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WO2016004933A1 - Engrenage planétaire à coulissement circulaire - Google Patents

Engrenage planétaire à coulissement circulaire Download PDF

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Publication number
WO2016004933A1
WO2016004933A1 PCT/DE2015/200230 DE2015200230W WO2016004933A1 WO 2016004933 A1 WO2016004933 A1 WO 2016004933A1 DE 2015200230 W DE2015200230 W DE 2015200230W WO 2016004933 A1 WO2016004933 A1 WO 2016004933A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring gear
teeth
gear
planetary gears
segments
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.)
Ceased
Application number
PCT/DE2015/200230
Other languages
German (de)
English (en)
Inventor
Franz Kurth
Ralph Schimpf
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2016004933A1 publication Critical patent/WO2016004933A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H1/321—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear the orbital gear being nutating
    • 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
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with the orbital gear having internal gear teeth

Definitions

  • the invention relates to a Kreisschiebeplanetenradgetriebe according to the closer defined in the preamble of claim 1.
  • Such a Kreisschiebeplanetenradgetriebe is known from DE 195 18 160 A1.
  • noise may occur in the case of circular displacement of the drive pulleys due to inaccurate engagement of these in the planetary gears, increased friction and malfunctions.
  • the invention is therefore an object of the invention to provide a Kreisschiebeplanetenradgetriebe of the aforementioned type, which is simple in construction and ensures safe operation,
  • the object is achieved by the Merkmaie of claim 1. Further advantageous embodiments will become apparent from the respective dependent claims, the description and the drawings.
  • the planet gears each have an axially continuous external toothing for engagement in the first and second Hohirad.
  • the Pianetenzier gradios are particularly easy and inexpensive hersteilbar.
  • the internal gears of the ring gears thereby different numbers of teeth can be achieved in a simple manner by profile displacement,
  • First and second Hohirad can be supported radially supported on overlapping axial end portions.
  • the second ring gear is preferably radially mounted at its end section on the end section of the first ring gear.
  • the first ring gear, the Pianetengen and the drive pulleys form a first gear stage with a first Ambiachia and the second ring gear, the planet gears and the planet carrier a second gear stage with a second partial translation. It is advantageous if the first Teiiüber acid is greater than the second partial translation. As a result, a self-locking of the transmission is avoided in a simple manner.
  • a total conversion of greater than 200 is achieved, the overall ratio being formed by the product of first and second partial translations. It is advantageous if the tooth numbers of the internal gears of the first and second ring gear have a large difference. Preferably, in this case, the number of teeth of the second ring gear is greater than that of the first.
  • the drive disks are preferably in each case in engagement with at least two planetary gears each time. This ensures that the drive pulleys each have two engagement points with respect to the planetary gears during the circular sliding movement and thus are completely determined in their movement, whereby an exact guidance of the drive pulleys is ensured on the planetary gears. In this way, disturbances are avoided and an effective operation of the Kreisschiebepianetenradgetriebes is ensured.
  • the drive disks each form concave circular-arc-shaped toothed segments with internal teeth for engagement with the planetary gears on the outer circumference.
  • the internal toothing of the successive tooth segments in the circumferential direction preferably has a tooth offset which depends on the respective position of the tooth segments by a predetermined angle relative to one another. Due to the tooth offset an exact tooth engagement between the Pianetenzumn and the tooth segments is achieved. Friction, wear and self-locking in Kreisscheiebepianetenradgetriebe can be easily reduced.
  • the tooth offset of the internal teeth of the successive tooth segments in the circumferential direction is preferred by one of the respective positions of the teeth Tooth segments, the number of teeth of the first ring gear, the number of teeth of the internal teeth of the toothed segments, the number of planetary gears and dependent on the first partial transmission angle determined.
  • the angle is preferably determined by
  • the drive disks each have a predetermined opening angle at the toothed segments for engagement with the planetary gears.
  • the arrangement of the drive pulleys is further optimized in engagement with the planetary gears. It reduces the forces, noise and self-locking forces.
  • the opening angle is preferably determined as a function of the number of planetary gears, the length of the engagement line from its inlet point to its pitch point between the external teeth of the planetary gears and the internal teeth of the toothed segments and depending on the tip circle and pitch circle diameter of the internal teeth of the toothed segments. It is preferable for the opening angle ⁇
  • the drive disks on the outer circumference in each case for engagement with three planetary gears three with these corresponding concave circular arc-shaped toothed segments with internal teeth form each having an opening angle aul undose, which is greater than 180 °.
  • an arrangement with four planet wheels and at least two drive pulleys, each having four toothed segments for engagement with the planetary gears is also conceivable.
  • the opening angle of the internal teeth of the toothed segments is reduced correspondingly, but this is preferably greater than 150 °.
  • the drive disks may each have recesses on the outer circumference in the circumferential direction between the toothed segments.
  • through holes can be provided radially in each case in a radially central region between the outer circumference and a central receiving opening.
  • the drive disks are preferably made in sheet metal and particularly easy to produce by punching.
  • the Kreisschiebeplanetenradgetnebe invention is, for example, particularly advantageous in Versteilantrieben with high ratios and without self-locking used. Brief description of the drawings
  • FIG. 1 shows a side view of a Kreisschiebeplanetenradge- invention drive
  • Figure 2 is a sectional view of the Kreisschiebepianetenradgetriebes
  • Figure 3 is a single view of a drive pulley according to the invention, schematically an enlarged partial view of a drive pulley in engagement with a planetary gear.
  • FIG. 1 shows, by way of example, a circular-slip planetary gear mechanism according to the invention, which is shown in FIG. 2 in a longitudinal section along the line A-A from FIG.
  • the Kreisschiebeplanetenradgetriebe has two coaxial with a Zentraiwelie 1 successively arranged ring gears 2, 3 and a set Pianeten impart 4, which are mounted on a Pianetenrad terme 5, which in turn rotatably, here on the central shaft 1, is centrally supported.
  • the planet gears 4 are in engagement with the hollow wheels 2, 3 and at the same time by so-called drive pulleys 6, 7. 8 drivable. These are axially one behind the other via associated eccentric 9. 10, 11 arranged on the central shaft 1.
  • a first ring gear 2 which surrounds the Pianetencken 4 and the drive pulleys 6, 7, 8 radially outside, is rotatably or fixed to the housing, while the second ring gear 3 is rotatably mounted coaxially with the first arranged.
  • the Pianetencken comb 4 each at a first axial portion of its outer teeth with an inner toothing of the first ring gear 2 and at a second axial portion of its outer toothing with an internal toothing of the second Hohrad 3
  • the external toothing of the planetary gears 4 is here continuously made axially continuous.
  • the second ring gear 3 also serves as an output.
  • the drive pulleys 6, 7, 8 are designed to be identical to one another and serve to drive the planetary gears 4 They each have at their outer periphery a number of arcuate concave tooth teeth corresponding to the number of pianeta wheels 4. Segments 12 for engagement with a respective Pianetenrad 4 on. Each toothed segment 12 is associated with a Pianetenrad 4. Upon rotation of the center shaft 1, the drive pulleys 6, 7, 8 alternately engage with their toothed segments 12 on their toothed segments 12 in engagement with the associated planetary gears 4, thereby pushing them on their outer toothings by at least one tooth.
  • the Kreisschiebeplanetenradgetriebe consists of two gear stages
  • the drive pulleys 6. form the planet gears 4 and the first ring gear 2, 7 ; 8 the first gear stage.
  • Connected thereto is the second gear stage consisting of the planetary gears 4 in engagement with the second ring gear 3.
  • the second gear stage forms a so-called Piusgetriebe, in which the second Hohirad 3 and the Pianetenrad- carrier 5 rotate in the same direction
  • a first partial ratio i, based on the first gear stage is determined by the Zenzzahi z H1 of the internal gear of the first ring gear 2, the number of teeth z p of the teeth of the planet gears 4 and the number of teeth z ex of the toothed segments 12 to the drive pulleys 6, 7, 8th It applies
  • the Zahnzahi z E refers to the internal toothing of a virtually formed on the toothed segments 12 ring gear.
  • the first partial translation i? Predetermined number of teeth Z H1 of the first ring gear 2 by the difference between the number of teeth z ex of the toothed segments 12 and the number of teeth z p of the planetary gears 4 is determined.
  • a second Teiiuage i 2 relative to the second gear stage is determined by the number of teeth Z H1 of the internal gear of the first ring gear 1, the number of teeth Z P of the external teeth of the Pianetenzier 4 and the teeth Z H2 of the internal toothing of the second ring gear 3, this applies
  • the first partial ratio i 1 is preferably larger than the second partial ratio i 2 applies, wherein the number of teeth Z H1 of the first ring gear 2 is smaller than the number of teeth Z H2 of the second ring gear third
  • the Kreisschiebepianetenradgetriebe example three Planetenröder 4 and three axially successively arranged drive pulleys 6, 7. 8 with three associated eccentrics 9. 10, 11 on. It is also conceivable, depending on the torque to be transmitted and the number of planet gears 4 more or less drive pulleys 6, 7, 8 or eccentric 9. 10, 11 to order. For example, four planet wheels 4 may be provided, which are in engagement with at least two drive pulleys 6, 7, 8.
  • the axially outer eccentric 8, 10 are each designed as a separate component, while the center between the outer eccentrics 9, 11 arranged eccentric 10 is formed integrally with the central shaft 1.
  • the eccentrics 9, 10, 11 are arranged on the central shaft 1 in the circumferential direction by 120 ° angularly offset from each other. As a result, the drive pulleys move 6. 7, 8 corresponding to the angular offset of the eccentric 9, 10, 11 phase-shifted.
  • Central shaft 1 and eccentric 9, 10, 11 form a so-called eccentric shaft.
  • the planet carrier 5 is rotatably mounted on parallel side wall sections on the Zentraiwelle 1. Between the side wall portions, the three planet wheels 4 are mounted on three bolts, which are truncated at their ends on the side wall portions.
  • the sidewall sections each consist of three ben, the outside record at free end portions of the bolts and star-shaped converge centrally to form there a bearing eye for storage on the central shaft 1.
  • the struts each have a recess for mass or weight reduction.
  • the first ring gear 2 is mounted radially on the second ring gear 3.
  • the ring gears 2, 3 are arranged overlapping at their mutually facing axial end portions.
  • To accommodate the storage of the end portion of the first Hohirads 2 is upgraded at its inner diameter at a first annular shoulder, while at the end portion of the second Hohirads 3 a corresponding second annular shoulder is provided with retracted outer diameter.
  • Between the ring shoulders a Wälzfagerung axially and radially fitted.
  • the second ring gear 3 encloses a set wall section of the planet wheel carrier 11 radially outward.
  • the first ring gear 2 is bounded axially inwardly by the first ring shoulder.
  • Figure 3 shows the configuration of a drive pulley 6. 7, 8 which can be hung on a central circular receiving opening 13 on the eccentrics 9, 10, 11 of the central shaft 1.
  • the center of the receiving opening 13 at the same time forms the center of an imaginary circular line 14 which comprises the drive pulley on the outer circumference.
  • Three circular arc-shaped toothed segments 12 are provided as concave bulges on the outer circumference with an internal toothing for engagement with a respective planetary gear 4.
  • the toothed segments 12 are arranged offset on central axes 15 by 120 ° to each other.
  • the central axes 15 extend through the geometric centers of the circular arc-shaped toothed segments 12 and through the center of the drive pulley 6, 7, 8. They also form symmetry axes, to which the drive pulley 6, 7, 8 is formed axially symmetrical.
  • the internal teeth of the latter have a tooth offset by a predetermined angle ⁇ j to each other.
  • the internal teeth of the successive tooth segments 12 are dependent on the respective position j of the toothed ring 12, the number of teeth z H1 of the first ring gear 2, the number of teeth ⁇ Ex of the internal teeth of the toothed segments 12th of the number n of the pia on each drive pulley 6, 7 " - Netenzier 4 and depending on the first partial translation i, designed to offset the angle ö j , which is determined by
  • the toothed segments 12 are formed with a predetermined opening or wrap angle y. This determines the circular arc length of the toothed segments 12, at which the Pianetenzier 4 can roll off in engagement with the toothed segments 12.
  • the drive pulley 6, 7. 8 behaves at its toothed segments 12 each as a thought ring gear, which is indicated by a dashed circle.
  • the toothed segments 12 form in this way in each case a Sectionhohlrad or a portion of an imaginary ring gear.
  • FIG. 4 schematically shows an enlarged detail of a drive pulley 6, 7, 8 on a toothed segment 12 in engagement with a planetary gear 4.
  • the opening angle y determines the length and duration of the engagement of the planet gears 4 with the drive pulley 6, 7, 8 during the circulation. It is designed in such a way that the drive pulley 6, 7, 8 is in each case in engagement with a planet wheel 4 at each time of its circular sliding movement on at least two toothed segments 12. As a result, the drive pulley 6, 7, 8 is arranged at any time during its movement.
  • the opening angle ⁇ in dependence on the number of Pianetenvid to be driven 4, the length of the engagement line AC of inlet point A to pitch point C between the outer teeth of the Pianetencken 4 and the internal toothing of the tooth segments 12th die Kopf réelle,mes ser and the pitch circle diameter m of the internal teeth of the Zahnsegmen
  • the internal toothing of the toothed segments 12 is designed with an opening angle ⁇ of approximately 200 °.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Pulleys (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un engrenage planétaire à coulissement circulaire. Ledit engrenage comprend un arbre central (1), une première couronne (2) fixée au carter, un ensemble de satellites (4), un porte-satellites (5) en appui rotatif, sur lequel les satellites (4) sont montés, et plusieurs poulies d'entraînement (6, 7; 8) disposées axialement les unes derrière les autres et servant à entraîner les satellites (4), les poulies d'entraînement (6, 7, 8) étant montées de manière excentrique sur l'arbre central (1) pour mettre en œuvre un coulissement circulaire. L'invention est caractérisée en ce qu'au moins une deuxième couronne (3) est montée coaxialement de manière à pouvoir tourner autour de la première couronne (2) et les satellites (4) sont en prise respectivement sur une première partie axiale avec la première couronne (2) et sur une deuxième partie axiale avec la deuxième couronne (3).
PCT/DE2015/200230 2014-07-07 2015-03-31 Engrenage planétaire à coulissement circulaire Ceased WO2016004933A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014213151.0A DE102014213151B4 (de) 2014-07-07 2014-07-07 Kreisschiebeplanetenradgetriebe
DE102014213151.0 2014-07-07

Publications (1)

Publication Number Publication Date
WO2016004933A1 true WO2016004933A1 (fr) 2016-01-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2015/200230 Ceased WO2016004933A1 (fr) 2014-07-07 2015-03-31 Engrenage planétaire à coulissement circulaire

Country Status (2)

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DE (1) DE102014213151B4 (fr)
WO (1) WO2016004933A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061634A (zh) * 2016-02-08 2017-08-18 谐波传动系统有限公司 行星齿轮减速机
CN108240419A (zh) * 2016-12-27 2018-07-03 比亚迪股份有限公司 驱动轴锁止装置以及动力驱动系统和车辆

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105805239B (zh) * 2016-05-15 2018-03-06 王福成 行星滚子轴承
CN111637198B (zh) * 2020-05-22 2021-11-12 东华大学 一种分体式人字齿轮及其行星传动装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2527603A1 (de) * 1975-06-20 1976-12-23 Elpatag Ag Exzenter-differenzgetriebe mit abtrieb ueber auf einem abtriebselement verteilte mitnahmebolzen
DE19518160A1 (de) 1994-09-29 1996-04-04 Brosowitsch Josef Dipl Htl Ing Planetengetriebe
CN201925420U (zh) * 2010-11-30 2011-08-10 大连老虎金属制品有限公司 两级行星齿轮减速机

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT509468B1 (de) * 2010-05-07 2011-09-15 Karl Ronald Schoeller Planeten-differentialgetriebe mit excenter-getriebestufe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2527603A1 (de) * 1975-06-20 1976-12-23 Elpatag Ag Exzenter-differenzgetriebe mit abtrieb ueber auf einem abtriebselement verteilte mitnahmebolzen
DE19518160A1 (de) 1994-09-29 1996-04-04 Brosowitsch Josef Dipl Htl Ing Planetengetriebe
CN201925420U (zh) * 2010-11-30 2011-08-10 大连老虎金属制品有限公司 两级行星齿轮减速机

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061634A (zh) * 2016-02-08 2017-08-18 谐波传动系统有限公司 行星齿轮减速机
CN108240419A (zh) * 2016-12-27 2018-07-03 比亚迪股份有限公司 驱动轴锁止装置以及动力驱动系统和车辆
CN108240419B (zh) * 2016-12-27 2020-02-04 比亚迪股份有限公司 驱动轴锁止装置以及动力驱动系统和车辆

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Publication number Publication date
DE102014213151A1 (de) 2016-01-07
DE102014213151B4 (de) 2016-08-25

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