WO1992005372A1 - Engrenage planetaire - Google Patents

Engrenage planetaire Download PDF

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Publication number
WO1992005372A1
WO1992005372A1 PCT/EP1991/001825 EP9101825W WO9205372A1 WO 1992005372 A1 WO1992005372 A1 WO 1992005372A1 EP 9101825 W EP9101825 W EP 9101825W WO 9205372 A1 WO9205372 A1 WO 9205372A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
support wheels
planetary gear
ring gear
sun gear
Prior art date
Application number
PCT/EP1991/001825
Other languages
German (de)
English (en)
Inventor
Gerhard Wagner
Original Assignee
Man Ghh Logistics Gmbh
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 Man Ghh Logistics Gmbh filed Critical Man Ghh Logistics Gmbh
Publication of WO1992005372A1 publication Critical patent/WO1992005372A1/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
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • 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
    • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
    • F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets

Definitions

  • the invention relates to a planetary gear with a bearing base, an input ring gear which can be driven to rotate about an axis of rotation, an output sun gear which is coaxial with it and at least three distributed in the initial direction and meshing with the ring gear and the sun gear and supported on the bearing base .
  • Reducing, ie speed-reducing, planetary gears are generally multi-stage if higher gear ratios are to be achieved.
  • the reduction ratio achievable with one step is comparatively low, since the planet gears are usually rotatably mounted on axes of a planet gear carrier and therefore a comparatively large pitch circle diameter of the planet gears must be provided. This applies in particular if the planet gears are mounted on roller bearings to increase the gearbox efficiency.
  • the manufacturing effort of the ring gear toothing of conventional planetary reduction gears is comparatively complex if high demands are placed on the gear efficiency. It is an object of the invention to provide a step-down planetary gear which, despite its simple design, has a high degree of efficiency with a high step-down ratio.
  • this object is achieved according to the invention in that axially on both sides of the sun gear firmly connected to the bearing base, with the same pitch circle diameters externally toothed support wheels are arranged coaxially with the sun gear and that the sun gear has a pitch circle diameter different from the pitch circle diameter of the support wheels and mesh the planet gears on both sides of the sun gear with the support wheels.
  • the planet gears are supported symmetrically to the ring gear on the support wheels and therefore do not require their own bearing axis.
  • the diameter of the planet gears can thus be kept comparatively small and can also be made considerably smaller than the pitch circle diameter of the sun gear.
  • a large number of planet gears can be distributed around the circumference of the sun gear and a high power split can be achieved.
  • a high reduction ratio of, for example, 1:50 and more can be achieved if the pitch circle diameter of the support wheels differs only slightly from the pitch circle diameter of the sun gear.
  • the pitch circle diameter of the support wheels can be chosen larger than the pitch circle diameter of the sun gear, so that a high reduction is achieved in a single gear stage.
  • this has the advantage that the inner toothing of the ring gear, which is more complicated to manufacture, is loaded only with comparatively small tooth forces, while high tooth forces act on the sun wheel toothing, which is easier to manufacture.
  • This also has a favorable effect on the transmission degree, since high efficiencies can be achieved even if no excessive demands are placed on the production quality of the ring gear toothing.
  • the planet gears can be designed as stepped gears and on both sides of a first gear stage meshing with the ring gear and the sun gear have second gear stages which each have the same pitch circle diameter and mesh with the support wheels.
  • the pitch circles can be selected to be the same as the pitch circles.
  • the toothing regions of the planet gears meshing with the ring gear, the sun gear and the two support wheels have the same toothing, in particular involute toothing, and that the toothing of the Sun gear and the support wheels for generating different rolling circles have profile-shifted teeth.
  • the planet gears are expediently axless, one-piece gears, which are guided axially with their end faces on guide elements, for example sliding rings or the like.
  • the guide elements can be provided on guide cheeks of the bearing base of the transmission or the support wheels, but are in particular arranged on guide cheeks of the ring gear, which enclose the planet gears between them.
  • the ring gear axially on both sides of the planet gears on guide cheeks which radially overlap the support wheels on the axially opposite sides and axially guide the ring gear relative to the bearing base.
  • the guide cheeks of the ring gear can also be guided axially via slide rings on the bearing base, but in particular on the outer sides of the support wheels pointing away from one another.
  • a bearing projection protruding outwards from the sun gear is expediently provided on at least one support wheel, on which the guide cheek is preferably rotatably mounted by means of a roller bearing.
  • the planet wheels act similarly to the rollers of a roller bearing, so that in a preferred variant the ring gear is also mounted directly on the support wheels via the planet wheels.
  • the ring gear is expediently installed with radial preload.
  • the ring gear and its guide cheeks form a closed annular chamber, the guide cheeks being sealed by sealing rings to the support wheels and the support rings by sealing rings to the sun gear.
  • the planetary gear thus forms a sealed unit in which the ring chamber can be used to hold lubricant.
  • the bearing base which can have the shape of a gear housing, for example, firmly connects the two support wheels to one another.
  • the sun gear which in turn can be guided axially, for example, via sliding rings on the support wheels, can have a hub provided with internal splines for mounting on an output gear. include wave.
  • Such a planetary gear can be combined, for example, with a drive motor to form a unit and used, for example, as a plug-in drive in crane trolleys or the like.
  • For the drive connection of the ring gear it is expediently provided with external teeth, in particular for a toothed belt. In this way, the outlay on construction parts is reduced even further.
  • FIG. 1 shows an axial longitudinal section through half of a planetary reduction gear.
  • FIG. 2 shows an axial cross section through a quadrant of the planetary gear, seen along a line II-II in FIG. 1;
  • Fig. 3 shows an axial longitudinal section through half of a variant of a planetary reduction gear
  • Fig. 4 shows an axial longitudinal section through another
  • the planetary reducer shown in FIGS. 1 and 2 comprises a housing 1 serving as a bearing base, in which a ring gear 5 and a sun gear 7 are arranged rotatably relative to one another coaxially with an axis of rotation 3.
  • a large number of planet gears 13 mesh with each other and with the axis of rotation 3 which are axially parallel have second toothing stages 17, which with external toothing Combinations 19 of axially arranged on both sides of the sun gear 7 support wheels 21.
  • the axially outer toothing stages 17 of the planet gears 9 have the same pitch circle diameter, which is smaller than the pitch circle diameter of the middle toothing stage 15.
  • the pitch circle diameters of the toothings 19 of the two support wheels 21 are the same.
  • the pitch circle diameter of the support wheels 21 is several times larger than the pitch circle diameter of the planet wheels 13.
  • the ring gear 5 forms the input part of the planetary gear and is provided on its outer circumference with teeth 23 for a drive toothed belt 25.
  • the ring gear 5 is axially provided on both sides with circular disk-shaped guide cheeks 27, which are guided radially on their inner circumference via roller bearings 29 on bearing projections 31 of the supporting wheels 21.
  • the bearing lugs 31 protrude axially away from the sun gear 7 and hold the support wheels 21 on the housing 1.
  • the sun gear 7 has a hub 33 which is fitted with an internal spline 35 on a complementary toothed output shaft 37 in a rotationally fixed manner.
  • Rolling bearings 39 seated in the bearing lugs 31 of the support wheels 21 guide the hub 33 axially on both sides of the sun wheel 7 in the radial direction.
  • slide rings 41 arranged between the guide cheeks 27 and the support wheels 21 fixed to the housing guide the ring gear 5 relative to the housing 1.
  • Further slide rings 43 are arranged between the sun gear 7 and the support wheels 21 and fix the sun gear 7 axially relative to the housing 1.
  • the one-piece planet gears 13 are axially supported axially without axles on the teeth 9, 11, 19 and are axially guided by sliding rings 45 between their end faces and the guide cheeks 27 of the ring gear 5.
  • the guide cheeks 27 and the ring gear 5 limit one Annulus, which is sealed by sealing rings 47 on the inner circumference of the guide cheeks 27 to the bearing lugs 31. Further sealing rings 49 seal the bearing lugs 31 to the hub 33 of the sun gear 7. The annular space within the ring gear 5 can therefore receive a lubricant supply in a sealed manner.
  • the pitch circle diameter of the toothing stages 17 is only slightly smaller than the pitch circle diameter of the toothing step 15 and the pitch circle diameter of the sun gear 7 is a multiple of this pitch circle diameter, the planetary gear explained has a comparatively large reduction ratio of 50 and more.
  • more than 10 planet gears 13 are provided.
  • FIGS. 1 and 2 Variants of the planetary reduction gear are to be explained below. Components having the same effect are identified by the reference numbers in FIGS. 1 and 2 and provided with a letter to distinguish them. To explain the structure and the mode of operation, reference is made to the description of FIGS. 1 and 2.
  • FIG. 3 shows a variant of the planetary reduction gear, which differs from the gear of FIG. 1 primarily in that the high number of planet gears in the manner of a ball bearing indicates the radial support of the ring gear and the sun gear the support wheels is used, which considerably reduces the outlay on construction parts.
  • the roller bearings 29, 39 are omitted in the planetary gear of FIG. 3, and the sun gear 7a is supported in the radial direction exclusively via its toothing 11a and the planet gears 13a on the support wheels 21a.
  • the ring gear 5a is exclusively through its teeth 9a and the planet gears 13a are supported radially on the support wheels 21a.
  • the ring gear 5a is installed with radial preload so that the tooth play of the planet gears 13a can be compensated. Otherwise, the planetary gear corresponds to the planetary gear of FIGS. 1 and 2.
  • FIG. 4 shows a variant of the planetary reduction gear, the toothing principle of which can also be used in the gearboxes of FIGS. 1 to 3.
  • 4 includes planet gears 13b which have on their outer circumference a " uniform involute toothing 51, essentially over their entire axial length.
  • the planet gears 13b mesh on the one hand with the involute inner toothing 9b of the ring gear 5b and on the other hand with the Involute toothing 11b of the sun gear 7b and the involute toothing 19b of the two support wheels 21b.
  • the involute toothing 11b, 19b have the same pitch circle diameter, but are profile-shifted to produce different pitch circle diameters are the same, but are also larger than the pitch circle diameter of the involute toothing 11b of the sun gear 7. If necessary, the involute toothing 9b of the ring gear 5b can also be shifted in profile for adaptation. It is understood that in individual cases Prof ilver ⁇ shift either only the sun gear 7b or only the support wheels 11b is sufficient.
  • the advantage of profiled toothing is that it is easier to manufacture, essentially cylindrical, planet gears.
  • the bearing of the wheels of the planetary gear, not shown in FIG. 4, relative to one another, can be designed in accordance with FIGS. 1 to 3.

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

Abstract

Le présent engrenage planétaire comporte une roue solaire (7), une couronne coaxiale correspondante (5) et une pluralité de pignons satellites (13) de type roue à gradins. Les pigons satellites (13) s'engrènent, avec une section de gradin de plus grand diamètre (15), dans la roue à denture intérieure (5) et dans la roue solaire (7), et, avec les sections de gradin de plus petit diamètre (17) disposées axialement des deux côtés de la roue solaire (7), dans des roues-support (21) solidaires du carter. De cette manière il est possible d'utiliser des pignons satellites (13) de taille réduite sans axes, et il est possible de dimensionner l'engrenage planétaire pour obtenir un rapport de réduction important.
PCT/EP1991/001825 1990-09-26 1991-09-25 Engrenage planetaire WO1992005372A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4030489.2 1990-09-26
DE19904030489 DE4030489A1 (de) 1990-09-26 1990-09-26 Planetengetriebe

Publications (1)

Publication Number Publication Date
WO1992005372A1 true WO1992005372A1 (fr) 1992-04-02

Family

ID=6415042

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1991/001825 WO1992005372A1 (fr) 1990-09-26 1991-09-25 Engrenage planetaire

Country Status (2)

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DE (1) DE4030489A1 (fr)
WO (1) WO1992005372A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10314069A1 (de) * 2003-03-25 2004-10-21 Klaus Plath Planetenringgetriebe mit gleich- oder gegeläufigem Sonnenrad
EP1753979A2 (fr) * 2004-06-10 2007-02-21 Moog Inc. Actionneur compact

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19944915A1 (de) 1999-09-14 2001-03-15 Brose Fahrzeugteile Antrieb für Verstellvorrichtungen in Kraftfahrzeugen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1586944A (en) * 1922-05-23 1926-06-01 Ruckstell Sales & Mfg Company Planetary-gear mechanism
FR1533859A (fr) * 1967-08-09 1968-07-19 Compact Orbital Gears Ltd Mécanisme d'engrenage épicycloïdal
FR2227465A1 (fr) * 1973-04-30 1974-11-22 Ct Techniki Okretowej Przed
DE2847513A1 (de) * 1978-11-02 1980-05-14 Curtiss Wright Corp Schwimmendes planetengetriebe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1586944A (en) * 1922-05-23 1926-06-01 Ruckstell Sales & Mfg Company Planetary-gear mechanism
FR1533859A (fr) * 1967-08-09 1968-07-19 Compact Orbital Gears Ltd Mécanisme d'engrenage épicycloïdal
FR2227465A1 (fr) * 1973-04-30 1974-11-22 Ct Techniki Okretowej Przed
DE2847513A1 (de) * 1978-11-02 1980-05-14 Curtiss Wright Corp Schwimmendes planetengetriebe

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10314069A1 (de) * 2003-03-25 2004-10-21 Klaus Plath Planetenringgetriebe mit gleich- oder gegeläufigem Sonnenrad
EP1753979A2 (fr) * 2004-06-10 2007-02-21 Moog Inc. Actionneur compact
EP1753979A4 (fr) * 2004-06-10 2007-12-26 Moog Inc Actionneur compact
CN100441920C (zh) * 2004-06-10 2008-12-10 莫戈公司 结构紧凑的致动器

Also Published As

Publication number Publication date
DE4030489A1 (de) 1992-04-02

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