WO2016026899A1 - Mécanisme de réglage - Google Patents

Mécanisme de réglage Download PDF

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Publication number
WO2016026899A1
WO2016026899A1 PCT/EP2015/069060 EP2015069060W WO2016026899A1 WO 2016026899 A1 WO2016026899 A1 WO 2016026899A1 EP 2015069060 W EP2015069060 W EP 2015069060W WO 2016026899 A1 WO2016026899 A1 WO 2016026899A1
Authority
WO
WIPO (PCT)
Prior art keywords
planet
gear
ring
adjusting mechanism
support ring
Prior art date
Application number
PCT/EP2015/069060
Other languages
German (de)
English (en)
Inventor
Michael Schober
Original Assignee
Magna powertrain gmbh & 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 Magna powertrain gmbh & co kg filed Critical Magna powertrain gmbh & co kg
Publication of WO2016026899A1 publication Critical patent/WO2016026899A1/fr

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
    • F16H1/46—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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/02004—Gearboxes; Mounting gearing therein the gears being positioned relative to one another by rolling members or by specially adapted surfaces on the gears, e.g. by a rolling surface with the diameter of the pitch circle
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the invention relates to an adjusting gear with an electric motor and a Wolfrom type planetary gear.
  • variable-speed gearboxes on the one hand, there are very high requirements in terms of compactness in relation to the torque capacity, and, on the other hand, the adjusting gear must also be designed as inexpensively as possible.
  • the compactness is achieved in the prior art from the combination of a small, high-revving, electric motor with a high-reduction gear.
  • the challenge is to present this high-reduction gearbox structurally compact as well as cost-effectively.
  • a Wolfromgetriebe is used, a type of transmission which can be very compact and represent high reduction.
  • Such a transmission is a planetary gear, which pairs at least two rotatably mounted on a common planet carrier Planetenrad- and two mutually substantially coaxially arranged ring gears, namely a housing-fixed support wheel and a driven shaft connected to a driven gear, wherein the numbers of teeth of the two ring gears to a predetermined integer ( ⁇ ) differ, and wherein one of the planetary gears of each pair of planetary gears meshes with the support wheel, while the respective other planetary gear of this pair of planetary gears meshes with the output gear.
  • ⁇ predetermined integer
  • the solution is that the Wolfromgetriebe with respect to the meshing on the one hand longitudinally symmetrical, or at least approximately longitudinally symmetrical to prevent tilting of the double planet from the outset.
  • the double planet only Abdrnature guide, so-called radial meshing forces that push the double planet from the meshing in the two ring gears in the direction of the center of the Wolfromgetriebes.
  • These Abdrfit be included in a conventional Wolfromgetriebe, as well as the Verkippungs concept, by the bearings of the double planet on the planet carrier.
  • the solution according to the invention is to absorb the pure forces of deflection by means of one or more simple support rings whose axis coincides with that of the Wolfrom gear, the support rings rolling on a cylindrical shoulder on the double planet.
  • the complex planet carrier is replaced by one or more simple support rings.
  • the object is achieved in particular by an adjusting gear with an electric motor and a planetary gear of the Wolfrom type, wherein the planetary gear has at least one support ring as a support for planets as a replacement for a planet carrier.
  • the radial deflection forces of the double planets in a longitudinally symmetrical Wolfrom transmission are advantageously accommodated by support rings which roll on a shoulder of the double planet.
  • the solution leads to a cost reduction, as well as a noise reduction by eliminating multiple bearings, as they would otherwise be provided in the planet carrier.
  • FIG. 1 shows a schematic representation of the exemplary embodiment in FIG.
  • Fig. 2 shows a cross section through the planet according to the invention.
  • FIGS 3a, 3b and 3c show different embodiments.
  • FIG. 1 shows a longitudinal section of a Versteilantriebs 1 is shown.
  • the adjusting drive is seated in a housing 2 which is fastened via flanges 3 at an installation location.
  • Such an adjustment drive is used, for example, for adjusting the compression of an internal combustion engine, in which the control of a Pleulaniser serves to adjust the compression of the engine.
  • An electric motor 5 with its rotor 6 drives the adjustment drive and is structurally connected via a screw 1 6 directly to the transmission and the sun gear 8.
  • the sun gear rotates about the center axis, which is shown in dashed lines.
  • Prerequisite for the realization of the invention is a longitudinally symmetrical design of the Wolfromgetriebes, which requires at least one additional ring gear.
  • the ring gears 9,10,11 are arranged along the longitudinal axis, wherein the ring gears 9 and 1 1 sit symmetrically about the central ring gear 10 in the housing.
  • the middle ring gear 10 is connected to the output 4.
  • the ring gear 1 1 is held in the housing and is supported in the direction of the flange 3.
  • the ring gear 9 must be supported centrally towards the rotor and enters the force in the direction of the screw, or the housing wall, which extends along the longitudinal axis.
  • the bearings and housing connections as well as the materials of the two outer ring gears must be of similar rigidity. This is not easy to realize insofar as the ring gear 1 1 has a thick and rigid housing and flange connection and the ring gear 9 is connected to the housing over a very long distance.
  • the connection of the ring gear 10 with the housing 2 and a flange of the gear attachment takes place axially, ie within the sun gear.
  • step plans 30 are arranged, which are mounted on bolts 7.
  • a stepped planet 30 in the example consists of a planet 9, a central planet 10 and a planet 1 1.
  • the bolt 7 each defines a stepped planet 30, both ends of the bolt forming cylindrical shoulders 17 on which support rings 15 roll.
  • Planet 9 and Planet 1 1 are identical or nearly identical in terms of tooth geometry.
  • the relievenplanet 30 interacts with the ring gear 9 and ring gear 1 1, which are identical or nearly identical with respect to the tooth geometry.
  • Figure 2 shows a plan view of the Wolfrom transmission.
  • the stepped planet 30 has a roll-off point 20 or first rolling point between the cylindrical shoulder 17 on the double planet, eg at the bolt end, and the support ring 15. The rolling contact results in very little friction, which benefits the efficiency of this transmission.
  • the roll-off point 21, the second rolling point, between the cylindrical shoulder 17 on the double planet 30 and the support ring 15 is also a rolling contact. This also creates very little friction.
  • the support ring 15 is preferably guided only over the cylindrical paragraphs 17 of the double planet 30 and is thus placed floating.
  • a second support ring 15 is integrated as one embodiment. This encompasses the cylindrical heels on the double planet 30 from the outside.
  • This embodiment is also shown again in Figure 3b, in which case the inner support rings are omitted in a further alternative embodiment.
  • the use of two support rings 15 inside and outside can be advantageous at high speeds and low torque load on the transmission, since the double planet 30 would be pressed into the teeth of the ring gears by the centrifugal force, which would lead to high friction and wear on the tooth flanks.
  • This outer support ring 15 could also be deliberately elastic according to eg thin wall thickness, so that it, with a corresponding reduced diameter, in the installed state, a biasing force in the roll-off points 20 and 21 causes. This also has a very beneficial effect on the noise behavior of this transmission.
  • the radial tooth engagement forces 23 are shown, which act on the double planetary gear 30 in engagement with the sun gear 8 and the resulting radial force from all tooth engagements of a double planet with the sun gear len represent.
  • This radial tooth engagement force 23 is much smaller than the radial tooth engagement forces 22.
  • the differences of these radial engagement forces are respectively received by the support ring 15 or the support rings 15. This prevents that it comes to a terminal namely to a two-sided concern of the tooth flanks in meshing engagement between the planet 30 and the sun gear 8.
  • an optimal balance of forces in the support ring is established, so that the best possible uniform distribution of the tooth forces in the different double planets is established.
  • the toothing of the sun gear 8 optionally engages only in the toothing of the central planetary gear 13, or in that of a planetary gear 12, or 13, or in both planet gears 12 and 13th
  • the at least one support ring 15 prevents the planet 30, are pressed by the high radial Abdrnature concept that occur in the meshing of the planetary gears with the ring gears, with their teeth in the teeth of the sun gear 8 bringing it to a terminals, a two-sided concerns the tooth flanks Bias, would come in this meshing. This would result in a dramatic decline in efficiency and high wear of these gears.
  • the dual planet 30 degenerates to a broad planet.
  • the teeth of Planet 13 and Planet 12 or 14 have the same number of teeth and tooth module, or / and have an identical tooth form and are not twisted together. This must also the ring gears 9 and 1 1, and ring gear
  • the ring gears 9 and 1 1 have in this case compared to the ring gear 10, a small number of teeth, for example, 2, 3 or 4. A proper meshing of these ring gears in the planet 30 is then achieved by profile displacement.
  • the connection of the two outer ring gears 9 and 1 1 is, as shown in Figure 1, in the transmission longitudinal region along the transmission axis of the Wolfromgetriebes, which corresponds to the axis of the sun gear and the ring gears on which take place the meshing, in the near-axis region by a kind Realized "wave" which is located within the inner diameter of the sun gear.
  • the electric motor 5 is housed together with the rotor 6 of this engine.
  • the support ring 15, or one or more further support rings 15 can be made elastic and slightly larger, so that the double planet 30 in the installed state radially outwardly pressed against the teeth of the ring gears 9,10,1 1 and thus biased.
  • This bias has significantly more favorable influence on a backlash of the transmission and also has significantly less negative impact on the efficiency.
  • This is at least a bias between the ring gear 10 and planetary gear 13 or ring gear 9 and ring gear 1 1 with the planetary gears 12, and 14 realized. This leads to a great advantage in noise behavior, especially in transmissions loaded with alternating torque.
  • the rotational stiffness between the ring gears 9 and 1 1 towards the housing flange can be deliberately designed differently, so that at high torque load in a preferred direction, the double planet optimally have no skewing and thus there is an optimal edge contact.
  • the torsional stiffness of the stiffness between the ring gears 9 and 1 1 towards the housing flange may consciously have a "kink” or a progressive or degressive behavior by additional measures or special materials, so that at high load, the planet 30 undergoes no skewing and the Doppelplanet at torque-free state of the transmission obliquely, so here sets a small bias in the meshing, which significantly improves the noise performance.
  • an additional support ring 15 may be used, which may be either rigid or designed to be elastic and with bias on the outside of the cylindrical shoulder 17 presses on the double planet 30.
  • a rigid support ring 15 With a rigid support ring 15, a double flank concerns between planetary and Hohlradvertechnikungen can be prevented or can be achieved with a resilient biased support ring 15 a tension in the roll-off points 20 and 21 which should benefit the noise behavior.
  • the meshing can also be clamped in a variety of ways, with conventional split gears are used.
  • the outer diameter of the support ring 15 is identical to the pitch circle diameter of the sun gear 8.
  • the diameter of the cylindrical shoulder 17 on the stepped planetary 30 is also identical to the pitch circle diameter of the planet gear, which is in engagement with the sun gear 8.
  • the support ring 15 can also be made in one piece with the sun gear 8.
  • FIG. 3c an alternative for the support ring 15 is shown. Only one support ring 15 is placed symmetrically to the tooth engagement, in which case the central plane 10 is divided.

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

Abstract

L'invention concerne un mécanisme de réglage comprenant un moteur électrique et un train épicycloïdal du type Wolfrom, ce train épicycloïdal ayant au moins une bague d'appui comme support de satellites en remplacement d'un porte-satellites.
PCT/EP2015/069060 2014-08-20 2015-08-19 Mécanisme de réglage WO2016026899A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102014216559 2014-08-20
DE102014216559.8 2014-08-20
DE102015202650.7A DE102015202650A1 (de) 2014-08-20 2015-02-13 Verstellgetriebe
DE102015202650.7 2015-02-13

Publications (1)

Publication Number Publication Date
WO2016026899A1 true WO2016026899A1 (fr) 2016-02-25

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ID=55274091

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/069060 WO2016026899A1 (fr) 2014-08-20 2015-08-19 Mécanisme de réglage

Country Status (2)

Country Link
DE (1) DE102015202650A1 (fr)
WO (1) WO2016026899A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017217235B4 (de) * 2017-09-27 2023-08-03 Deutsches Zentrum für Luft- und Raumfahrt e.V. Wolfromgetriebe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981000899A1 (fr) * 1979-09-04 1981-04-02 J Eichorst Systeme d'engrenage planetaire flottant
DE102010012879A1 (de) * 2010-03-26 2011-09-29 Maxon Motor Ag Planetengetriebe in Wolfromanordnung sowie Elektromotor mit integriertem Planetengetriebe in Wolfromanordnung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981000899A1 (fr) * 1979-09-04 1981-04-02 J Eichorst Systeme d'engrenage planetaire flottant
DE102010012879A1 (de) * 2010-03-26 2011-09-29 Maxon Motor Ag Planetengetriebe in Wolfromanordnung sowie Elektromotor mit integriertem Planetengetriebe in Wolfromanordnung

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DE102015202650A1 (de) 2016-02-25

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