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WO2018188692A1 - Engrenage planétaire - Google Patents

Engrenage planétaire Download PDF

Info

Publication number
WO2018188692A1
WO2018188692A1 PCT/DE2018/100314 DE2018100314W WO2018188692A1 WO 2018188692 A1 WO2018188692 A1 WO 2018188692A1 DE 2018100314 W DE2018100314 W DE 2018100314W WO 2018188692 A1 WO2018188692 A1 WO 2018188692A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring gear
housing
gear
planetary gear
planetary
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/DE2018/100314
Other languages
German (de)
English (en)
Inventor
Hans-Walter Wodtke
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 WO2018188692A1 publication Critical patent/WO2018188692A1/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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • 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 gears
    • F16H1/2818—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet gears by allowing limited movement of the ring gear relative to the casing or shaft

Definitions

  • the invention relates to a planetary gear with a ring gear, which is mounted in a housing of the planetary gear.
  • Planetary gear are used in motor vehicles, for example, in automatic transmissions or axle differentials.
  • planetary gears are used as a summing gear to couple the electric motor and the internal combustion engine to a common output.
  • a planetary gear usually consists of a centrally mounted sun gear, a ring gear and a plurality of planet wheels that roll between the sun gear and ring gear. From this structure explains the term planetary gear, because the planetary gears orbiting the sun so astronomical sense, the planet a sun.
  • the advantage of the planetary gear results from the load distribution on several planetary gears. This makes it possible to transmit high torques in a compact design and to realize correspondingly large transmission ratios.
  • Planetary gear also have a high mechanical efficiency. In this case, planetary gears often have a high operating noise, which arises primarily by the rolling of the gears of the planetary gear and the engagement of the corresponding tooth flanks. While the airborne sound produced within the transmission does not penetrate to any appreciable extent, the vibrations of the gears and carriers are transmitted via the ring gear and a housing connected to the ring gear, which also makes the vibrations audible outside the planetary gear.
  • a planetary gear with a ring gear, a sun gear and a plurality of planetary gears is known, wherein the ring gear is rotatably mounted on vibration damping elements in the housing of the planet gear.
  • DE 10 2012 105 549 A1 a planetary gear with a sun gear, a plurality of planet gears and a ring gear is known, wherein the ring gear is rotatably mounted in a housing and wherein damping elements are provided to prevent striking of the ring gear on the housing of the planetary gear.
  • DE 1 204 076 discloses a planetary gear with two ring gears, two sun gears and a plurality of planet gears, wherein the sun gears and the ring gears are connected to each other via axial bolts to allow the most elastic connection of the gears to a drive train and compensate for misalignments and shocks.
  • a motor vehicle transmission in planetary construction in which a damping device is provided to reduce the vibrations between the ring gear and the output shaft in order to reduce the transmitted from the ring gear to the output shaft structure-borne noise and thus the sound emitted to the outside minimize the planetary gear.
  • a disadvantage of such a solution is that only insufficient axial forces can be transmitted by the solution proposed in DE 102 30 861 A1, this solution has an increased space requirement in the radial direction and requires a complex assembly of the planetary gear.
  • the solution of DE 102 30 861 A1 can not be transferred without significant modifications to a ring gear connected to the housing, since in this case the vibrations are transmitted to the housing and thus the transmission noises are carried to the outside.
  • the object of the invention is to improve the noise and the vibration behavior in a planetary gear with rotatably mounted ring gear and in particular to reduce the structure-borne sound transmission to the housing.
  • the object is achieved by a planetary gear with a sun gear, at least one planetary gear and a ring gear, wherein the ring gear rotatably disposed in a housing, wherein on the ring gear and / or on the housing at least one recess is provided, and wherein between the ring gear and the housing at least one decoupling element is arranged, which is received positively in the at least one recess.
  • the planetary gear according to the invention it is possible to significantly improve the vibration behavior and noise of the planetary gear and in particular to greatly reduce a transmission of structure-borne noise to the housing of the planetary gear.
  • the vibration behavior can be tuned by the replacement of the decoupling elements and adapted to the respective intended use.
  • the ring gear is centered by the decoupling elements.
  • the axial forces arising due to helical gears can be supported on the ring gear, so that this solution can be used both for straight-toothed ring gears and for helical gears.
  • the elastic compliance of the bearing can be adjusted via the cross-sectional shape, hardness and profile design of the decoupling elements.
  • a decoupling element is to be understood as meaning an element which, in addition to the energy dissipation, makes it possible to decouple the ring gear from the housing.
  • the decoupling element is designed as a corrugated spring.
  • a corrugated spring By a corrugated spring, a vibration decoupling between the ring gear and the housing of the planetary gear can be realized in a simple and cost-effective manner.
  • the corrugated springs can positively transmit torque and thus the ring gear is centered clearly in the housing, recesses are provided both on the ring gear and on the housing, which surround the crests of the corrugated springs partially.
  • the elastic resilience of the storage can preferably via the free Sections of the wave spring and the Wellfederquerites be adjusted. Compliance and damping can also be influenced by shaping the corrugations of the corrugated springs and the recesses in the housing.
  • the spring stiffness can be advantageously influenced by a layering of a plurality of corrugated springs to form a corrugated spring package.
  • the decoupling element is arranged on an axial end face of the ring gear.
  • the decoupling elements are arranged on the axial end faces of the ring gear.
  • the decoupling element is biased in the axial direction.
  • a corresponding bias of the decoupling elements it is possible to store the ring gear in the housing. This can prevent the decoupling elements from sliding out of the recesses of the ring gear and / or the housing and shifting undesirably.
  • the floating bearing of the ring gear leads to an elastic centering and thus to a better load distribution on the planetary gears, since the ring gear receives a limited displaceability, and thus load peaks can be intercepted. This increases the durability of the planetary gear.
  • a groove or a shoulder is provided, which reduces the width of the ring gear.
  • a shoulder or a corresponding groove in an axial end face of the ring gear it is possible to reduce the width of the ring gear in this area, so that additional space for the decoupling elements can be created.
  • an inventive planetary gear does not require more axial space than a planetary gear in which the ring gear is rigidly fixed in the housing of the planetary gear. Under certain circumstances, however, the space requirement in the radial direction may increase slightly, because the ring gear must be made with a greater material thickness and thus thicker to absorb the forces and moments.
  • the decoupling element is substantially incompressible.
  • the decoupling element is preferably made of a metallic material and does not allow any further compression except for an elastic deformation according to the E-modulus of the material.
  • the decoupling element preferably contains no gas spring, no elastomer or other components, which already at low forces have a significant change in volume in order to avoid striking the ring gear on the housing. Elastomers are less suitable because they deform non-linearly under load, have a settling behavior and are subject to noticeable aging.
  • a gas spring is not very suitable because there is a risk of leakage over the long service life of a planetary gear and they no Shear stresses can transmit, making it unsuitable to support the occurring at planetary gears high torques.
  • the aim of the decoupling elements is primarily a vibration isolation of the ring gear and not a damping in the sense of energy dissipation.
  • energy dissipation particularly by stratification of corrugated springs, can positively assist the desired effect of vibration isolation.
  • a gap is formed between a radial circumferential surface of the ring gear and the housing.
  • the decoupling element between a radial outer surface of the ring gear and the housing is arranged.
  • decoupling elements which are arranged on the axial end faces of the ring gear
  • the ring gear has a corresponding decoupling element on its radial lateral surface.
  • the ring gear is preferably decoupled in the axial direction by corresponding column of the housing, so that all forces and moments are passed through the decoupling element. Due to the axial forces and shear moments occurring, however, such a solution is generally less favorable than a damping over the axial end faces.
  • a plurality of uniformly distributed over the circumference of the ring gear decoupling elements are preferably provided which a Allow radial bias of the decoupling between the housing and the radial end face of the ring gear.
  • Figure 1 shows a detail of a planetary gear according to the invention, in which a vibration-damping decoupling element is arranged between the ring gear and the housing.
  • Fig. 2 is an enlarged detail of the radial end portion of the
  • Fig. 3 shows a detail of an alternative embodiment of a planetary gear according to the invention.
  • the planetary gear 1 shows a section through an inventive planetary gear.
  • the planetary gear 1 has a housing 5, in which a ring gear 4 is rotatably mounted.
  • the ring gear 4 has at a radially outer end portion on a web 25, which reduces the width B of the ring gear 4 respectively.
  • each one shown in Fig. 2 paragraph 14 is formed.
  • At the axial end faces 10, 1 1 of the ring gear 4 are on both sides decoupling elements 8, 9 arranged in the region of the web 25, with which the ring gear 4 is held in the housing 5.
  • the decoupling elements 8, 9 are biased by a clamping element 17 in the axial direction.
  • the bias of Decoupling elements 8, 9 can be adjusted via an interference fit of the decoupling elements 8, 9.
  • the bias voltage can be adjusted via a screw 18.
  • a gap 16 results between a radial circumferential surface 15 of the ring gear 4 and the housing 5, so that no vibrations are transmitted from the ring gear 4 to the housing 5 in this area.
  • the ring gear 4 is connected to a toothing 24 shown in FIG. 2 in engagement with at least one planetary gear 3, which is supported by a planet carrier 19.
  • a first housing opening 21 is provided to connect the planet carrier 19 with a drive or output shaft.
  • the planetary gear 3 is engaged with a sun gear 2 which is connected to a drive or output shaft 20.
  • the drive or output shaft 20 penetrates the housing 5 through a second housing opening 22, which is opposite to the first housing opening 21.
  • the ring gear 4, the sun gear 2 and the planet carrier 19 are arranged concentrically to a central axis 23 of the planetary gear 1.
  • the housing 5 may also be closed on the second end face and the drive shaft 20 on the same side of the housing as a hollow shaft connected to the planet carrier 19 exit from the housing 5.
  • a radial portion of the ring gear 4 is shown.
  • the ring gear 4 has in the region of the web 25 two opposite recesses 6, in which the decoupling elements 8, 9, which are preferably designed as corrugated springs 12, are positively received.
  • a further recess 7 is in each case formed on the housing 5 shown in FIG. 1 and on the clamping element 17 in order to receive the respective decoupling element 8, 9 in a form-fitting manner.
  • the decoupling elements 8, 9 are preferably not in the radial direction.
  • the centering of the ring gear 4 is preferably carried out exclusively by tangential positive locking.
  • FIG. 3 shows an alternative embodiment of a planetary gear 1 according to the invention.
  • the ring gear 4 in this embodiment no web 25 and two paragraphs 14, but at the two axial end faces 10, 1 1 each have a groove 13 in which the respective decoupling element 8, 9 is recorded.
  • the groove 13 is only so deep that the decoupling element 8, 9 projects beyond the respective axial end face 10, 1 1 of the ring gear 4 even at maximum deformation.
  • additional recesses 6 are formed to receive the decoupling elements 8, 9 positively.
  • Recesses 7 are also provided on the housing 5 and on the tensioning element 17 in order to receive the decoupling element 8, 9 in a form-fitting manner and thus to enable transmission of tangential forces.

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

Abstract

L'invention concerne un engrenage planétaire (1) comportant un pignon planétaire (2), au moins un pignon satellite (3) et une couronne (4). La couronne (4) est agencée bloquée en rotation dans un carter (5), un évidement (6, 7) est pratiqué au niveau de la couronne (4) et/ou du carter (5), et entre la couronne (4) et le carter (5) est agencé au moins un élément de désaccouplement (8, 9) qui est logé dans l'évidement (6, 7) par complémentarité de forme.
PCT/DE2018/100314 2017-04-12 2018-04-09 Engrenage planétaire Ceased WO2018188692A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017107929.7 2017-04-12
DE102017107929.7A DE102017107929B4 (de) 2017-04-12 2017-04-12 Planetengetriebe

Publications (1)

Publication Number Publication Date
WO2018188692A1 true WO2018188692A1 (fr) 2018-10-18

Family

ID=62104059

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2018/100314 Ceased WO2018188692A1 (fr) 2017-04-12 2018-04-09 Engrenage planétaire

Country Status (2)

Country Link
DE (1) DE102017107929B4 (fr)
WO (1) WO2018188692A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019018596A1 (fr) 2017-07-21 2019-01-24 General Electric Company Ensemble train de transmission pour éolienne
WO2021160373A1 (fr) * 2020-02-12 2021-08-19 Zf Friedrichshafen Ag Dispositif doté d'une chemise de cylindre découplée
WO2022167155A1 (fr) * 2021-02-08 2022-08-11 Fm Energie Gmbh & Co.Kg Boîte de vitesses à train planétaire insonorisée et éolienne comprenant une telle boîte de vitesses
EP4257848A1 (fr) * 2022-04-04 2023-10-11 Ovalo GmbH Système de transmission

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018127942A1 (de) * 2018-11-08 2020-05-14 Schaeffler Technologies AG & Co. KG Planetengetriebe
DE102019218535A1 (de) * 2019-11-29 2021-06-02 Zf Friedrichshafen Ag Planetengetriebeanordnung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1204076B (de) 1962-12-11 1965-10-28 Kurt Eisfeld Dipl Ing Schleppkoerper mit Einrichtungen zur Messung und Anzeige der Schussablage bei Schiessuebungen auf Luftschleppziele
CH424410A (de) 1962-04-11 1966-11-15 Demag Ag Umlaufrädergetriebe mit Schrägverzahnung
DE69700196T2 (de) * 1996-02-16 1999-12-16 Denso Corp., Kariya Anlasser mit Planetuntersetzungsgetriebe
DE10230861A1 (de) 2002-07-09 2004-01-22 Zf Friedrichshafen Ag Kraftfahrzeuggetriebe
US20060130600A1 (en) * 2004-12-16 2006-06-22 Denso Corporation Structure of engine starter equipped with planetary gear speed reducer
WO2013021181A1 (fr) * 2011-08-05 2013-02-14 David Brown Gear Systems Limited Agencement de commande pour éolienne
DE102012105549A1 (de) 2012-06-26 2014-03-20 Zf Lenksysteme Gmbh Planetengetriebe hohlradaufhängung

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1191648B (de) * 1958-01-31 1965-04-22 Renk Ag Zahnraeder Planetenradgetriebe mit doppelschraegverzahnten Umlaufraedern
DE1135256B (de) * 1960-01-13 1962-08-23 Leipzig Getriebewerke Planetengetriebe mit Selbsteinstellung der Zentralraeder
DE1203076B (de) * 1962-05-16 1965-10-14 Demag Ag Planetengetriebe mit in der Radialebene geteilten Raedern
SE7512492L (sv) * 1975-11-07 1977-05-08 Stal Laval Turbin Ab Anordning for momentoverforing i epicyklisk vexel
DE102011075916A1 (de) * 2011-05-16 2012-11-22 Zf Friedrichshafen Ag Lastausgleichendes Hohlrad
DE102014202494B4 (de) * 2013-12-20 2022-12-22 Zf Friedrichshafen Ag Planetengetriebe mit einstellbeweglichem Hohlrad

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH424410A (de) 1962-04-11 1966-11-15 Demag Ag Umlaufrädergetriebe mit Schrägverzahnung
DE1204076B (de) 1962-12-11 1965-10-28 Kurt Eisfeld Dipl Ing Schleppkoerper mit Einrichtungen zur Messung und Anzeige der Schussablage bei Schiessuebungen auf Luftschleppziele
DE69700196T2 (de) * 1996-02-16 1999-12-16 Denso Corp., Kariya Anlasser mit Planetuntersetzungsgetriebe
DE10230861A1 (de) 2002-07-09 2004-01-22 Zf Friedrichshafen Ag Kraftfahrzeuggetriebe
US20060130600A1 (en) * 2004-12-16 2006-06-22 Denso Corporation Structure of engine starter equipped with planetary gear speed reducer
WO2013021181A1 (fr) * 2011-08-05 2013-02-14 David Brown Gear Systems Limited Agencement de commande pour éolienne
DE102012105549A1 (de) 2012-06-26 2014-03-20 Zf Lenksysteme Gmbh Planetengetriebe hohlradaufhängung

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019018596A1 (fr) 2017-07-21 2019-01-24 General Electric Company Ensemble train de transmission pour éolienne
EP3655647A4 (fr) * 2017-07-21 2021-03-31 General Electric Company Ensemble train de transmission pour éolienne
WO2021160373A1 (fr) * 2020-02-12 2021-08-19 Zf Friedrichshafen Ag Dispositif doté d'une chemise de cylindre découplée
WO2022167155A1 (fr) * 2021-02-08 2022-08-11 Fm Energie Gmbh & Co.Kg Boîte de vitesses à train planétaire insonorisée et éolienne comprenant une telle boîte de vitesses
EP4288681A1 (fr) * 2021-02-08 2023-12-13 FM Energie GmbH & Co. KG Boîte de vitesses à train planétaire insonorisée et éolienne comprenant une telle boîte de vitesses
EP4257848A1 (fr) * 2022-04-04 2023-10-11 Ovalo GmbH Système de transmission

Also Published As

Publication number Publication date
DE102017107929B4 (de) 2021-06-24
DE102017107929A1 (de) 2018-10-18

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