EP1415100A1 - Train d'engrenages a modules emboites - Google Patents

Train d'engrenages a modules emboites

Info

Publication number
EP1415100A1
EP1415100A1 EP99935795A EP99935795A EP1415100A1 EP 1415100 A1 EP1415100 A1 EP 1415100A1 EP 99935795 A EP99935795 A EP 99935795A EP 99935795 A EP99935795 A EP 99935795A EP 1415100 A1 EP1415100 A1 EP 1415100A1
Authority
EP
European Patent Office
Prior art keywords
gear
module
housing
planetary gears
modules
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.)
Withdrawn
Application number
EP99935795A
Other languages
German (de)
English (en)
Other versions
EP1415100A4 (fr
Inventor
Ivan Romero
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.)
Mattel Inc
Original Assignee
Mattel 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 Mattel Inc filed Critical Mattel Inc
Publication of EP1415100A1 publication Critical patent/EP1415100A1/fr
Publication of EP1415100A4 publication Critical patent/EP1415100A4/fr
Withdrawn legal-status Critical Current

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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/033—Series gearboxes, e.g. gearboxes based on the same design being available in different sizes or gearboxes using a combination of several standardised units
    • 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
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears

Definitions

  • This invention relates generally to gear systems and particularly to gear systems known as planetary gear systems.
  • a speed reduction gear set is commonly used to divide the speed down for eventual use due to the corresponding torque multiplication which occurs.
  • the use of gear systems to trade speed versus torque has been basic in the design of such systems and is well known.
  • the first is often referred to as "speed reduction" gear system in which the rotational speed output of a high speed motor is reduced by a series of gears to a lower speed while the torque is correspondingly multiplied up.
  • the second system is the converse of the speed reduction gear in which the rotational output of a slower motor is increased in speed by a plurality of gears with a corresponding multiple for loss of torque.
  • gear systems are known as a "planetary” gear system.
  • the name for such planetary gear systems arises out of the arrangement of gears which in some sense is similar to the rotation of planets about the sun.
  • gear systems are often also referred to as “sun” gears.
  • a plurality of gears are rotatably supported on fixed posts at radial positions from a center.
  • the gears are spaced and of such size that a center gear may be inserted into the center of the gear array and engage all of the planetary gears.
  • the planetary gear system further includes a ring gear encircling the outer portions of the planetary gears.
  • the coupled portions of the gear system are the ring gear and the center gear, both of which engage the planetary gears.
  • speed reduction occurs when the center gear is the driven power input gear and the ring gear is the output gear.
  • speed increase is accomplished when the outer ring gear is the power driven gear and the center gear is coupled to the load.
  • the ruggedness and flexibility of such gear systems has allowed designers to utilize planetary gear systems in a wide range of applications extending from heavy industrial and commercial equipment to miniaturized toys powered by small battery driven motors. Despite this wide range of use and adaptability in each instance, the foregoing advantages are equally realized making the planetary gear system a popular choice by designers.
  • U.S. Patent 5,240,462 issued to Mochizuki et al sets forth a PLANETARY REDUCTION GEAR having pairs of partial planetary gears, two partial internal gears, and a sun gear in which one of the partial gears is fixed to the input shaft or to the casing while the other gear is loosely connected to the input shaft or the casing by a spiral coupling.
  • the spiral coupling allows the partial gear to move in a spiral direction.
  • Means are provided for pushing the partial gear in the axial direction moving the partial gear.
  • U.S. Patent 4,186,626 issued to Chamberlain sets forth a WHEEL FINAL DRIVE ASSEMBLY in which a two stage or double reduction planetary gearing mechanism is positioned within wheel hubs of a vehicle and connected to the vehicle drive wheels.
  • a drive axle shaft for interconnecting a vehicle power train differential and gearing mechanism together with a separate part hollow hub having positioning faces containing an axially positioning gears of the mechanism is used.
  • U.S. Patent 3,815,445 issued to Gorrell sets forth a VARIABLE SPEED PLANETARY TRANSMISSION including a succession of planetary gear trains adapted to provide a relatively uniform step or percentage change between speed ratios.
  • U.S. Patent 4,334,440 issued to Fonck sets forth an AUTOMATIC TRANSMISSION providing a continuously varying speed characteristic using a plurality of planetary gear sets commonly coupled in pairs and having different gear ratios to vary the speed reduction or multiplication.
  • U.S. Patent 2,529,423 issued to Schou sets forth a TRANSMISSION MECHANISM in which a planetary gear system utilizes a beveled gear driving a plurality of smaller beveled gears in a four-sided arrangement to couple operative power.
  • U.S. Patent 5,012,693 issued to Enomoto et al sets forth a DRIVE MECHANISM FOR REAR-VIEW MIRROR ASSEMBLY OF MOTOR-DRIVEN FOLDING TYPE which includes an electric motor fixed on a mirror housing which in turn is supported rotatably on a shaft fixed to the mirror base.
  • the mirror base is secured to a vehicle body such that it may be turned between normal and retracted positions by the drive mechanism.
  • U.S. Patent 5,136,197 issued to Hallett sets forth a REACTION CONTAINMENT DRIVE FOR POWER TOOL having a motor supporting a rotatable case within the tool casing and an internal drive shaft.
  • a planetary gear set is an integral portion of the drive.
  • a gear system comprising: a plurality of gear modules each having, a housing having a plurality of planetary gears supported by the housing, a rotor having an internal ring gear engaging the planetary gears and an output gear, and attachment means for securing each of the gear modules to another of the gear modules in the plurality of gear modules such that its output gear engages the plurality of planetary gears of another of the gear modules.
  • Figure 1 sets forth a perspective view of an exemplary gear system module
  • Figure 2 sets forth a perspective assembly view of the module of Figure 1; and Figure 3 sets forth a section view of a plurality of nested gear modules constructed in accordance with the present invention.
  • Gear module 10 includes a generally cylindrical housing 11 supporting a plurality of forwardly extending spring clips 14, 15, 16, and 17 which in turn define end portions having a gripping edge 24, 25, 26, and 27, respectively.
  • Spring clips 14 through 17 are preferably fabricated of a resilient spring material such as resilient plastic or spring steel or the like.
  • Housing 11 further defines an interior cavity 13 within which a generally cylindrical ring gear rotor 30 is received.
  • Ring gear rotor 30 further supports a forwardly extending center gear 31.
  • rotor 30 defines an interior ring gear 32 which is received upon a plurality of planetary gears (gears 41 through 44 seen in Figure 2) .
  • rotor 30 is rotatably supported within interior cavity 13 and is rotatable in either direction as indicated by arrows 36.
  • gear module 10 forms a single stage which, as is described below, may be combined with other similar modules in a stacked arrangement using the attachment of spring clips 14 through 17 to provide a succession of gear modules to form a gear system.
  • gear module 10 is fabricated of substantially rigid components and with the exception of spring clips 14 through 17 which are resilient, the remainder of gear module 10 is preferably fabricated of relatively rigid material such as molded plastic or composite material or steel as required for a particular application.
  • FIG. 2 sets forth a perspective assembly view of module 10 showing ring gear rotor 30 in partial section.
  • module 10 includes a housing 11 having a generally cylindrical shape and defining a cylindrical wall 12. Housing 11 further defines a generally planar back wall 40 supporting a plurality of posts 61, 62, 63, and 64 which receive and rotatably support a plurality of planetary gears 41, 42, 43, and 44. Gears 41 through 44 are secured to posts 61 through 64 in a rotatable attachment in which posts 61 through 64 are received within apertures 51 through 54 formed respectively in gears 41 through 44.
  • Back wall 40 further defines a center aperture 45 which is aligned with the center line of the arrangement of planetary gears 41 through 44.
  • Gear module 10 is completed by ring gear rotor 30 which, as described above, is generally cylindrical and defines an outer face 35 and an outer wall 34. As is also described above, rotor 30 supports a center gear 31 extending forwardly from outer face 35. As can be seen by the broken section of Figure 2, ring gear rotor 30 defines an interior cavity 33 and an internal ring gear 32. In accordance with conventional ring gear fabrication, internal ring gear 32 will be understood to extend the entire circumference of ring gear rotor 30. With planetary gears 41. through 44 received upon posts 61 through 64, rotor 30 is assembled to housing 11 such that planetary gears 41 through 44 each engage internal ring gear 32.
  • the resulting assembly allows the insertion of a center gear identical to center gear 31 through aperture 45 of back wall 40 to mutually engage each of planetary gears 41 through 44,
  • the center gear commonly coupled to the plurality of planetary gears is referred to as the "sun" gear.
  • the completed and assembled gear module formed by housing 11, gears 41 through 44, and ring gear rotor 30 produces the module shown in Figure 1 in which rotation of rotor 30 produces corresponding rotations of gears 41 through 44.
  • a gear substantially identical to gear 31 is inserted through aperture 45 engaging gears 41 through 44.
  • the resulting gear system of module 10 provides rotation of ring gear rotor 30 in response to such rotation of an inserted center gear.
  • rotation of ring gear rotor 30 produces a rotation of the inserted center gear.
  • center gear 31 provides the output gear of gear module 10.
  • module 10 once completed is configured to receive an identical gear module in a nesting arrangement in which center gear 31 becomes the input gear passing through the aperture formed in the next gear module in the manner shown in Figure 3 as center gear 31 passes through aperture 86 of housing 81 of module 80.
  • the speed and torque relationship between the input gear inserted through center aperture 45 and the output gear provided by center gear 31 is determined by the relative sizes of the center gear, the planetary gears, and the internal ring gear of the module.
  • gear module 10 there exists a drive characteristic such as speed reduction and torque multiplication which, in essence, defines the gear module. It will also be noted that successive gear modules having defined characteristics of gear ratio and torque ratio are multiplied when two or more gear modules are nested and engaged as set forth below in Figure 3.
  • Figure 3 sets forth a section view of a planetary gear system utilizing a plurality of gear modules coupled in a serial or stacked configuration.
  • a motor 70 fabricated in accordance with conventional fabrication techniques, includes an output shaft 71 supporting an output gear 72.
  • Figure 3 is intended to illustrate the nested or stacked configuration of a number of substantially identical gear modules to produce an overall gear ratio between output gear 72 of motor 70 and the final output gear of the end module (gear 134 of module
  • module 10 includes a generally cylindrical housing 11 having a back wall 40 and an interior cavity 23.
  • Back wall 40 further defines a center aperture 45 and a plurality of forwardly extending posts 61 through 64 (posts 62 and 64 seen in Figure 2) .
  • Housing 11 further defines an edge 28 and a plurality of forwardly extending spring clips such as spring clips 14 and 16.
  • Spring clip 14 defines a gripping edge 24 while spring clip 16 defines a gripping edge 26.
  • a ring gear rotor.30 defines an interior cavity 33 and a center gear 31.
  • Ring gear rotor 30 further defines an internal ring gear 32 extending about the outer wall of ring gear rotor 30.
  • Module 10 is assembled in the manner described above in Figures 1 and 2 and is completed by the insertion of ring gear rotor 30 into interior cavity 23 of housing 11 such that ring gear 32 engages planetary gears 41 through 44 (gears 42 and 44 seen in Figure 2).
  • Motor 70 and shaft 71 are positioned with respect to module 10 such that output gear 72 is inserted through aperture 45 and commonly engages each of planetary gears 41 through 44 (gears 42 and 44 seen in Figure 2).
  • gear module 80 which is substantially identical to gear module 10, is secured to gear module 10 by the cooperation of edge 28 of housing 11 and spring clips 14 through 17 (clips 13 and 17 shown in Figure 2) .
  • module 80 includes a generally cylindrical housing 81 having a cylindrical wall 94 and a center aperture 45.
  • Housing 81 supports a plurality of forwardly extending posts such as posts 96 and 98 which support planetary gears 97 and 99 in a rotatable attachment.
  • Housing 81 further defines an edge 82 and a plurality of forwardly extending spring clips such as spring clips 90 and 91.
  • housing 81 supports a greater plurality of forwardly extending spring clips similar to those shown in Figure 2 for module 10.
  • the number of spring clips for any given module is subject to variation should the user desire in meeting certain design requirements. It is equally feasible to select nested or stacked gear modules which are constructed in accordance with gear module 10 but which have different gear sizes to produce different gear ratios.
  • gear module 80 is substantially identical to gear module 10.
  • Module 80 further includes a ring gear rotor 83 having an internal ring gear 95 and a center gear 85. As was the case in the assembly of module 10, ring gear rotor 83 is received upon the plurality of planetary gears such as gears 97 and 99 in engagement with internal ring gear 95.
  • the multiple module gear system shown in Figure 3 provides a plurality of stacked or nested gears coupled between module 10 and the final gear module 110.
  • each successive module is secured to the preceding module by the engagement of spring clips having gripping edges and the outer edge of the succeeding housing.
  • module 80 having spring clips 90 and 91 which define gripping edges 92 and 93 will be understood to couple to and engage the next succeeding gear module in the manner in which spring clips 14 and 16 engage housing 81 of module 80.
  • Module 110 together with end cap 140 show the cooperation of the last or end most module and end cap 140.
  • module 110 includes a housing 111 defining an aperture 113 through which center gear 100 extends in the manner described above for modules 10 and 80.
  • Module 110 is preferably formed substantially identical to module 10 and thus includes a housing 111 supporting a plurality of posts such as posts 125 and 131, each of which supports a rotatable planetary gear such as gears 124 and 130.
  • Module 110 further includes a ring gear rotor 132 having an internal ring gear 133.
  • ring gear rotor 132 is received within housing 111 such that internal ring gear 133 engages the planetary gears of the module such as gears 124 and 130.
  • Housing 111 includes a plurality of forwardly extending spring clips such as spring clips 120 and 122 having respective gripping edges such as edges 121 and 123.
  • Ring gear rotor 132 further includes a forwardly extending center gear 134.
  • an end cap 140 is secured to housing 111 of module 110 to maintain the captivity of ring gear rotor 132 within housing 111.
  • end cap 140 is generally cylindrical in shape and defines a center aperture 142, a forward edge 141, and a back 143.
  • the assembly of end cap 140 to module 110 is carried forward in substantially the same manner as assembly between successive gear modules in that the spring clips of module 110 such as clips 120 and 122 are received upon the outer surface of end cap 140 and snap-fit thereto through the engagement of the respective gripping edges of the spring clips such as edges 121 and 123 of spring clips 120 and 122.
  • the gear ratio or ratio of speed and torque between output gear 72 of motor 70 and the final module gear shown as center gear 134 of module 110 is determined by the multiplication of the individual ratios of each module.
  • the overall gear ratio of the system is 64 to 1. That is to say four times four times four. If two gear modules are used in the system and each has a 4 to 1 gear ratio, then the system exhibits a 16 to 1 overall gear ratio.
  • gear ratios may be provided by the various modules which are nested or stacked together in accordance with the present invention.
  • the preferable fabrication of the present invention is that in which the individual gear models are substantially identical both in structure and in gear ratio. This facilitates the high volume production of a great number of identical gear modules which may then be combined in the appropriate number in a given fabrication or design to produce the overall gear ratio desired.
  • the module of the present invention may be fabricated using virtually any sufficiently rigid material, it has been found extremely advantageous to utilize the present invention module gear system using low cost injection molded plastic components which are relatively strong and rigid, relatively quiet in their operation, and which are well suited to low cost, high volume production.
  • modulized gear system is not limited to the illustrated use in which a motor drives the gear module input and a gear shaft forms its output.
  • the system of the present invention is bidirectional in that the roles may be reversed between input and output.
  • power may be applied to center gear 134 in the system of Figure 3 and the driven output gear may take the place of output gear 72 of motor 70.
  • motor 70 may be any load such as a generator or lifting device without departing from the spirit and scope of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

Ce train d'engrenages comporte plusieurs modules d'engrenages (10) pourvus, chacun, d'attaches à ressort (14, 15, 16, 17) assurant un raccordement à encliquetage avec un autre module de structure identique (110) ainsi qu'un accouplement des engrenages entre modules. Chaque module possède un carter (11), dans lequel plusieurs engrenages planétaires (41, 42, 43, 44) sont montés rotatifs autour d'une ouverture commune (45), ainsi qu'un rotor à engrenages (30) venant se placer sur les engrenages planétaires et possédant une couronne de train planétaire intérieure (32) en prise avec les engrenages planétaires. Chaque rotor de chaque module comporte un engrenage central faisant saillie vers l'extérieur (31). Chaque carter de chaque module d'engrenages comporte plusieurs attaches à ressort (14, 15, 16, 17), dont les rebords de prise (24, 25, 26, 27) viennent se placer sur la face extérieure d'un capuchon d'extrémité, et un mécanisme à cliquet venant s'appliquer sur le carter du module d'engrenages suivant. Il est possible de combiner ces modules et ce, quelqu'en soit le nombre ou quasiment, pour obtenir le rapport de démultiplication souhaité, lequel rapport est un multiple des rapports de démultiplication propres à chaque module.
EP99935795A 1998-08-18 1999-07-21 Train d'engrenages a modules emboites Withdrawn EP1415100A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US13643598A 1998-08-18 1998-08-18
US136435 1998-08-18
PCT/US1999/016521 WO2000011372A1 (fr) 1998-08-18 1999-07-21 Train d'engrenages à modules emboîtés

Publications (2)

Publication Number Publication Date
EP1415100A1 true EP1415100A1 (fr) 2004-05-06
EP1415100A4 EP1415100A4 (fr) 2006-04-12

Family

ID=22472852

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99935795A Withdrawn EP1415100A4 (fr) 1998-08-18 1999-07-21 Train d'engrenages a modules emboites

Country Status (4)

Country Link
EP (1) EP1415100A4 (fr)
AU (1) AU5119899A (fr)
CA (1) CA2344813A1 (fr)
WO (1) WO2000011372A1 (fr)

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CA2740358A1 (fr) * 2008-10-12 2010-04-15 Christopher C. Sappenfield Ensembles tournants, mecanismes tournants et applications associees
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Also Published As

Publication number Publication date
WO2000011372A1 (fr) 2000-03-02
AU5119899A (en) 2000-03-14
CA2344813A1 (fr) 2000-03-02
EP1415100A4 (fr) 2006-04-12

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