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
  • F16H48/00—Differential gearings
  • F16H48/06—Differential gearings with gears having orbital motion
  • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
  • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
  • F16H1/2863—Arrangements for adjusting or for taking-up backlash
• • 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

Definitions

• the invention relates to a planetary stage according to the preamble of claim 1.
• DE 102015009070 A1 recommends a special arrangement of planet gears.
• the planet gears are irregularly spaced from each other in the circumferential direction of the rotation axis of a sun gear. This has the consequence that the teeth of the planetary gears at different times of the single intervention to double engagement and so reduce the noise emissions.
• the invention has for its object to eliminate the inherent disadvantages of the prior art solutions disadvantages.
• the noise emissions of a planetary stage are to be lowered without impairing their durability and performance.
• a planetary stage is defined as an associated with a transmission arrangement with a sun gear, a planet carrier, one or more planetary gears and a ring gear.
• the planet gears are each one relative to the planet carrier fixed axis of rotation mounted on the planet carrier. They mesh respectively with the sun gear and / or the ring gear.
• Two of the three components sun gear, planet carrier and ring gear are rotatably mounted about a common central axis.
• the third component is rotationally fixed, preferably stationary, arranged.
• the planetary stage according to the invention comprises, in addition to a ring gear and a sun gear, a first planetary gear and a second planetary gear.
• the first planetary gear and the second planetary gear mesh respectively with the ring gear and with the sun gear.
• a tip diameter of the first planet gear is greater than a tip circle diameter of the second planet gear.
• the tip diameter of the first planetary gear may be at least 0.2 percent greater than the tip diameter of the second planetary gear.
• the tip diameter of the first planetary gear is at least 0.4 percent greater than the tip circle diameter of the second planetary gear.
• the tip diameter defines a boundary of the flanks of the teeth of the first planetary gear and the second planetary gear to the outside. Due to the outer boundary of the tooth flanks, the engagement paths of the tooth engagements of the first planetary gear and the sun gear, the first planet gear and the ring gear, the second planet gear and the sun gear and the second planet gear and the ring gear are set in length.
• the engagement distances of the first planetary gear are longer than the corresponding engagement distances of the second planetary gear. This results in different profile overlaps.
• the profile coverage affects the ratio of single intervention to double intervention.
• the invention thus achieves that the ratios of individual engagement to double engagement differ in the first planetary gear and the corresponding ratios of single engagement to double engagement in the second planetary gear. This has the consequence that the temporal correlation of the engagement shocks of the first planetary gear and the second planetary gear is widened. This reduces tonalities, ie individual peaks in the frequency spectrum of the noise emissions of a transmission. The resulting frequency spectrum corresponds to noise.
• the planetary stage according to the invention is particularly suitable for use in a wind turbine gearbox.
• the planetary stage according to the invention is suitable as a second planetary stage of the initially described, known from the prior art, three-stage wind turbine gearbox.
• the other toothing parameters of the toothings of the first planetary gear and of the second planetary gear preferably coincide.
• the first planetary gear and the second planetary gear are involute gearwheels whose base circle diameters coincide.
• the numbers of teeth, the pitch circle diameter and / or the profile displacements or profile displacement factors of the first planetary gear and the second planetary gear coincide.
• the modules of the first planetary gear and the second planetary gear preferably match.
• Further parameters of the first planetary gear and the second planetary gear, which preferably coincide, are their Wälz Vietnamese bemesser, supplement Vietnamese bemesser, tooth thicknesses on the pitch circle, pitches on the pitch circle, tooth widths, gap widths on the pitch circle, pitches on the pitch circle.
• the head heights of the teeth of the first planetary gear and the second planetary gear differ from each other due to the different tip diameter.
• first planetary gear and the second planetary gear are cylindrical wheels. This means that the totality of all head circles, base circles and pitch circles forms one cylinder each.
• the first planetary gear and the second planetary gear may be straight or obliquely toothed.
• the sun gear and a planet carrier of the planetary stage, the sun gear and the ring gear or the planet carrier and the ring gear are preferably further rotatably formed about a common axis of rotation, called central axis.
• a first, relative to the planet carrier fixed axis of rotation about which the first planetary gear is rotatably mounted on the planet carrier, and a second, fixed relative to the planet carrier rotation axis about which the second planet gear is rotatably mounted on the planet carrier are in one beyond preferred development arranged equidistant from the central axis.
• the first axis of rotation, the second axis of rotation and the central axis preferably run parallel to one another.
• the planetary stage may have more than two planet gears.
• it can be developed with a third planetary gear, which meshes with the ring gear and the sun gear.
• the head circle diameter of the third planetary gear is smaller than the tip circle diameter of the second planetary gear and thus smaller than the tip circle diameter of the first planetary gear and.
• the remaining gear parameters of the third planetary gear preferably coincide with the gear parameters of the first planetary gear and the second planetary gear. This applies in particular to the gear parameters listed above, in which the toothings of the first planetary gear and of the second planetary gear coincide.
• FIG. 1 A preferred embodiment of the invention is shown in FIG. 1 in detail shows:
• Fig. 1 is a planetary stage.
• the planetary stage 101 shown in FIG. 1 has a ring gear 103, a first planetary gear 105, a second planetary gear 107, a third planetary gear 109 and a sun gear 111.
• the first planetary gear 105, the second planetary gear 107 and the third planetary gear 109 mesh with the ring gear 103 and the sun gear 111, respectively.
• a tip diameter (d ai ) of the first planetary gear 105, a tip circle diameter ⁇ d a2 ) of the second pinion 107, and a tip diameter (d a3 ) of the third pinion 109 For a tip diameter (d ai ) of the first planetary gear 105, a tip circle diameter ⁇ d a2 ) of the second pinion 107, and a tip diameter (d a3 ) of the third pinion 109,

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Retarders (AREA)
• Wind Motors (AREA)
• General Details Of Gearings (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=61168070

Family Applications (1)

Country Status (5)

Families Citing this family (1)

Family Cites Families (7)

• 2017
  • 2017-02-28 DE DE102017203214.6A patent/DE102017203214A1/de not_active Withdrawn
• 2018
  • 2018-01-29 WO PCT/EP2018/052062 patent/WO2018158017A1/de unknown
  • 2018-01-29 EP EP18703529.0A patent/EP3589865A1/de not_active Withdrawn
  • 2018-01-29 JP JP2019546904A patent/JP2020518770A/ja active Pending
  • 2018-01-29 CN CN201880004554.5A patent/CN110998149A/zh active Pending

Also Published As

Similar Documents

Legal Events