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

Definitions

• the invention relates to built-in planetary drive assembled of joined planetary gearings aligned one behind the other, with gears with differential mechanism that are joined to the motor shaft, said planetary gearings being solved as gearings built into limited spaces of drums, hubs, electro-drums etc. of various machinery equipments.
• the satellite carrier or the ring gear of the first planetary gearing is joined to the sun gear of the next planetary gearing.
• the sun gear of the first planetary gearing with the driving shaft, fitted with the gear coupling, is led by satellites and the sun gears of the following planetary gearings are freely seated and ring gear of last planetary gearing is led by means of coupling teeth. In this way the differential mechanisms are formed for uniform distribution of the supplied power to individual satellites.
• the sun gear with the driving shaft of the first planetary gearing is placed in the contracted section of the hollow body constructing the basic immobile supporting frame of the planetary drive with the built-in motor.
• the gearbox with overhung larger gears of double satellites and with reached one gear reduction at least is joined to the body face.
• the double satellites pinion gears and the ring gear of the last gear reduction are built into the space between the outer circumference of the contracted section of the body and the inside diameter of the ' sleeve hub which is driven by coupling teeth of the ring gear.
• Satellite pins are located by means of satellite bearings in bearing bores of the joining flange face into which the body is extended and in bearing bores of the radially shaped body which are provided ith closing clips of the satellite bearings.
• the hub sleeve is strongly joined to the hub which is located by means of the hub bearings on the outer body circumference.
• the first planetary gearing with simple satellites is placed into the contracted section of the hollow body between the second and third gear reductions of the last planetary gearing or behind the last gear reduction which is nearer to the motor.
• the Fig. 2 presents the kinematical scheme of the assembly of the Fig. 1 where the "replace- ment of mechanism" is applied.
• FIG. 4 the kinematical realization with three planetary gearings i.e. with four gear reductions is presented.
• the Fig. 5 presents the project scheme fro the Fig. 1 where the first planetary gearing is placed into the contracted section of the hollow body.
• the second planetary gearing 3 is formed by two gear reductions 6, 7 with double satellites 37, 38, 39, i.e. in epicycloid and hypocycloid realization of gears which is briefly named as epi- hypo.
• This means that the gear reduction 6 is realized in permanent meshing of the sun gear 30 and the larger of the gears of the double satellites 37, 38 , 39 with external teeth and in the gear reduction 7 there is the pinion gear 42 with smaller external teeth of the double satellites 37, 38, 39 in permanent mesh with the ring gear 34 having internal teeth.
• the first planetary gearing I is realized with the rotating satellite carrier 21 and with the fixed ring gear 20, the second planetary gearing 3 is realized as the pseudoplanetary one with fixed satellite carrier 35 and the rotating ring gear 34.
• the first planetary gearing 1 is formed by the sun gear 16 with the longer, torsional elastic driving shaft 9 located at the side of the motor 14 in the gear coupling 10 passing over the hollow body ⁇ where the sun gear 16 is in permanent mesh with simple satellites 17, 18, 19 and these ones with the ring gear 20.
• the satellites 17, 18, 19 can be used only in the number of three as based on theoretical analysis of force conditions.
• the differential mechanism 43, 44, 45 serves to achieve uniform distribution and dividing of transmitted power to the individual satellites 17, 18 . , 19 and 37, 38, 39 of the planetary gearings I and 3.
• the satellite carrier 21 of the first gear reduction 4 is joined to the sun gear 30 freely seated among the satellites 37, 38, 39 of the second planetary gearing 3.
• the hollow body H forms the basic immobile supporting frame for the whole built-in planetary drive with the built-in motor 14 and said hollow body is shaped to the contracted section 12 which is extended in the joining flange 13.. At the front face of this body H and its joining flange 13 the gear box 8 is joined.
• the overhung location is placed of the greater gears of the double satellites 37, 38, 39 located on the satellite pins 36, on pinion gears 42 if need be, in the satellite bearings 49 of the planetary gearing 3, i.e. in the bearing bores 51 of the front joining flange 13 and in the bearing bores 52 of the radially formed body H, said bores being fitted with closing clips 53 of the satellite bearings 50.
• the planetary gearing 1 is placed which is joined, by means of the satellite carrier 21, to the freely located sun gear 30 of the second planetary gearing 3 and here the sun gear 30 is in permanent meshing with three satellites 37, 38, 39.
• gear box 8 is formed of the disk flange 46 to which the cylindrical detail 63 is screwed which is closed by the shaped face 64.
• This gear box 8 is covered as the whole by the cover 65 of the lubricating space .
• the pinion gears 42 with smaller gears of the double satellites 37, 38, 39 with the meshing gear 34 of the last gear reduction 7 are built into the space between the outer circumference of the contracted section 12 of the body H and the inside diameter of the sleeve hub 48.
• this hub sleeve 48 is driven together with the strongly joined hub 54 which is located at the outer circumference of the body H by means of the hub bearings 55 and 56.
• the planetary drive formed in this way built into the drum space of the hub 54, can be solved in other variants as will be seen partially on other figures.
• the Fig. 2 displays the kinematical scheme of the conception given in the Fig. 1.
• the difference of the conception of the Fig. 1 is based on that for the new form of the built-in planetary drive the so called "replacement of mechanism" in the first planetary gearing 1 has been used.
• the satellite carrier 21 has been transformed into the immobile member which became the fixed member now, at the rotating sun gear 16, the rotating member is the ring gear 20 now.
• the ring gear 20 of the first gear reduction is joined to the free sun gear 30 of the second planetary gearing 3 with double satellites 37, 38, 39 of the gear reductions 6, 7.
• FIG. 3 the kinematical scheme of the connection of two second planetary gearings 1, 3 to the double satellites 31, 32, 33 and 37, 38, 39 is shown which form four gear reductions 4, 5, 6, 7.
• the first planetary gearing 1 consists of the sun gear 16 and the ring gear 27 which are in permanent mesh with the satellites 31, 32, 33 leading the sun gear 16 joined to the driving shaft 9.
• the satellite carrier 21 is joined to the freed sun gear 30 of the second planetary gearing 3.
• the ring gear 34 of the last gear reduction 7 is led and coupled to the hub sleeve 48 by means of the coupling teeth 47.
• the satellite pins 29 and 36 can be made together with gears of smaller diameters of double satellites 31, 32, 33 and 37, 38, 39 of one piece of material as the pinion gears 40 and 42.
• the supporting hollow body H and further details can be formed.
• three gear reductions 4, 5, 6 are built which occupy some greater width.
• first and second planetary gearings 1 2 simple satellites 17, 18, 19 and 24, 25, 26 are used and in the third planetary gearing 3 of the double satellites 37, 38, 39 are applied in epi- hypo realization as well.
• the assembly of the first planetary gearing 1 with rotating sun gear 16 and the satellite carrier 21 at the fixed ring gear 20 is identical with the Fig. 1.
• the first planetary gearing 1 is joined by the satellite carrier 21 to the free sun gear 23 of the second planetary gearing 2 at fixed satellite carrier 28.
• the pseudoplanetary gearing 2 has been originated the rotating ring gear 27 of which is joined to the freed sun gear 30 of the third planetary gearing 3.
• the pseudoplanetary realization of the planetary gearing 3 is applied at satellite carrier 35 being fixed.
• the ring gear 34 of the last gear redution 7 is led by means of the coupling teeth 47 and coupled with the hub sleeve 48.
• the differential mechanism 43, 44, 45 is formed for uniform power distribution to individual satellites 17, UL 19, 24, 25, 26 and 37, 38, 39 in all gear reductions 4, 5, 6, 7.
• the Fig. 5 presents the project scheme resulting from the Fig. 1.
• the first planetary gearing 1 with simple satellites 17, 18, 19 is placed in the contracted section 12 of the hollow body H between the second and the third gear reductions 6, 7 of the last planetary gearing 3 wit double satellites 37, 38, 39.
• the first planetary gearing 3 remains the first aligned gear reduction 4 on the driving shaft 9 of the motor 14.
• the built-in planetary drives assembled of planetary gearings aligned one behind the other with gears and differential mechanism can be used as gearings built in spaces of drums, hubs etc. with limited dimensions for engineering devices, e.g. electro-drums with requested higher gear ratio.
• the invention can be exploited in the branch with traction and mobile drives i.e. for heavy duty machines for transportation of loose materials, earth, minerals, and solid fuels etc.

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Citations (4)

• 2003
  • 2003-12-15 CZ CZ200414965U patent/CZ14832U1/cs not_active IP Right Cessation
  • 2003-12-15 CZ CZ20033411A patent/CZ20033411A3/cs not_active IP Right Cessation
• 2004
  • 2004-12-10 WO PCT/CZ2004/000084 patent/WO2005057047A1/en active Application Filing

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