.
  • the hole 530 may be a through-hole, extending between the first end 501 and the second end 502 of the compound gear 500.
  • the hole 530 may be a blind hole extending only partially from the first end 501 through the compound gear 500 or extending only partially from the second end 502 through the compound gear 500.
  • the compound gear may encompass two blind holes 530 (one hole 530 extending from the first end 501 and one hole extending from the second end 502).
  • the hole 530 has a constant diameter along its entire length (e.g., between the first end 501 and the second end 502 of the compound gear).
  • the interior of the hole 530 may encompass one or more bearing sets to aid rotation of the compound gear 530 relative to a mounting shaft.
  • the hole 530 has a variable diameter, such as having a first diameter along its length between the first end 501 and the transition plane 503 and having a second diameter along its length between the second end 502 and the transition plane 503.
  • the second diameter is larger than the first diameter.
  • the hole 530 may have a tapered interior surface.
  • Table 1 measurements taken in the normal direction are measured perpendicular to the gear surface, and measurements taken in the transverse direction are taken along a circumference of the gear section (as shown in Figure 6A). Moreover, in Table 1, the number of teeth reflects a count of the number of teeth around the outer perimeter of gear section.
  • the normal module is proportional to the normal pitch, measured perpendicular to the gear surface (the normal pitch divided by pi is equal to the normal module, and the pitch being equal to the length of an entire gear tooth).
  • the helix angle reflects the angle that the gear teeth extend around perimeter of gear section.
  • the transverse module is proportional to the transverse pitch, measured around the circumference of the gear section.
  • the profile shift coefficient reflects the amount that a particular tooth is shifted relative to the reference diameter to influence contact between the gear tooth and a meshing gear.
  • the standard pressure angle reflects the leaning angle of each gear tooth.
  • the transverse working pressure angle reflects the leaning angle of each gear tooth, as measured within a plane parallel to a circumference of the gear.
  • the standard reference pitch circle diameter is measured at a midplane (see FIG. 6A) of each gear section, and reflects the diameter of the gear, measured at the base of the addendum of the gear teeth.
  • the operating pitch diameter is also measured at the midplane of each gear section.
  • the base circle diameter is measured at a midplane of the gear, and reflects a circle from which the involute portion of the gear teeth are generated.
  • the circular pitch at the reference pitch circle reflects the gear tooth pitch measured in a plane parallel with the reference circle.
  • the normal tooth thickness at the reference pitch circle reflects the thickness of each gear tooth, measured perpendicular to the gear tooth.
  • the transverse tooth thickness at the operating pitch circle reflects the tooth thickness measured in a plane parallel with the circumference of the gear section.
  • the cone angle reflects the angle of taper of each gear section.
  • the width is a measure between opposite ends of the gear section.
  • the minimum and maximum profile shift reflect the profile shift of the gear tooth measured at the small and large diameter ends of each gear section, respectively.
  • the normal tooth thickness - negative is a measure of the tooth thickness at the small end of each gear section (having a negative profile shift), measured perpendicular to the gear tooth.
  • the transverse tooth thickness - negative is a measure of the tooth thickness at the small end of each gear section (having a negative profile shift), measured within a plane parallel to the circumference of the gear section.
  • the normal tooth thickness - positive is a measure of the tooth thickness at the large end of each gear section (having a positive profile shift), measured perpendicular to the gear tooth.
  • the transverse tooth thickness - positive is a measure of the tooth thickness at the large end of each gear section (having a positive profile shift), measured within a plane parallel to the circumference of the gear section.
  • the gear assembly comprising an injection-molded compound gear 500 encompassing a first tapered gear section 510 and a second tapered gear section 520.
  • the first tapered gear section 510 is integrally molded with the second tapered gear section 520, such that a first end of the first tapered gear section 510 is molded adjacent to a second end of the second tapered gear section 520 (the first tapered gear section 510 and the second tapered gear section 520 meet at a transition plane 503 perpendicular to the axis A of the compound gear 500).
  • the first end of the first tapered gear section 510 has a diameter different than the diameter of the second end of the second tapered gear section 520.
  • Each of the first tapered gear section 510 and the second tapered gear section 520 has a constant helix angle, and the helix angle of the first tapered gear section 510 matches the helix angle of the second tapered gear section 520.
  • the gear assembly additionally comprises at least one shim in contact with an end of the compound gear 500, the shim enabling optional axial translation of the compound gear 500 within a gearbox, while each of the first tapered gear section 510 and the second tapered gear section 520 remains in geared contact with corresponding portions of the gearbox.
  • Yet other embodiments are directed to a gearbox comprising at least one injection-molded compound gear 500 encompassing a first tapered gear section 510 and a second tapered gear section 520.
  • the first tapered gear section 510 is integrally molded with the second tapered gear section 520, such that a first end of the first tapered gear section 510 is molded adjacent to a second end of the second tapered gear section 520 at a transition plane 503 oriented perpendicular to an axis A of the compound gear 500.
  • the first end of the first tapered gear section 510 has a diameter different than the diameter of the second end of the second tapered gear section 520.
  • the gearbox additionally comprises a first contact gear in geared contact with the first tapered gear section 510 and a second contact gear in geared contact with the second tapered gear section 520.
  • the gearbox additionally comprises at least one shim in contact with an end of the compound gear 500, the shim enabling optional axial translation of the compound gear 500 within the gearbox, while each of the first tapered gear section 510 remains in geared contact with the first contact gear and the second tapered gear section 520 remains in geared contact with the second contact gear.
  • the gearbox may be embodied as a torque amplifier positioned within an outer housing 710 in certain embodiments, and the injection-molded compound gears 500 are embodied as planetary rollers in the example gearbox shown in FIG. 7.
  • the contact gears are embodied as a first sun gear (e.g., an input sun gear 701), a second sun gear (e.g., an idling sun gear 704 rotationally secured around an exterior surface of a sun cylinder 703 which rotates with the input sun gear 701), a first ring gear (e.g., an output ring gear 705 secured relative to an output housing portion 712) and a second ring gear (e.g., a fixed ring gear secured relative to a fixed outer housing portion 711).
  • the input gear may be embodied as a ring gear
  • the output gear may be embodied as a sun gear.
  • a gearbox may be provided as a symmetric gearbox, incorporating a plurality of multi-part symmetric compound gears (e.g., formed by fastening two compound gears 500 relative to one another) within the gearbox.
  • the contact gears of a symmetric gearbox are provided in a symmetric configuration to contact geared sections of the multi-part symmetric compound gears (the construction of example multi-part symmetric compound gears is discussed in greater detail herein).
  • the compound gear 500 may be implemented as a planetary gear in a gearbox as one of a plurality of planetary gears (each planetary gear having an identical configuration), and one or more of the first tapered gear section 510 and the second tapered gear section 520 is in geared contact with a sun gear and/or a ring gear.
  • One of the sun gear or the ring gear is stationary.
  • the gearbox may be driven by an input gear (either an input sun gear or an input ring gear) or a driven planet carrier.
  • the gearbox provides an output via a sun gear, a ring gear, or a planet carrier.
  • the compound gear 500 may be incorporated into an assembled multi-part gear.
  • two identical compound gears 500 each having a configuration as discussed herein may be secured relative to one another after manufacture (e.g., via a fastener, such as an adhesive, a bolt, a screw, and/or the like) to form a symmetric multi-part gear.
  • the two identical compound gears 500 may be secured relative to one another while maintaining axial adjustability of the relative positioning of the two identical compound gears 500 relative to one another (e.g., via a threaded fastener securing the two identical compound gears 500 relative to one another; via a tensile spring in combination with a fastener securing the identical compound gears 500 relative to one another; and/or the like).
  • the symmetric multi-part gear may be incorporated into a symmetric gearbox.
  • a plurality of symmetric multi-part gears may be provided as planetary gears within a symmetric gearbox, such that a large diameter center portion (centered at the connection between the fastened identical compound gears) of the symmetric multi-part gear is provided within the gearbox, and smaller diameter outer portions (at opposing ends of the symmetric multi-part gear) are provided proximate outer ends of the gearbox.
  • compound gears 500 extend along an axial length between a smaller first end 501 and a larger section end 502.
  • the larger second end 502 of a first compound gear 500 may be secured onto the larger second end 502 of a second compound gear 500 to create a multi-part gear having equal and opposite dimensions across a plane formed at the connection between the first compound gear and the second compound gear.
  • the multi-part gear may comprise at least one compound gear 500 as discussed herein and one cylindrical and/or non- helical gear, with the compound gear 500 secured at one axial end to the cylindrical and/or non-helical gear.
  • two compound gears 500 may be secured to the cylindrical and/or non-helical gear (one at each axial end of the cylindrical and/or non-helical gear).
  • a tapered compound gear 500 having a constant helix angle along the length of the tapered compound gear 500 between a first (small diameter) end 501 and a second (large diameter) end 502 of the compound gear 500 may be manufactured in accordance with injection molding techniques utilizing a one-piece or two-piece injection mold having a tapered interior surface (to provide a tapered exterior surface of the molded part) and defining gear teeth with a constant helix angle between a first end of the tapered interior surface and a second end of the tapered interior surface of the mold.
  • the mold may be provided to form a compound gear including at least two tapered gear sections forming a stepped relationship therebetween.
  • the tapered compound gear design and constant helix angle of the gear teeth along the length of the compound gear 500 enable the compound gear 500 to be withdrawn from a mold without interference between the molded gear teeth and the corresponding contours of the mold itself.
  • a mold e.g., a two-piece mold configured for axial withdrawal of a molded tapered gear having a constant helix angle
  • a molten material e.g., a plastic material such as nylon, a reinforced plastic material, a metal material, and/or the like
  • the mold is opened, and the molded compound gear is twisted and withdrawn axially from the mold to extract the molded compound gear from the injection mold.
  • the mold has an interior surface configured to form a tapered compound gear as discussed herein.
  • the interior surface of the mold defines a first tapered gear mold section and a second tapered gear mold section.
  • the first tapered gear mold section extends between a first end of the mold and a transition plane of the mold, which defines a stepped transition between the first tapered gear mold section and the second tapered gear mold section.
  • the second tapered gear mold section extends between the transition plane of the mold and a second end of the mold.
  • the transition plane of the mold may be located at a mid-point between the first end and the second end of the mold, although other placements of the transition plane of the mold (to adjust the relative length of the first tapered gear mold section and the second tapered gear mold section) are possible.
  • the mold is configured to accommodate a spacer centered at the transition plane, the spacer being configured to form a gap between a first gear section and a second gear section of an injection molded gear.
  • the spacer may comprise a material identical to the mold.
  • the spacer may be a separate component that may be selectively secured in a desired position within a mold, and may be removed from the mold together with an injection molded compound gear such that the spacer may be separately removed from the injection molded compound gear.
  • the spacer may define a hole extending through a center thereof, such that the molten material provided to the mold flows through the hole so as to form an integrally formed compound gear encompassing the first gear section and the second gear section formed on opposite sides of the spacer.
  • the spacer may be a two-part spacer that may be disassembled to be removed from a formed compound gear.
  • features of the interior surface of the mold that are configured to form gear surfaces, gear teeth, and/or other surface features of the first gear section need not align with the features of the interior surface of the mold that are configured to form gear surfaces, gear teeth, and/or other surface features of the second gear section.
  • the diameter of the first tapered gear mold section at the transition plane of the mold may be smaller than the diameter of the second tapered gear mold section at the transition plane. Even with such a difference in sizing between the first tapered gear mold section and the second tapered gear mold section, a formed compound gear may be twisted and withdrawn from a second end (corresponding to the larger end of the tapered compound gear mold) of the mold.
  • Each of the first tapered gear mold section and the second tapered gear mold section are defined by features for forming gear teeth that are defined within an interior surface of the mold. These gear teeth-forming features form helical gear teeth having a constant helix angle. The helix angle of the gear teeth-forming features of the first tapered gear mold section match the helix angle of the gear teeth-forming features of the second tapered gear mold.
  • the mold may comprise one or more features for forming a hole within a formed gear.
  • the features for forming a hole within a formed gear may be provided as a second component of the mold that may be removed separately from other portions of the mold.
  • the feature forming the hole may extend from an interior end of the mold to form the hole within the formed gear.
  • the hole-forming feature may be configured to form a through-hole extending entirely through the injection-molded gear.
  • the hole forming feature may be configured to form a blind hole extending only partially through the interior of the injection-molded gear.
  • the mold comprises two hole-forming features (one hole-forming feature formed as a part of each of the two-part mold, so as to form blind holes extending into opposing ends of the compound gear.
  • the hole-forming features may have different diameters (e.g., a diameter of a hole-forming feature forming a hole extending into the large end of the compound gear may have a larger diameter than the diameter of a hole-forming feature forming a hole extending into the smaller end of the compound gear).

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)

Abstract

Un engrenage composite moulé par injection ayant un angle d'hélice constant est pourvu d'au moins deux sections d'engrenage, chaque section d'engrenage étant effilée. Chacune des au moins deux sections d'engrenage a un conducteur variable, cependant, l'engrenage composite peut être retiré d'un moule d'injection par torsion et retrait de l'engrenage moulé à travers une extrémité axiale d'un moule en deux parties utilisé pour former l'engrenage moulé.
PCT/IB2021/051548 2020-03-03 2021-02-24 Engrenage hélicoïdal et son procédé de fabrication WO2021176304A1 (fr)

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Application Number Priority Date Filing Date Title
DE112021001392.0T DE112021001392T5 (de) 2020-03-03 2021-02-24 Schraubenrad und herstellungsverfahren dafür

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US202062984441P 2020-03-03 2020-03-03
US62/984,441 2020-03-03

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WO2021176304A1 true WO2021176304A1 (fr) 2021-09-10

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WO (1) WO2021176304A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT525262B1 (de) * 2021-12-13 2023-02-15 Miba Sinter Austria Gmbh Verfahren zum Pressen eines Grünlings

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4864893A (en) * 1986-07-28 1989-09-12 Kabushiki Kaisha Toshiba Planetary gear having its orbital gears out of phase
US5012691A (en) * 1985-10-16 1991-05-07 Ecia - Equipements Et Composants Pour L'industrie Automobile Cluster of molded gears with helical teeth
WO2001048397A2 (fr) * 1999-12-28 2001-07-05 Diro Gmbh & Co. Kg Dispositif d'ajustement
US20020098260A1 (en) * 2001-01-19 2002-07-25 Samsung Electronics Co., Ltd. Die unit for injection molding
US20020098261A1 (en) * 2001-01-19 2002-07-25 Samsung Electronics Co., Ltd. Die unit for injection molding
DE202005008274U1 (de) * 2004-06-03 2005-10-20 Iku Holding Montfoort B.V. Getriebe
US7022042B2 (en) * 2004-01-27 2006-04-04 Yakov Fleytman Epicyclic gear train
US20080173119A1 (en) * 2006-12-27 2008-07-24 Enplas Corporation Injection-molded resin bevel gear
US20100307274A1 (en) * 2008-02-07 2010-12-09 Enplas Corporation Worm Wheel, Method of Producing Injeciton-Molding Die for Worm Wheel, and Method of Producing Worm Wheel
CN202367909U (zh) * 2011-11-24 2012-08-08 深圳市兆威机电有限公司 斜齿轮模具的复位机构及斜齿轮模具
US20160017976A1 (en) * 2014-07-18 2016-01-21 Canon Kabushiki Kaisha Compound gear, method for manufacturing the same, image forming apparatus, consumables, and image processing apparatus
WO2018218363A1 (fr) * 2017-05-31 2018-12-06 Genesis Robotics And Motion Technologies Canada, Ulc Actionneur à réducteur de vitesse
WO2018229737A1 (fr) * 2017-06-17 2018-12-20 Genesis Robotics And Motion Technologies Canada, Ulc Amplificateur de couple
WO2019051614A1 (fr) * 2017-09-16 2019-03-21 Genesis Advanced Technology Inc. Boîte de vitesses à trains planétaires différentiels
WO2020024061A1 (fr) * 2018-08-01 2020-02-06 Genesis Advanced Technology Inc. Boîtier à rouleaux dentés

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5012691A (en) * 1985-10-16 1991-05-07 Ecia - Equipements Et Composants Pour L'industrie Automobile Cluster of molded gears with helical teeth
US4864893A (en) * 1986-07-28 1989-09-12 Kabushiki Kaisha Toshiba Planetary gear having its orbital gears out of phase
WO2001048397A2 (fr) * 1999-12-28 2001-07-05 Diro Gmbh & Co. Kg Dispositif d'ajustement
US20020098260A1 (en) * 2001-01-19 2002-07-25 Samsung Electronics Co., Ltd. Die unit for injection molding
US20020098261A1 (en) * 2001-01-19 2002-07-25 Samsung Electronics Co., Ltd. Die unit for injection molding
US7022042B2 (en) * 2004-01-27 2006-04-04 Yakov Fleytman Epicyclic gear train
DE202005008274U1 (de) * 2004-06-03 2005-10-20 Iku Holding Montfoort B.V. Getriebe
US20080173119A1 (en) * 2006-12-27 2008-07-24 Enplas Corporation Injection-molded resin bevel gear
US20100307274A1 (en) * 2008-02-07 2010-12-09 Enplas Corporation Worm Wheel, Method of Producing Injeciton-Molding Die for Worm Wheel, and Method of Producing Worm Wheel
CN202367909U (zh) * 2011-11-24 2012-08-08 深圳市兆威机电有限公司 斜齿轮模具的复位机构及斜齿轮模具
US20160017976A1 (en) * 2014-07-18 2016-01-21 Canon Kabushiki Kaisha Compound gear, method for manufacturing the same, image forming apparatus, consumables, and image processing apparatus
WO2018218363A1 (fr) * 2017-05-31 2018-12-06 Genesis Robotics And Motion Technologies Canada, Ulc Actionneur à réducteur de vitesse
WO2018229737A1 (fr) * 2017-06-17 2018-12-20 Genesis Robotics And Motion Technologies Canada, Ulc Amplificateur de couple
WO2019051614A1 (fr) * 2017-09-16 2019-03-21 Genesis Advanced Technology Inc. Boîte de vitesses à trains planétaires différentiels
WO2020024061A1 (fr) * 2018-08-01 2020-02-06 Genesis Advanced Technology Inc. Boîtier à rouleaux dentés

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
REVOLUTIONARY PLASTIC GEARBOX WILL OUT-PERFORM METAL BOXES, 21 June 2018 (2018-06-21), XP055853449, Retrieved from the Internet <URL:https://drivesncontrols.com/news/fullstory.php/aid/5735/_91Revolutionary_92_plastic_gearbox91willout-performmetalboxes92.html> *

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