US20070169580A1 - Worm-gear assembly having a pin raceway - Google Patents

Worm-gear assembly having a pin raceway Download PDF

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Publication number
US20070169580A1
US20070169580A1 US11/340,920 US34092006A US2007169580A1 US 20070169580 A1 US20070169580 A1 US 20070169580A1 US 34092006 A US34092006 A US 34092006A US 2007169580 A1 US2007169580 A1 US 2007169580A1
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US
United States
Prior art keywords
worm
pins
raceway
gear assembly
worm screw
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US11/340,920
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English (en)
Inventor
Eric Carrier
David Carrier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SpinControl Gearing LLC
Original Assignee
SpinControl Gearing 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
Application filed by SpinControl Gearing LLC filed Critical SpinControl Gearing LLC
Priority to US11/340,920 priority Critical patent/US20070169580A1/en
Assigned to SPINCONTROL GEARING LLC reassignment SPINCONTROL GEARING LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CARRIER, ERIC D., CARRIER, DAVID O.
Priority to MYPI20082750A priority patent/MY147527A/en
Priority to RU2008134723/11A priority patent/RU2418213C2/ru
Priority to AU2007210179A priority patent/AU2007210179B2/en
Priority to EP07762885A priority patent/EP1977137B1/en
Priority to JP2008552364A priority patent/JP5253180B2/ja
Priority to KR1020087018383A priority patent/KR101385626B1/ko
Priority to CN201110060008.3A priority patent/CN102102737B/zh
Priority to EP11151627A priority patent/EP2312182A1/en
Priority to DK07762885.7T priority patent/DK1977137T3/da
Priority to AT07762885T priority patent/ATE532991T1/de
Priority to PCT/US2007/001774 priority patent/WO2007089479A2/en
Priority to CN200780002978XA priority patent/CN101371060B/zh
Priority to ES07762885T priority patent/ES2376269T3/es
Priority to PL07762885T priority patent/PL1977137T3/pl
Priority to BRPI0707172-8A priority patent/BRPI0707172A2/pt
Priority to CA2638016A priority patent/CA2638016C/en
Publication of US20070169580A1 publication Critical patent/US20070169580A1/en
Priority to ZA200806261A priority patent/ZA200806261B/xx
Priority to EG2008071250A priority patent/EG24990A/xx
Priority to HK08113049.6A priority patent/HK1123594A1/xx
Priority to US12/800,593 priority patent/US8302502B2/en
Priority to US13/661,388 priority patent/US8601894B2/en
Priority to JP2013007406A priority patent/JP5548788B2/ja
Priority to US14/096,489 priority patent/US8950281B2/en
Abandoned legal-status Critical Current

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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
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F16H1/166—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with members rotating around axes on the worm or worm-wheel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts
    • Y10T74/19651—External type
    • Y10T74/19656—Pin teeth
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19698—Spiral
    • Y10T74/19828—Worm

Definitions

  • the present invention relates to worm-gear assemblies, and more particularly, to worm-gear assemblies in which a worm screw is engaged by pins on the periphery of a wheel.
  • gear systems An important consideration in the design of gear systems is the minimization of friction between gear components.
  • friction between gear components By minimizing friction between gear components, the efficiency of a gear system is increased. For example, in a gear system that is used for the transmission of power, transmission loss due to friction within the system is reduced when friction within the system is reduced. Further, by minimizing friction between gear components, the longevity of a gear system is increased. That is, by reducing inter-component friction in the gear system the rate of frictional wear on the components is reduced, thereby increasing the amount of time the system can be operated before it fails.
  • a common gear system of the prior art includes two or more gears having a circular body.
  • Each gear includes a plurality of “teeth” along the periphery of its circular body.
  • the teeth of the two gears intermesh such that force can be transmitted from one of the gears to the other through the intermeshing teeth.
  • the gear's teeth will exert a force on the teeth of the other gear, causing the other gear to rotate.
  • the sliding of the respective sets of teeth against each other is a source of gear system friction.
  • FIG. 1 is an isometric view of a prior gear system in which rotatable pins have been used in lieu of teeth.
  • a multiple of rotatable pins 5 are positioned along the periphery of a wheel 10 and engage a worm screw 15 .
  • the pins are arranged in a single “row” along the circumference of the wheel.
  • the worm screw has an hourglass shape and has a spiral grove 20 cut into its surface. The pins engage the worm screw by moving through the spiral groove.
  • the gear system of FIG. 1 is typically used to transmit power from a drive shaft 25 to an axel 30 . More specifically, as a torque is applied to shaft 25 in the direction shown by arrow 35 , the groove exerts a force on the pins it engages, causing the wheel to rotate in the direction shown by arrow 40 . Bearings 45 a and 45 b support the wheel while allowing it to rotate.
  • pins 5 As the pins 5 rotate through the groove they are free to turn about their longitudinal axes by virtue of bearings 50 . For example, as pin 7 moves through the groove it rotates in the direction shown by arrow 55 . Since the pins are free to rotate about their longitudinal axes, the friction between the pins and the walls of the groove is reduced. That is, since the pins can rotate about their longitudinal axes they can rotate about the walls of the groove. Whereas, if the pins could not rotate about their longitudinal axes they would have to slide against the walls of the groove.
  • FIG. 2 is a plan view in profile of some of the elements of the gear system of FIG. 1 .
  • FIG. 2 shows pins 5 , bearings 50 and worm screw 15 .
  • spiral groove 20 Also shown are spiral groove 20 , drive shaft 25 and a plurality of internal bearings 60 .
  • the internal bearings are internal to wheel 10 and help support the pins.
  • FIG. 3A illustrates the effect of pin slip.
  • the figure shows a slipped pin entering the spiral groove of the worm screw.
  • the pin does not enter spiral groove 20 smoothly. Indeed, as the pin moves into position to enter the groove, it could strike the base of the groove.
  • FIG. 3B is provided as a contrast to FIG. 3A .
  • FIG. 3B shows how a pin that has not slipped enters the spiral groove of the worm screw.
  • Skid starting is related to the initiation of the rotation shown by arrow 55 . More specifically, as pin 7 exits spiral groove 20 there is no force on the pin to maintain its rotation about its longitudinal axis, thus the rotation of the pin will decrease or stop during the time that it is not within the spiral groove. Thus, as the pin travels about the center of wheel 10 and once again enters groove 20 , the groove exerts a torque about the pin's longitudinal axis. The torque is exerted on the pin by the wall of the groove (see e.g. FIG. 3B ). The initiation of torque between the groove wall and the pin causes the pin to skid rather than roll into the groove, resulting in a roughness in the system's operation, which decreases efficiency and longevity.
  • Any movement of the wheel in direction 80 is a source of wheel misalignment. That is, any movement of the wheel in the direction 80 changes the path of the pins relative to the worm screw. The change in path takes the pins off of their intended path and gives rise to roughness and/or inefficiency of operation.
  • the present invention was conceived to overcome the foregoing problems.
  • a worm-gear assembly includes a worm screw having at least one groove and a wheel having a plurality of rotatable pins along its periphery for engaging the worm screw.
  • the pins are able to rotate in a direction other than a direction of wheel rotation.
  • At least one raceway is provided for contacting pins that are not engaged with the worm screw during operation of the assembly.
  • the invention realizes many advantages over prior worm-gear assemblies.
  • the invention makes possible a rotatable pin type worm-gear assembly capable of smooth operation over a complete performance range, with substantially less wear and tear, greater efficiency, and greater useful life.
  • FIG. 1 is an isometric view of a prior gear system in which rotatable pins have been used in lieu of teeth.
  • FIG. 2 is a plan view in profile of some of the elements of the gear system of FIG. 1 .
  • FIG. 3A illustrates the effect of pin slip.
  • FIG. 3B shows how a pin that has not slipped enters the spiral groove of the worm screw.
  • FIG. 4 is an exploded view of a gear system in accordance with a first embodiment of the present invention.
  • FIG. 5 is an isometric view of the gear system of FIG. 4 in assembled form.
  • FIG. 6 is a profile view of the assembled gear system depicted in FIG. 5 with one of the raceways removed for purposes of illustration.
  • FIG. 7 is an exploded view of a gear system in accordance with a second embodiment of the present invention.
  • FIG. 8 is a detail view of a rotating pin portion of the first and second embodiments.
  • FIG. 9 is a detailed view of how a rotatable pin interfaces with a raceway in accordance with the invention.
  • FIG. 10 is an isometric view of a gear system in accordance with a third embodiment of the invention.
  • FIG. 11 is a cross-sectional view of the gear system of FIG. 10 .
  • FIG. 12 is an isometric cross-sectional view of the gear system of FIG. 10 .
  • FIG. 12A shows a raceway interfacing with a mechanical shifting mechanism.
  • FIG. 12B shows the raceway of FIG. 12A apart from the shifting mechanism.
  • FIGS. 12C-12F illustrate how the shifting mechanism of FIG. 12A functions.
  • FIG. 13 is an exploded view of a gear system in accordance with a fourth embodiment of the present invention.
  • FIG. 14 is an isometric cross-sectional view of the gear system depicted in FIG. 13 .
  • FIG. 15A is a cut-away view of the gear system of FIG. 13 with a portion removed for purposes of illustration.
  • FIG. 15B is a cut-away view of a portion of the elements of FIG. 15A .
  • FIG. 15C is a cut-away view of a portion of the elements of FIG. 15B .
  • FIG. 16 shows a fifth embodiment of a gear system in accordance with the invention.
  • FIG. 17 shows a first alternative embodiment of a pin in accordance with the invention.
  • FIG. 18 shows a second alternative embodiment of a pin in accordance with the invention.
  • FIG. 4 is an exploded view of a gear system in accordance with a first embodiment of the present invention.
  • the gear system includes a worm screw 100 , a worm wheel 105 and two raceways 110 a and 110 b .
  • the worm screw has an hourglass shape and has a multiple of spiral grooves 115 cut into its surface.
  • the wheel includes a multiple of rotatable pins 120 positioned along its circumference. The pins are arranged in a single “row” along the circumference of the wheel and engage the worm screw by moving through the spiral grooves.
  • the pins 120 rotate through the grooves they are free to turn about their longitudinal axes in a manner similar to that described in connection with the FIG. 1 system.
  • the use of bearings 125 allows the pins to rotate about their longitudinal axes. Since the pins are free to rotate about their longitudinal axes, the friction between the pins and the walls of the grooves is reduced. That is, since the pins can rotate about their longitudinal axes they can rotate about the walls of the grooves. Whereas, if the pins could not rotate about their longitudinal axes they would have to slide against the walls of the grooves.
  • the raceways 110 a and 110 b of FIG. 4 include raceway bearing surfaces 130 a and 130 b .
  • surface 130 a is clearly visible while surface 130 b is obscured.
  • the raceway contacts all of the pins that are not engaged with the worm screw.
  • the raceway may contact fewer than all pins that are not engaged with the worm screw. Whether the worm wheel is turning or stationary, either raceway may contact all of the pins that are not engaged with the worm screw, fewer than all pins that are not engaged with the worm screw, or none of the pins.
  • FIG. 5 is an isometric view of the gear system of FIG. 4 in assembled form. As can be seen from FIG. 5 , the raceways are positioned at opposite sides of the worm wheel so as to readily engage those of pins 120 that are not engaged by grooves 115 .
  • FIG. 6 is a profile view of the assembled gear system depicted in FIG. 5 with one of the raceways removed for purposes of illustration.
  • raceway 110 a is not shown in FIG. 6 such that raceway 110 b and raceway surface 130 b are clearly visible.
  • the relative positioning of pins 120 and raceway surface 130 b is also clearly visible.
  • FIG. 7 is an exploded view of a gear system in accordance with a second embodiment of the present invention.
  • the FIG. 7 embodiment is similar to the FIG. 4 embodiment with the exception that raceway 110 b and raceway bearing surface 130 b are not included in the FIG. 7 embodiment.
  • the FIG. 7 embodiment includes a worm screw 135 , a worm wheel 145 and raceway 155 .
  • the worm screw has an hourglass shape and has a multiple of spiral grooves 140 formed in its surface.
  • the wheel includes a multiple of rotatable pins 150 that are positioned along the wheel's circumference. The pins are arranged in a single “row” along the circumference of the wheel and engage the worm screw by moving through the spiral grooves.
  • the raceway includes a raceway bearing surface 160 .
  • the raceway contacts those of pins 150 that are not engaged with the worm screw. That is, as the worm wheel turns the raceway bearing surface contacts those of pins 150 that are not engaged with grooves 140 .
  • the raceway contacts all of the pins that are not engaged with the worm screw.
  • the raceway may contact fewer than all of the pins that are not engaged with the worm screw. Whether the worm wheel is turning or stationary, the raceway may contact all of the pins that are not engaged with the worm screw, fewer than all pins that are not engaged with the worm screw, or none of the pins.
  • FIG. 8 is a detail view of a rotating pin portion of the first and second embodiments.
  • the pins can be rotatable in exclusively the counter-clockwise direction, rotatable in exclusively the clockwise direction, or rotatable in both the clockwise and counter-clockwise directions.
  • the pins are rotatably supported in wheel 145 by bearings 157 .
  • the raceways function to alleviate the problems of pin slip, skid starting and wheel misalignment. More specifically, as the rotation of the worm screw causes the wheel to rotate about its axis, those pins which are not engaged with the worm screw and in contact with a raceway are acted on by the raceway in a manner that keeps them rotating about their longitudinal axes, counters the centrifugal force of the rotating wheel, and counters the worm screw force that urges the wheel toward misalignment (the “misalignment force”).
  • FIG. 9 is a detailed view of how a rotatable pin 165 interfaces with a raceway section 170 .
  • the figure is applicable to raceways 110 a , 110 b and 155 , and to raceway bearing surfaces 130 a , 130 b and 160 .
  • the contact between pin 165 and the raceway imparts a counter-clockwise torque to the pin (represented by arrow 175 ).
  • Torque 175 keeps the pin rotating about its longitudinal axis when it is not in contact with the worm screw, such that the pin is already rotating about its longitudinal axis when it contacts the worm screw and the pin does not skid start. Further, the raceway imparts a downward force (represented by arrow 180 ) countering the centrifugal force due to wheel rotation (represented by arrow 185 ). Still further, the raceway imparts a left-to-right force (represented by arrow 190 ) countering the misalignment force.
  • FIG. 10 is an isometric view of a gear system in accordance with a third embodiment of the invention.
  • the system includes a worm screw 200 having spiral grooves 205 , a worm wheel 210 including rotatable pins 215 , and a raceway 220 .
  • the raceway 220 is a one-piece component having two raceway bearing surfaces 220 a and 220 b formed within its inner surface.
  • FIG. 11 a cross-sectional view of the gear system of FIG. 10 .
  • the cross-section has been taken along line AA′ of FIG. 10 and the FIG. 11 view is that seen when looking in the direction of the arrows shown in FIG. 10 .
  • FIG. 12 is an isometric cross-sectional view of the gear system of FIG. 10 .
  • the cross-section has been taken along line AA′ of FIG. 10 and the view is that looking opposite the direction of the arrows of FIG. 10 .
  • a pin 215 a is urged in a direction “into” the page as a pin 215 b is urged in a direction “outward” from the page.
  • pin 215 b is in contact with bearing surface 220 b .
  • the contact between pin 215 b and surface 220 b causes the pin to rotate about its longitudinal axis (represented by line 217 ) as it moves outward from the page. In this manner, the raceway maintains rotation of the pin about the pin's longitudinal axis as the pin exits the spiral groove of the worm screw.
  • the pin is rotating about its longitudinal axis in a manner complimentary to the longitudinal-axis-rotation that the pin experiences when in contact with the groove.
  • the pin does not skid start.
  • the portion of the pin that extends from the periphery of the wheel and contacts surface 220 b i.e. the “pin head”
  • surface 220 b contacts the lateral surface of the frustum
  • surface 220 b applies a force to the pin in counter-action to the centrifugal force (represented by arrow 235 ).
  • FIG. 11 The dynamics illustrated in FIG. 11 are mirrored in FIG. 12 .
  • FIGS. 11 and 12 were described in the context of the worm screw rotating in the direction indicated by arrow 230 , the invention is equally applicable to rotation of the worm screw in the opposite direction.
  • pin 215 b is urged against raceway bearing surface 220 a , either by the “misalignment force” that the screw imparts to the wheel, or by some shifting mechanism. Once pin 215 b contacts surface 220 a , the misalignment force caused by rotation of the worm screw in a direction opposite direction 230 is countered by a force transmitted through surface 220 a.
  • a gear system according to the invention could be employed in a vehicle drive system such that one direction of rotation of the worm screw corresponds to the “forward” vehicle direction and the other direction of rotation of the worm screw corresponds to the “reverse” vehicle direction.
  • the gear system is preferably employed along with a shifting mechanism, the shifting mechanism being used to urge pins against a first raceway bearing surface when the rotation of the worm screw corresponds to the “forward” vehicle direction and to urge pins against a second raceway bearing surface when rotation of the worm screw corresponds to the “reverse” vehicle direction.
  • FIG. 12A An illustrative shifting mechanism is shown in FIG. 12A .
  • the shifting mechanism shown in FIG. 12A is a mechanical shifting mechanism.
  • the invention is not limited to mechanical shifting mechanisms.
  • suitable shifting mechanisms include electric motor powered rotating threaded shafts, hydraulic actuators, electric solenoids, and hand operated shifting mechanisms and levers.
  • the invention is not limited to the case of the worm screw driving the worm wheel. Rather, the worm wheel could drive the worm screw such that a rotational torque applied to the worm wheel moves the rotatable pins through the groove(s) in the worm screw, and thereby causes the worm screw to rotate.
  • the invention is not limited to raceway bearing surfaces of any particular geometry.
  • the invention is not limited to raceway bearing surfaces having a planar cross-section as shown in FIG. 9 , or a concave cross-section as shown in FIG. 14 . Indeed, upon viewing this disclosure one skilled in the art of the invention will readily appreciate the wide range of suitable raceway geometries.
  • the worm screw of the present invention is not limited to an hourglass shape.
  • the worm screw could have a cylindrical shape.
  • groove or grooves formed in the worm screw are not limited to a spiral form. While spiral grooves are preferred, a wide range of groove configurations are suitable for use with the invention. Upon viewing this disclosure one skilled in the art of the invention will readily appreciate the wide range of suitable groove forms.
  • FIG. 12A shows a raceway 265 of the invention interfacing with a mechanical shifting mechanism 270 .
  • the shifting mechanism is used to position the raceway relative to rotatable pins of a worm wheel.
  • FIG. 12B is provided for comparison purposes, and it shows the raceway of FIG. 12A apart from the shifting mechanism.
  • the mechanical shifting mechanism includes an adjustment screw 270 a , a barrel 270 b and a locking nut 270 c .
  • the adjustment screw is in threaded engagement with the barrel, which is fixedly attached to the raceway. By rotating the adjustment screw within the barrel, the barrel is moved relative to the adjustment screw, and thus the raceway is moved relative to the adjustment screw.
  • the locking nut is also in threaded engagement with the adjustment screw, and when the raceway is correctly positioned through rotation of the adjustment screw, the locking nut is rotated into position to secure the adjustment screw.
  • FIGS. 12C-12F illustrate how the shifting mechanism of FIG. 12A functions.
  • FIGS. 12C-12F show a gear system including the raceway 265 , the mechanical shifting mechanism 270 , a worm wheel 275 and a worm screw 280 .
  • the raceway includes a raceway bearing surface 265 a .
  • the worm wheel includes a multiple of rotatable pins 275 a .
  • the worm screw includes a spiral groove 280 a .
  • FIGS. 12C and 12D show the worm wheel positioned such that the rotatable pins are not in contact with the raceway bearing surface. Accordingly, FIG. 12D shows that the adjustment screw of the shifting mechanism has been rotated within the mechanism's barrel so as to move the raceway away from the worm wheel.
  • FIGS. 12E and 12F show the worm wheel positioned such that the rotatable pins are in contact with the raceway bearing surface. Accordingly, FIG. 12E shows that the adjustment screw of the shifting mechanism has been rotated within the mechanism's barrel so as to move the raceway toward the worm wheel.
  • the screw can be rotated by a hydraulic motor or actuator, or by an electric motor.
  • the locking nut could be replaced by a hydraulic braking mechanism or a fixed stop that is attached to the raceway or that is part of the raceway.
  • FIG. 13 is an exploded view of a gear system in accordance with a fourth embodiment of the present invention.
  • the system includes a worm screw 300 having a spiral groove 305 , a worm wheel 310 including rotatable pins 315 , and a pin raceway 325 having a raceway bearing surface 325 a .
  • the components are secured within a housing 320 .
  • the housing is a one-piece housing.
  • Raceway 325 is formed within the housing's inner surface and is an integral part of the housing.
  • FIG. 14 is an isometric cross-sectional view of the gear system depicted in FIG. 13 .
  • FIG. 15A is a cut-away view of the gear system of FIG. 13 with a portion removed for purposes of illustration.
  • FIG. 15B is a cut-away view of a portion of the elements of FIG. 15A .
  • FIG. 15C is a cut-away view of a portion of the elements of FIG. 15B .
  • FIG. 13 embodiment is not limited to a raceway or raceways that are an integral part of the housing.
  • One or more raceways may be secured to or attached to the housing, rather than being an integral part of the housing.
  • one skilled in the art of the invention will readily appreciate a wide range of manufacturing processes of a raceway or raceways that are secured to or attached to the housing.
  • gear system housing of the FIG. 13 embodiment is preferably formed from a relatively hard, durable, and commercially available material, such as hardened steel, stainless steel or a metal composite.
  • the housing of the FIG. 13 embodiment is not limited to a one-piece housing.
  • the housing may be made up of two or more pieces.
  • FIG. 16 shows a fifth embodiment of a gear system in accordance with the invention.
  • the FIG. 16 embodiment includes a worm wheel 400 , a worm screw 405 , and two pin raceways 410 a and 410 b .
  • the worm wheel has two sets of rotatable pins arranged in respective rows 415 a and 415 b , and the worm screw has a spiral groove 405 a cut into its surface for the purpose of engaging the pins.
  • the raceways are formed on the inner surface of a housing 420 and engage those pins that are not engaged by the worm screw. Only a portion of the housing is shown in cross-section for purposes of clarity of presentation.
  • the gear system of FIG. 16 is used to drive an axel 425 . The operation of the gear system of FIG. 16 is readily appreciated in view of the detailed description of FIGS. 1-15 .
  • FIG. 16 is merely illustrative of a multiple-raceway/multiple-pin-row embodiment of the invention, and that a worm wheel of the invention could have more than two raceways and/or more than two rows of pins.
  • the rotatable pins of the present invention are not limited to any one geometry.
  • FIGS. 17 and 18 are provided.
  • FIG. 17 shows a first alternative embodiment of a pin in accordance with the invention.
  • the drawing shows a pin 500 positioned in a worm wheel 505 and engaging a worm screw 510 .
  • the pin has a head 515 in the shape of a truncated sphere. The head of the pin engages a groove 520 in the worm screw.
  • the pin is supported in wheel 505 by a first bearing 525 , a flange 530 and a second bearing 535 .
  • the bearings and flange are seated in a bore within the wheel, the bore including three sections, a lower section 540 , a middle section 545 , and an upper section 550 .
  • the longitudinal axis of the pin is indicated by line 555 .
  • FIG. 18 shows a second alternative embodiment of a pin in accordance with the invention.
  • the figure shows a pin 600 positioned in a wheel 605 and engaging a worm screw 610 .
  • the pin has a head 615 in the shape of a double-truncated sphere.
  • the head of the pin engages a groove 620 in the worm screw.
  • the longitudinal axis of the pin is indicated by line 655 .
  • the corresponding worm screw groove(s) and raceway bearing surface(s) have a mating shape.
  • the pin of FIG. 17 would “mate with” and “roll along” a concave worm screw groove, and would “mate with” and “roll along” a concave raceway bearing surface.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
US11/340,920 2006-01-26 2006-01-26 Worm-gear assembly having a pin raceway Abandoned US20070169580A1 (en)

Priority Applications (24)

Application Number Priority Date Filing Date Title
US11/340,920 US20070169580A1 (en) 2006-01-26 2006-01-26 Worm-gear assembly having a pin raceway
CA2638016A CA2638016C (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
CN200780002978XA CN101371060B (zh) 2006-01-26 2007-01-23 具有销座圈的蜗轮组件
PL07762885T PL1977137T3 (pl) 2006-01-26 2007-01-23 Zespół przekładni ślimakowej mający bieżnię sworznia
AU2007210179A AU2007210179B2 (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
EP07762885A EP1977137B1 (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
JP2008552364A JP5253180B2 (ja) 2006-01-26 2007-01-23 ピン軌道を有するウォームギア組立体
KR1020087018383A KR101385626B1 (ko) 2006-01-26 2007-01-23 핀 레이스웨이를 갖는 웜 기어 조립체
CN201110060008.3A CN102102737B (zh) 2006-01-26 2007-01-23 具有销座圈的蜗轮组件
EP11151627A EP2312182A1 (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
DK07762885.7T DK1977137T3 (da) 2006-01-26 2007-01-23 Snekkehjulsindretning med tapløbering
AT07762885T ATE532991T1 (de) 2006-01-26 2007-01-23 Schneckengetriebeanordnung mit einer pin- laufstrecke
PCT/US2007/001774 WO2007089479A2 (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
MYPI20082750A MY147527A (en) 2006-01-26 2007-01-23 Worm-gear assembly having a pin raceway
ES07762885T ES2376269T3 (es) 2006-01-26 2007-01-23 Conjunto de engranaje de tornillo sin fin que tiene un anillo de rodadura de clavijas.
RU2008134723/11A RU2418213C2 (ru) 2006-01-26 2007-01-23 Узел червячной передачи, имеющий дорожку для пальцев
BRPI0707172-8A BRPI0707172A2 (pt) 2006-01-26 2007-01-23 conjunto de engrenagem de rosca sem fim, e, método de operação do mesmo
ZA200806261A ZA200806261B (en) 2006-01-26 2008-07-18 Worm-gear assembly having a pin raceway
EG2008071250A EG24990A (en) 2006-01-26 2008-07-24 Worm-gear assembly having a pin raceway.
HK08113049.6A HK1123594A1 (en) 2006-01-26 2008-11-28 Worm-gear assembly having a pin raceway
US12/800,593 US8302502B2 (en) 2006-01-26 2010-05-18 Worm-gear assembly having a pin raceway
US13/661,388 US8601894B2 (en) 2006-01-26 2012-10-26 Worm-gear assembly having a pin raceway
JP2013007406A JP5548788B2 (ja) 2006-01-26 2013-01-18 ウォームギア組立体
US14/096,489 US8950281B2 (en) 2006-01-26 2013-12-04 Worm-gear assembly having a pin raceway

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US13/661,388 Expired - Fee Related US8601894B2 (en) 2006-01-26 2012-10-26 Worm-gear assembly having a pin raceway
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US14/096,489 Expired - Fee Related US8950281B2 (en) 2006-01-26 2013-12-04 Worm-gear assembly having a pin raceway

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EP (2) EP2312182A1 (ru)
JP (2) JP5253180B2 (ru)
KR (1) KR101385626B1 (ru)
CN (2) CN101371060B (ru)
AT (1) ATE532991T1 (ru)
AU (1) AU2007210179B2 (ru)
BR (1) BRPI0707172A2 (ru)
CA (1) CA2638016C (ru)
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HK (1) HK1123594A1 (ru)
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US20120000305A1 (en) * 2009-03-10 2012-01-05 Illinois Tool Works Inc. Hybrid enveloping spiroid and worm gear
US20130061704A1 (en) * 2011-09-09 2013-03-14 Illinois Tool Works Inc. Enveloping spiroid gear assemblies and method of manufacturing the same
WO2015086352A1 (de) * 2013-12-09 2015-06-18 Weiss Gmbh Antriebseinheit
US20150343553A1 (en) * 2012-06-14 2015-12-03 Aktiebolaget Skf Machine arrangement
CN106199238A (zh) * 2016-06-23 2016-12-07 国网山东省电力公司济阳县供电公司 便携式电气设备状态观测仪
WO2016185357A3 (en) * 2015-05-19 2018-01-11 STEENKAMP, Sarah-may Adjustable ballast bulb for a sailing vessel
WO2016185356A3 (en) * 2015-05-19 2018-01-18 STEENKAMP, Sarah-may Sailing vessel
CN109869466A (zh) * 2019-03-20 2019-06-11 盐城瑞升齿轮有限公司 高速插秧机变速齿轮结构
CN110259915A (zh) * 2019-06-14 2019-09-20 成都中良川工科技有限公司 一种可消除传动间隙的变速装置及其间隙消除方法

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CN103062336A (zh) * 2012-12-24 2013-04-24 台州金剑机械制造有限公司 一种滚动锥销蜗轮环面蜗杆传动结构
EP2792893B1 (en) * 2013-04-19 2016-02-10 Aktiebolaget SKF Cage with parallel pockets for rolling bearing
CN103707129A (zh) * 2013-12-18 2014-04-09 烟台环球机床附件集团有限公司 一种高效精密无背隙陶瓷球分度装置
CN106624745B (zh) * 2015-11-02 2019-05-17 英属维尔京群岛商鉱腾有限公司 滚轮组装定位机构
CN110056610A (zh) * 2017-08-31 2019-07-26 赵若君 一种蜗轮
KR102007321B1 (ko) * 2018-05-10 2019-08-05 설인환 동력전달장치
TWM572942U (zh) * 2018-05-23 2019-01-11 邱垂財 雙列式滾齒凸輪傳動結構
CN113007312B (zh) * 2019-06-14 2022-07-08 成都中良川工科技有限公司 一种自转驱动的蜗轮
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120000305A1 (en) * 2009-03-10 2012-01-05 Illinois Tool Works Inc. Hybrid enveloping spiroid and worm gear
US20130061704A1 (en) * 2011-09-09 2013-03-14 Illinois Tool Works Inc. Enveloping spiroid gear assemblies and method of manufacturing the same
US20150343553A1 (en) * 2012-06-14 2015-12-03 Aktiebolaget Skf Machine arrangement
US9897514B2 (en) * 2012-06-14 2018-02-20 Aktiebolaget Skf Machine arrangement
WO2015086352A1 (de) * 2013-12-09 2015-06-18 Weiss Gmbh Antriebseinheit
WO2016185357A3 (en) * 2015-05-19 2018-01-11 STEENKAMP, Sarah-may Adjustable ballast bulb for a sailing vessel
WO2016185356A3 (en) * 2015-05-19 2018-01-18 STEENKAMP, Sarah-may Sailing vessel
US10322773B2 (en) 2015-05-19 2019-06-18 Sarah-May Steenkamp Adjustable ballast bulb for a sailing vessel
US10710685B2 (en) 2015-05-19 2020-07-14 Sarah-May Steenkamp Sailing vessel
CN106199238A (zh) * 2016-06-23 2016-12-07 国网山东省电力公司济阳县供电公司 便携式电气设备状态观测仪
CN109869466A (zh) * 2019-03-20 2019-06-11 盐城瑞升齿轮有限公司 高速插秧机变速齿轮结构
CN110259915A (zh) * 2019-06-14 2019-09-20 成都中良川工科技有限公司 一种可消除传动间隙的变速装置及其间隙消除方法

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JP2013100906A (ja) 2013-05-23
WO2007089479A2 (en) 2007-08-09
US8950281B2 (en) 2015-02-10
CN102102737B (zh) 2014-03-26
JP2009524785A (ja) 2009-07-02
EP1977137A2 (en) 2008-10-08
PL1977137T3 (pl) 2012-03-30
DK1977137T3 (da) 2012-01-23
US20100229667A1 (en) 2010-09-16
US8601894B2 (en) 2013-12-10
MY147527A (en) 2012-12-31
CN101371060A (zh) 2009-02-18
BRPI0707172A2 (pt) 2011-04-26
ZA200806261B (en) 2009-07-29
HK1123594A1 (en) 2009-06-19
KR20080095864A (ko) 2008-10-29
RU2418213C2 (ru) 2011-05-10
EP1977137B1 (en) 2011-11-09
AU2007210179A1 (en) 2007-08-09
KR101385626B1 (ko) 2014-04-15
RU2008134723A (ru) 2010-03-10
US8302502B2 (en) 2012-11-06
ATE532991T1 (de) 2011-11-15
WO2007089479A3 (en) 2007-10-04
EP2312182A1 (en) 2011-04-20
US20130047766A1 (en) 2013-02-28
JP5548788B2 (ja) 2014-07-16
US20140090502A1 (en) 2014-04-03
JP5253180B2 (ja) 2013-07-31
CA2638016A1 (en) 2007-08-09
ES2376269T3 (es) 2012-03-12
CN102102737A (zh) 2011-06-22
AU2007210179B2 (en) 2012-08-16
EG24990A (en) 2011-04-13
CA2638016C (en) 2014-08-19

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