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EP2802791A2 - Système de transmission de puissance, procédé de transmission de puissance dans un système de type engrenage et utilisation d'un système de transmission de puissance - Google Patents

Système de transmission de puissance, procédé de transmission de puissance dans un système de type engrenage et utilisation d'un système de transmission de puissance

Info

Publication number
EP2802791A2
EP2802791A2 EP12840552.9A EP12840552A EP2802791A2 EP 2802791 A2 EP2802791 A2 EP 2802791A2 EP 12840552 A EP12840552 A EP 12840552A EP 2802791 A2 EP2802791 A2 EP 2802791A2
Authority
EP
European Patent Office
Prior art keywords
gear
pinion
unit
gearing
gears
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.)
Withdrawn
Application number
EP12840552.9A
Other languages
German (de)
English (en)
Other versions
EP2802791A4 (fr
Inventor
Taimo Majalahti
Pekka Majalahti
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP2802791A2 publication Critical patent/EP2802791A2/fr
Publication of EP2802791A4 publication Critical patent/EP2802791A4/fr
Withdrawn legal-status Critical Current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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. a stepped orbital gear or Ravigneaux
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2028—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 6 connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention relates to a power transmission arrangement as defined in the preamble of claim 1 and a method for power transmission in a gear system as defined in the preamble of claim 9.
  • a gearbox whose purpose is to convey the torque and rotational speed produced by a drive unit forward in a suitable extent.
  • a gearbox usually contains some gears for moving forward, and in addition cars have one reverse gear.
  • gearings may be needed.
  • one gear is used the most of time but in some special situations a different trans- mission is needed.
  • a good gearing would be such that it contains one gear for forward moving and additionally a reduction gear that transmits high torque to the wheels.
  • This kind of gearing would be suitable also for example for a fishing boat where in normal driving a normal gear could be used, and when trolling a gear allowing a slow speed could be used.
  • This kind of gearing is, however, known to be complicated to put into practice in a traditional way.
  • gearing In wind power plants producing electricity a gearing is needed to transmit the slow rotation of the wind rotor to a faster rotation suitable for the rotor of the electric generator. In the gearing of the wind power plant a fairly high gear ratio is needed, and because of this known gearings are extremely complicated and expensive with several gear wheels and other components. Several components make also the size and the mass of the gearing larger.
  • the object of the present invention is to eliminate the drawbacks described above and to achieve a cost effective and by its structure straightforward power transmission arrangement and method for transmitting power in a gearbox that contains a gear suitable for normal driving, and additionally one or more reduction gears and possibly also a reverse gear.
  • the object is to achieve a simply feasible power transmission arrangement and method for transmitting power in a gearing where the gear ratio is extremely high.
  • the power transmission arrangement according to the invention is characterized by what is presented in the characterization part of claim 1
  • the method according to the invention is characterized by what is presented in the characterization part of claim 9.
  • Other embodiments of the invention are characterized by what is presented in the other claims.
  • the solution of the invention has among other things the advantage that because only rotational force is aimed to the housing of the gearing, the housing can be extremely small, simple and lightweight by its structure. Yet, an advantage is that the power losses of the gearing are extremely small.
  • One advantage is also that in addition to a normal gear, one or more reduction gears, and if wanted also a reverse gear can be made to the gearing with ease and using simple structures.
  • a further advantage is also that the gear ratio of the gearing can be done easily and simply extremely high in which case the gearing suits well to use for example in wind power plants.
  • the contact surface of the teeth of the gearing is large, which has an advantageous effect among other things on the noise level, lubrication and material choices. Yet, an advantage is that the arrangement is simple, versatile and inexpensive to realize.
  • Fig. 1 presents in a side view and in a simplified way and in a cross section one embodiment according to the invention
  • Fig. 2 presents in a oblique side view a power-in unit or primary unit according to the solution of Fig. 1 ,
  • Fig. 3 presents in a side view and in a partial cross a power-in unit according to
  • Fig. 4 presents in a side view and in a simplified way and in a cross section one gear assembly with its bearings used in the arrangement according to the invention
  • Fig. 5 presents in a side view and in a simplified way and in a cross section one gear assembly according to Fig. 4 in its location in the primary unit
  • Fig. 6 presents in a side view and in a simplified way and in a cross section along the line B-B in Fig. 7 another embodiment according to the inven- tion
  • Fig. 7 presents a solution according to Fig. 6 in a simplified way and in a transversal section along the line A-A of Fig. 6,
  • Fig. 8 presents a transmission unit according to the solution of Fig. 6 in a side view, in a simplified way and in a cross section along the line B-C of Fig. 7,
  • Fig. 9 presents in a side view and in a simplified way and in a cross section one gear assembly used in the solution according to Fig. 6, and
  • Fig. 10 presents in a side view, schematically and in a simplified way and in a cross section a third embodiment of the arrangement according to the invention.
  • FIGs. 1 -5 an embodiment according to the invention is shown with its components.
  • Fig. 1 one embodiment according to the invention is presented in a side view and in a simplified way and in a cross section.
  • a power-in unit 8 or primary unit according to the invention is shown in a more precise way
  • Figs. 4 and 5 one pinion gear assembly 13 according to the invention is shown in a more precise way and in a side view, and in a simplified way and in a cross section.
  • Fig. 1 presents a gearbox where a gearing is fitted in an essentially cylindrical housing 1 that is for example essentially circular in its cross section and made of metal, such as aluminum by casting.
  • the housing 1 contains at least an essentially cylindrical frame 1 a and at the first end of the frame a a first end part 1 b equipped with a center hole and a bearing housing, and at the second end of the frame 1 a a second end part 1 c equipped with a center hole and a bearing housing.
  • the end parts 1 b and 1 c have been fastened to the frame 1 a for example by screw fastening.
  • the main parts of the gearing inside the housing 1 are the first axle or power-in axle 2, the second axle or power-out axle 3, the power-in unit 8, a power-out unit 21 , pinion gear assemblies 13, ring gears 18, 19, 20 with internal gears, brake units 29, 30 acting as gear actuators, clutch unit 22 and a clutch actuator for the clutch unit 22.
  • the power-in axle 2 and power-out axle 3 are mounted in bearings 4 and 5 on the end parts 1 b and 1 c of the housing 1 .
  • the primary axle 2 equipped with grooves 2a at its first end has been fitted to the housing 1 of the gearbox in a way that only the first end of the primary axle 2 is outside the housing 1 .
  • a first carrier flange 9 and a second carrier flange 10 are connected fixedly to the primary axle 2 and the carrier flanges form together with the coaxial primary axle 2 an essentially uniform power-in unit 8 or a primary unit cast for example of metal.
  • both the primary axle 2 and the carrier flanges 9, 10 rotates always together with the same speed towards the same direction around the central axis of the gearing, which central axis is coaxial with the rotation axis of the primary axle 2.
  • the primary unit 8 contains a cylindrical extension 1 1 that extends axially from the second carrier flange 10 and having the diameter of the inner surface advantageously larger than the diameter of the outer surface of the second carrier flange 10, and into which inner surface of the cylindrical extension a group of clutch discs 22a of the clutch unit 22 are fastened in order to couple the primary unit 8 to the power-out unit 21 or secondary unit equipped with the secondary axle 3.
  • the gearing according to the invention comprises additionally a group of mutually essen- tially similar pinion gear assemblies 13 whose gears 15, 16, 17 function like planet gears though the gearing does not contain a sun gear.
  • the pinion gear assemblies 13 are mounted in bearings 36 and 37 by their support shaft 14 on the carrier flanges 9 and 0 situated in the axial direction between the pinion gears 15-1 7.
  • the pinion gear assem- blies 13 can be radially at even angle intervals for example two, three, four, five, six or even more depending the size of the gearing.
  • the solution according to the example has four pinion gear assemblies 13 at even angle intervals, in which case the angle between them is 90 degrees. Fig.
  • Each pinion gear assembly 13 has three coaxial pinion gears 15-17 with an axial distance to each other and arranged to rotate with the support shaft 14 as one unit mutually at the same speed around the rotation axis of the support shaft 14, and the reference diameters of the pinion gears 15-17 are mutually of different sizes.
  • the first pinion gear 15 having the smallest diameter is machined directly to the axle 14
  • the middle or second pinion gear 16 having the largest diameter and the third pinion gear 17 having the second largest diameter are non-rotatably mounted in relation to the support shaft 14 by the help of grooves 38 and 39.
  • the gearing according the example comprises four mutually essentially identical pinion gear assemblies 13 that while rotating around their own support shaft 14 revolve at the same time also around the common rotation axis of the center axle or primary axle 2 and the secondary axle 3 of the whole gearing.
  • the ring gears 18-20 with internal gears are fitted to mesh with pinion gears 15- 7 of the pinion gear assemblies 13 so that all the first pinion gears 15 of the pinion gear assemblies 13 are mutually simultaneous meshing with smallest diameter internally geared first ring gear 18 that is mounted on a bearing 2b to the primary unit 8 to rotate in relation to the primary unit 8.
  • all the second pinion gears 16 of the pinion gear assemblies 13 are mutually simultaneous meshing with largest diameter internally geared second ring gear 19 that is freely supported on the second pinion gears 16, and all the third pinion gears 17 of the pinion gear assemblies 3 are mutually simultaneous meshing with the internally geared third ring gear 20 having a diameter that is only slightly larger than the diameter of the first ring gear 18, and being fixedly connected to the secondary unit 21 that is mounted on a bearing 4a to the second end 12 of the primary unit 8 to rotate in relation to the primary unit 8. All the internally geared ring gears 18-20 are mutually coaxial and fitted to rotate around the common rotation axis of the center axle or primary axle 2 and the secondary axle 3 of the whole gearing.
  • the gearing comprises the brake unit 29 of the first ring gear 18 and the brake unit 30 of the first ring gear 19, which brake units 29, 30 are arranged to stop the rotational movement of the ring gears 18, 19 one at a time when using the gearing.
  • the brake units guided electrically or hydraulically to move axially are coupled non-rotatably to the inner surface of the cylindrical frame 1 a of the gearbox housing 1 for example by the help of axially directed grooves 31 .
  • each pinion gear assembly 13 shows only three pinion gears 15-17 having different reference diameters, but on the same support shaft 14 there can be also more coaxial pinion gears with mutually different reference diameters, and the inner surface of the housing 1 comprises in that case internally geared and non-rotatable lockable ring gears corresponding each pinion gear.
  • the largest diameter pinion gear produces to the secondary axle 3 the slowest speed of rotation in the direction of the primary axle 2, and the smallest diameter pinion gear produces the reverse rotation in the direction of the primary axle 2 as long as even the smallest pinion gear has a larger reference diameter than the pinion gear 17 meshing with the ring gear 20 of the secon- dary unit 21 .
  • the gearing comprises in addition also the clutch unit 22 whose clutch discs 22a, 22b are situated between the inner surface of the cylindrical extension 1 1 of the primary unit 8 and the outer surface of the third internally geared ring gear 20.
  • the first clutch discs 22a are fitted into their location by the help of the axial grooves 23 of the primary unit 8, and the second clutch discs 22b are fitted into their location by the help of the axial grooves 24 of the secondary unit 21 .
  • the clutch discs 22a, 22b When using the clutch the clutch discs 22a, 22b are pressed tightly against each other with an electric or hydraulic actuator 27 by the help of a thrust bearing 25 and a pressing member 26, and then all the gears and other rotating components of the gearing are rotating as one unit mutually the same speed, and inside the gearbox the gears or other rotating components do not have a different rotation speed in relation to each other.
  • the electric or hydraulic driving power for the actuator 27 of the clutch unit 22 is conducted via an energy interface 28 through the second end part 1 c of the gearing housing 1 .
  • the power-in unit 8 or primary unit according to the invention is presented in a more precise way.
  • the primary unit 8 comprises at least the primary axle 2, the first carrier flange 9, the second carrier flange 10 and the cylindrical extension 1 1 of the primary unit extending from the second carrier flange 10. All the components 2 and 9-1 1 mentioned are mutually coaxial.
  • the primary unit 8 comprises at least bridges 32 connecting the carrier flanges 9 and 10, the number of the bridges being advantageously as many as the number of the pinion gear assemblies 13, that is four pieces in the case according to the example, and the bridges 32 are advantageously mutually at even angle intervals on the outer perimeter of the flanges 9, 10 or near the mentioned outer perimeters.
  • the second pinion gears 16 are fitted between the flanges 9 and 10, and between the bridges there are openings 33 through which the teeth of the second pinion gears 16 are arranged to extend at least outside the outer perimeter of the first carrier flange 9, and to mesh with the second ring gear 19.
  • the primary axle 2, the first carrier flange 9, the second carrier flange 10 and the cylindrical extension 1 of the primary unit extending from the second carrier flange 10, and the bridges 32 form a uniform entity, for example cast of the same material, like metal, called the primary unit 8 where all the mentioned components 2, 9-1 1 and 32 are fixedly integral to each other and rotate always mutually to the same direction and the same speed of rotation around the central axis of the primary unit 8 and at the same time around the central axis of the primary axle 2.
  • the first carrier flange 9 of the primary unit 8 has holes 34 mutually at even angle intervals for the first bearings 36 of the pinion gear assemblies 13, and correspondingly the second carrier flange 10 of the primary unit 8 has holes 35 mutually at even angle intervals for the second bearings 37 of the pinion gear assemblies 13.
  • the inner surface of the cylindrical extension 1 1 of the second carrier flange 10 comprises axial grooves 23 in order to fit the first clutch discs 22a of the clutch unit 22 into their location non-rotary in relation to the primary unit 8 but movable in the axial direction.
  • the grooves 23 are not shown in Fig. 2, and in Fig. 3 they are shown only in the upper and lower edge of the inner surface of the extension 1 1. In Figs.
  • one pinion gear assembly 13 is shown in a more precise way in a side view, simplified and in a cross section.
  • the pinion gear assembly 13 is disconnected and in Fig. 5 it is installed to the primary unit 8.
  • the first pinion gear 15 having the smallest diameter is machined directly to the support shaft 1
  • the middle or second pinion gear 16 having the largest diameter and the third pinion gear 17 having the second largest diameter are non-rotatably mounted in relation to the support shaft 14 by the help of grooves 38 and 39.
  • the first bearing 36 of the support shaft 14 is situated between the first pinion gear 15 and the second pinion gear 16, and correspondingly the second bearing 37 of the support shaft 14 is situated between the second pinion gear 16 and the third pinion gear 17.
  • the second pinion gear 16 can be a spur gear, but advantageously it is a double-helical gear that cannot move in the axial direction and is therefore at the same time arranged to keep the freely supported internally geared ring gear 18 meshing with it axially at its location, which ring gear 19 has in that case also herringbone teeth.
  • the power transmission arrangement functions as follows: All rotational directions are looked as axial view from the primary axle 2 towards the secondary axle 3.
  • the support shafts 14 of the pinion gear assemblies 13 with their pinion gears 15-17 are also revolving clockwise around the rotation axis of the primary axle 2. Because all the pinion gears 15-17 of the same support shaft 14 are non-rotatably mounted on their support shaft and there is no mutually relational rotation between them, all the pinion gears 15-17 with their support shafts 14 are forced to rotate together at the same clockwise speed around the rotation axis of the primary axle 2.
  • the third pinion gears 17 of the pinion gear assemblies 13 are meshing with the third internally geared ring gear 20 that belongs integrally to the secondary unit 21 .
  • the tooth contact of the third pinion gears 17 with the third internally geared ring gear 20 compels all the support shafts 14 with their pinion gears 16-17 to rotate on their own bearings 36, 37 counter-clockwise around the own rotation axis of the support shafts 14.
  • the second pinion gears 16 Because the diameter and number of teeth of the second pinion gears 16 is larger than the diameter and number of teeth of the third pinion gears 17, the second pinion gears 16 rotating counter-clockwise around their own support shafts 14 compel the second internally geared ring gear 19 freely meshing with them to rotate counter-clockwise around the rotation axis of the primary axle 2 of the gearing.
  • the diameter and number of teeth of the first pinion gears 15 is smaller than the diameter and number of teeth of the third pinion gears 17, the first pinion gears 15 rotating counter-clockwise around their own support shafts 14 compel the first internally geared ring gear 8 meshing with them to rotate clockwise around the rotation axis of the primary axle 2 of the gearing.
  • the clutch unit 22 When to highest speed of rotation of the secondary axle 3 is wanted the clutch unit 22 is activated, in which case the clutch discs 22a, 22b are pressed tightly against each other with an electric or hydraulic actuator 27 by the help of a thrust bearing 25 and a pressing member 26, as already mentioned above.
  • the brake units 29, 30 when the brake units 29, 30 are not activated, all the gears 15-17 and 18-20, axles 2, 3, 14 and other rotating components 9- 14 and 21 -26 of the gearing are rotating around the rotation axis of the primary axle 2 of the gearing as one unit mutually the same speed, and inside the gearbox the gears or other rotating components do not have a different rotation speed in relation to each other.
  • the secondary axle 3 is forced to rotate to the same direction and with the same speed than the primary axle 2, in which case the transmission of the gearing is direct, or the transmission ratio is 1 :1 .
  • the internal structure of the gearing is in a dormant state, in which case the power loss between the primary axle 2 and the secondary axle 3 is at its minimum, and conversely the efficiency is at its maximum.
  • a gear suitable for example for fast forward driving is coupled on in the gearing.
  • the clutch 22 is released and the brake unit 30 of the second ring gear 19 is activated in order to stop the second ring gear 19.
  • the applications can be for example wind power plants where the gear ratio as high as 1 :100...1 :200, advantageously 1 :120...1 :150 between the primary axle 2 and the rotor unit 42a acting as a power-out unit, is possible to achieve.
  • One advantage of the structure is among other things the fact that thanks to the high gear ratio the rotor unit 42a is made to rotate extremely fast, in which case the size of the rotor unit 42a and the size of the whole generator 41 can be much smaller than the structures of prior art.
  • the size of the gearing according to the invention realized with extremely few gearing components can be much smaller than the corresponding structures of prior art.
  • rotational force is aimed to the housing 1 , which further helps in making the size of the housing smaller and lighter. Consequently, when used as an accelerating gearing in a wind power plant the structure according to the invention can be by its size and weight as much as about 50% smaller and lighter than the corresponding structures of prior art.
  • the structure according to the invention can be also used as a reduction gearing, in which case the generator 41 acts as an electric motor and the axle 2 acts as a power-out axle. In that case an extremely high torque is obtained from the power-out axle with a slow speed of rotation.
  • a gearbox according to the invention in which gearbox the gearing is fitted into an essentially cylindrical housing 1 that is for example circular in its cross section and made of some appropriate metal.
  • the housing 1 contains at least an essentially cylindrical frame 1 a and at the f irsf end of the frame 1 a a first end part 1 b equipped with a center hole and a bearing housing, and at the second end of the frame 1 a a second end part 1 c equipped with a center hole and a bearing housing.
  • the end parts 1 b and 1 c have been fastened to the frame 1 a for example by screw fastening.
  • the main parts of the gearing in the housing 1 are the first axle 2 called later the power-in axle 2 or the primary axle, power-in unit 8, power transmission unit 21 a, pinion gear assemblies 13, internally geared ring gears 18a and 19, generator 41 and as a power-out unit acting rotor unit 42a that is a part of the generator 41 .
  • the power-in axle 2 or the primary axle is placed in the housing 1 of the gearbox so that only the first end of the first axle 2 equipped with the grooves 2a is outside the housing 1.
  • the primary axle 2 extends to a first flange 40, at the vicinity of the outer rim of which the first internally geared ring gear 18a coaxial with the primary axle 2 is mounted for example with a screw fastening.
  • the primary axle 2, the first flange 40 and the first ring gear 18a form the power-in unit 8 or the primary unit that is mounted with its first end on the first end 1 b of the housing 1 with a bearing 4, and with its second end 12 on the on the power transmission unit 21 a with a bearing 12a.
  • the power transmission unit 21 a that is shown more precisely in Fig. 8 consists of at least three support flanges 9a, 10a and 1 1 a, and a second axle 3b called later the transmission unit support axle 3b, all the parts 3b and 9a-1 1 a being mutually coaxial.
  • the transmission unit 21 a mounted on bearings to rotate freely is mounted with its first end to the second end of the primary axle 2 by the help of the bearing 12a, and with its second end to the second end part 1 c of the housing 1 by the help of the bearing 5.
  • the power transmission unit 21 a comprises a group of mutually essentially similar pinion gear assemblies 13, which can be radially at even angle intervals for example two, three, four, five, six or even more depending the size of the gearing.
  • the solution according to the example shown in Figs. 6-9 has three pinion gear assemblies 13 at even angle intervals, in which case the angle between them is 120 degrees.
  • each pinion gear assembly 13 has two pinion gears of which the first pinion gears 15a are smaller by their reference diameter than the second pinion gears 16.
  • the pinion gears 15a and 16 are fitted to rotate around the rotation axis of the support shaft 14 at the same speed of rotation with each other and with the support shaft 14.
  • the support shaft 14 is mounted with its first end to the first support flange 9a of the transmission unit 21 a by the help of a bearing 36, and with its second end to the third flange 1 1 a of the transmission unit 21 a by the help of a bearing 37.
  • the first pinion gear 15a is arranged to mesh with the internally geared ring gear 18a having a smaller reference diameter
  • the second pinion gear 16 is arranged to mesh with the internally geared ring gear 19 having a larger reference diameter, which ring gear 19 is locked nonrotary in relation to the housing 1 to the inner surface of the frame part 1 a of the housing 1 by the help of grooves 31 or the corresponding locking elements.
  • the rotor unit 42a of the generator 41 is mounted with its first end to a stationary support flange 43 inside the housing 1 by the help of a bearing 5a, and with its second end 42b to the second end part 1 c of the housing 1 by the help of a bearing 5b.
  • the shaft of the rotor unit 42a is hollow and is fitted over the support axle 3b of the transmission unit 21 a.
  • an isolating, anti-magnetic flange 44 in connection of which there is a rotor 45.
  • the stator coil 46 of the generator 41 is at the second end of the housing 1 inside an isolating, anti-magnetic protective sheath 47.
  • a tapping point 48 of the produced electricity has been conveyed from the generator 41 through the second end part 1 c of the housing 1 .
  • a seal 6 Between the primary axle 2 and the first end part 1 b of the housing 1 there is further a seal 6, and correspondingly at the second end of the housing 1 there are seals 7a in order to seal the oil space of the gearing and to separate it from the generator 4 .
  • a solution according to Fig. 6 is shown in a simplified way and in a transversal section along the line A-A of Fig. 6.
  • a transmission unit 21 a according to the solution of Fig. 6 is shown in a more precise way in a side view and in a simplified way and in a cross section along the line B-C of Fig. 7.
  • FIG. 7 shows the second support flange 10a of the transmission unit 21 a and in front of it three pinion gears 16 that are on their shafts 14 and are meshing with the second internally geared ring gear 19.
  • Fig. 7 shows bridges 32a between the second flange 10a and the third support flange 1 1 a of the transmission unit 21 a, which bridges are three pieces at even angle intervals in the gaps between the second pinion gears 16. Between the bridges 32a there are gaps 33a for the second pinion gears 16 in order to make the tooth contact with the pinion gears 16 and the second internally geared ring gear 19 feasible.
  • the second pinion gears 16 of the pinion gear assemblies 13 have been mounted on the support shaft 14 through an elastic joint 16a, in which case the torque transmitting to the pinion gear 16 effects a small spring between the second pinion gear 16 and the support shaft 1 and the first pinion gear 15a.
  • the support shaft 14 can be realized so that it yields optimally in its twist direction so that the support shaft 14 makes an even pressure caused by the flank contact possible in the tooth contact.
  • Fig. 8 one transmission unit 21 a according to the invention is shown in a cross section.
  • the first support flange 9a At an axial distance from it there is the second support flange 10a, further at an axial distance from it there is the third support flange 1 a.
  • the support axle 3b At the second end of the transmission unit 21 a there is the support axle 3b whose first end extends to the second support flange 10a through the center hole 50 of the third support flange 11 a, through which center hole 50 the sun gear 42 of the rotor unit 42a has been fitted to its location.
  • the first carrier flange 9a has holes 34 at even angle intervals for the first bearings 36 of the pinion gear assemblies 13, and the third carrier flange 1 1 a has holes 35 at even angle intervals for the second bearings 37 of the pinion gear assemblies 13.
  • the second carrier flange 10a has holes 49 at even angle intervals for the support shafts 14 of the pinion gear assemblies 13.
  • the support flanges could be also only two, for example only the support flanges 9a and 10a, in which case the second bearing 37 should be placed on the second support flange 0a. In that case, however, the axial distance of the bearings 36 and 37 becomes shorter compared to what is presented above.
  • the short distance saves room and material but correspondingly the longer distance presented earlier and the three support flanges make extremely balanced and steady bearing structure possible.
  • the bridges 32a are for example the same casting with the support flanges 9a-1 1 a and the support axle 3b as shown in Fig. 8, or they can also be separate and for example fastened to the support flanges with a screw fastening.
  • pinion gear assembly 13 used in the solution according to Fig. 6 is shown in a side view, in a simplified way and in a cross section.
  • the first pinion gear 15a with a smaller reference diameter is mounted on its support shaft 14 with grooves 38 to be nonrotary in relation to the support shaft 14.
  • the second pinion gear 16 with a larger reference diameter is mounted on its support shaft 14 with the elastic joint 16a to be non-rotary in relation to the support shaft 14 as mentioned earlier.
  • the transmission unit 21 a with its flanges 9a-11 a, support axle 3b and bridges 32a, and pinion gear assemblies 13 form a solid entity that rotates as one unit always to the same direction and at the same rotation speed around the central axis of the gearing, which central axis is at the same time the rotation axis of the primary axle 2 and the support axle 3b of the transmission unit 2 a, and the rotor unit 42a.
  • the gearing arrangement according to the invention shown in Figs. 6-9 works as follows: All directions of rotation is seen from direction of the primary axle 2 towards the second end of the gearing.
  • the primary axle 2 of the primary unit 8 is rotated clockwise by the help of an external power source, for example the rotors of the wind power plant, the first internally geared ring gear 18a is also rotating clockwise with the same speed, and meshing with the first pinion gears 15a of the pinion gear assemblies 13 causes a large clockwise torque to the first pinion gears 15a.
  • first pinion gears 15a of the pinion gear assemblies 13, support shafts 14 and the second pinion gears 16 cannot rotate in relation to each other, they have no mutual relative rotary motion between them, in which case the essentially same clockwise torque is transmitted through the support shafts 14 and the second pinion gears 16 to the second internally geared ring gear 19 that is locked with the grooves 31 non-rotary in relation of the housing 1 of the gearing. Because the second internally geared ring gear 19 does not rotate, the mentioned clockwise torque forces the support shafts 14 and the first and second pinion gears 15a, 16 of the pinion gear assemblies 13 to rotate counter-clockwise around the central axis of the support shafts 14 on the bearings 36, 37 of the support shafts 14.
  • the pinion gears 15a, 16 rotating together to the same direction and the same speed are forced to rotate counter-clockwise around the central axis of the support shaft 14.
  • the whole transmission unit 21 a with its flanges 9a-11 a and bridges 32a is revolving clockwise around the central axis of the primary axle 2 of the gearing at the speed of rotation caused by the same gear ratio, the central axis of the primary axle 2 being congruent with the central axis of the whole gearing.
  • the mentioned second pinion gears 16 are also meshing with the sun gear 42 at the first end of the rotor unit 42a, which sun gear belongs as an integrated structure to the rotor unit 42a, or is coupled to rotate with the rotor unit 42a for example by the help of a groove fastening.
  • the rotary motion of the sun gear 42 forces also the rotor unit 42a with its rotor 45 to rotate clockwise at the same high speed of rotation.
  • the gear ratio determined by the differences of the reference diameters of the first and second pinion gears 15a, 16, and the gear ratio between the second ring gear 19 and the sun gear 42 together form an extremely high combined gear ratio that forces the rotor unit 42a with its rotor 45 to rotate at an extremely high speed.
  • the solution according to the invention makes it possible to achieve for example a gear ratio between 1 :100...1 :200, suitably for example between 1 :120... :150.
  • the rotor unit 42a of the generator with its rotor 45 rotates at the speed of 1400 rpm. Thanks to an extremely high speed of rotation about 60% smaller magnetic flux resistance is achieved in the air gap between the rotor 45 and the stator winding 46, which feature makes an essentially equal output power of the generator 41 possible as in prior art generators of double size, which prior art generators are used for example with double planet gears that achieve a gear ratio of at maximum only about 1 :50.
  • the mentioned smaller magnetic flux resistance or braking power in the air gap between the rotor 45 and the stator winding 46 makes also much smaller flank pressures or surface pressures possible to the teeth of the sun gear 42.
  • the speed of rotation of the rotor 45 more than twice as high as with the conventional solutions
  • the sun gear 42 with its diameter 30% larger than in the conventional solutions make about 50-60% smaller Hertzian surface pressure possible on the contact surfaces of the sun gear 42 than in prior art solutions with double planet gears and with sun gears of the same width and under the same load.
  • a third embodiment of the arrangement according to the invention is shown. Also this structure suits very well to either an accelerating or a reduction gearing allowing a high gear ratio.
  • the applications can be for example wind power plants where it is possible to achieve a gear ratio as high as 1 :100...1 :200, suitably for example 1 :120 ...1 :150 between the primary axle 2 and the second axle 3 acting as a power-out unit.
  • An advantage of the structure is among other things the fact that thanks to the high gear ratio the second axle 3 is made to rotate extremely fast, in which case the size of the generator or the electric motor coupled to the second axle 3 can be much smaller than the structures of prior art.
  • the structure according to Fig. 10 has more components, weight and axial measurements than the corresponding structure according to Fig. 6, but correspondingly the structure according to Fig. 10 is extremely robust and it has no large diameter bearings whose large diameter and speed of rotation might cause too high circumferential speeds of the bearing surface.
  • the size of the gearing according to Fig. 10 can also be much smaller than the corresponding structures according to prior art.
  • the housing 1 is only loaded by rotational counterforce, which further helps in reducing the size and weight of the housing.
  • the structure according to the invention can be by its size and weight as much as about 50% smaller and lighter than the corresponding structures according to prior art.
  • the first axle 2 acting as a power-in axle or power-out axle in this example the primary axle is fitted in the housing 1 of the gearbox in the way that only the first end of the primary axle 2 equipped with grooves 2a is outside the housing 1.
  • the primary axle 2 extends to the flange 40 at the proximity of whose perimeter the first internally geared ring gear 18a, coaxial with the primary axle 2, is fastened for example by a screw fastening 40a.
  • first flange 40 and the first ring gear 18a form together the power-in unit 8 or primary unit that is mounted at its first end on the first end flange 1b of the housing in a bearing 4, and at its second end on the power transmission unit 21 a in a bearing 12a.
  • the hub of the flange 43a that is fastened with screws 60 to the non-rotary housing 1 there is a bearing 5a by which the second end of the power transmission unit 21 a is bearing-mounted on the flange 43a.
  • the power transmission unit 21 a has two support flanges 9a and 1 1 a, of which the first support flange 9a coupled to the power transmission unit 21 a with a groove fastening 52, is the nearest to the power-in unit 8.
  • the second support flange 1 1 a is integrally the same metal with the power transmission unit 21 a.
  • pinion gear assemblies 13 each consisting of the first pinion gear 15a with a smaller reference diameter and integrally the same metal with the support shaft 14 of the pinion gear assembly 13, and of the second pinion gear 16 with a larger reference diameter, and coupled with a groove joint 16b to rotate together at the same speed with the first pinion gear 15a and with the support shaft 14.
  • the internally geared ring gear 18a belonging to the primary unit 8 is meshing with the smaller reference diameter first pinion gears 15a of the pinion gear assemblies 13, and the internally geared ring gear 19 screw fastened non-rotary to the non-rotary housing 1 a is meshing with the larger reference diameter second pinion gears 16 of the pinion gear assemblies 13.
  • the pinion gear assemblies 13 are at even angle intervals for example 2, 3, 4 or even more.
  • the groove joint 6b of the second pinion gears 16 to the support shaft 1 has an inclined serration when the meshing contacts 15a, 18a and 16, 19 have spur gears.
  • the mentioned meshing contacts 15a, 18a and 16, 19 have helical gears it is sufficient to make the groove joint 16b with a straight serration.
  • spur teeth are used in the pinion gears 15a and 16 of the pinion gear assemblies 3 and correspondingly in the internally geared ring gears 18a and 19, the mentioned inclined serration joint has been cut so that the second pinion gear 16 having a larger reference diameter is pressed by the influence of the rotating load axially towards the smaller first pinion gear 15a.
  • An elastic ring 16a made of flexible material is fitted on the both sides of the pinion gear 16, which elastic ring yields optimally a short way in the axial compression caused by the inclined serration joint 16b.
  • the small axial movement of the pinion gears 16 can take place also away from the pinion gear 15a. If more traction load is directed to one of the larger pinion gears 16 of the pinion gear assemblies 13 than to the corresponding pinion gears 16 of the other pinion gear assemblies 13, then the more rotary loaded pinion gear 16 minimally moves in the axial direction slightly closer to the smaller pinion 15a being its pair.
  • the inclined serration 16b makes with the same movement the most loaded pinion gear 16 also yield optimally a little bit in the rotary direction, in which case more traction load passes to the other correspond- ing pinion gear pairs. Consequently, in the meshing contacts 15a, 18a and 16, 19 an even traction load is distributed to all the flanks of the pinion gears.
  • the pinion gear 16 is supported axially from the side of the flange 1 1 a on its support shaft 14 with a fitting ring 51 .
  • the aim of the inclined serration 16b is a small flexibility in the rotary direction, which flexibility makes the load of the pinion gears more even.
  • the second pinion gears 16 having the larger reference diameter are fitted with straight serration joints 16b on the support shafts 14.
  • the helical toothing causes axial pressure in the rotary load, in which case a suitably resilient elastic ring 16a between the pinion gears 15a and 16 yields a little bit.
  • the first part of the gearing structure according to Fig. 10 is a gear arrangement that forms one fixed gear ratio, which arrangement has no sun gear but the pinion gears 15a and 16 working partially as planet gears are meshing only with the internally geared ring gears 18a and 19.
  • Fig. 10 works for instance as follows: All rotational directions are looked from the direction of the primary axle 2 towards the second end of the gearing.
  • an external power source for example by the rotors of the wind power plant
  • the internally geared ring gear 18a rotates clockwise at the same speed and torque and when meshing with the first pinion gears 15a causes a high clockwise torque to the first pinion gears 15a of the pinion gear assemblies 13.
  • first pinion gears 15a, support shafts 14 and the second pinion gears 16 of the pinion gear assemblies 13 cannot rotate in relation to each other, the same clockwise torque is directed through the support shafts 14 to the second pinion gears 16 and through them to the second internally geared ring gear 19 screw-fastened to the non-rotary housing 1 a. Because the internally geared ring gear 19 does not rotate, the mentioned clockwise torque forces the first and second pinion gears 15a, 16 of the pinion gear assemblies 13 to rotate counter-clockwise with their support shafts 14 on the bearings 36, 37 around the central axis of the support shafts 14.
  • the reference diameter of the first pinion gears 15a is smaller than the reference diameter of the second pinion gears 16, which second pinion gears 16 are meshing with the non-rotary second internally geared ring gear 19. Consequently, the pinion gears 15a, 16 rotating together to the same direction and at the same speed are forced to rotate counter-clockwise together around the central axis of the support shafts 14. This counter-clockwise rotary motion correspondingly forces the pinion gears 15a, 16 to revolve circumferentially clockwise in their meshing contacts in relation to both the internally geared ring gears 8a, 19.
  • the circumferentially revolving support shafts 14 force through the bearings 36, 37 the whole power transmission unit 21 a to rotate clockwise with the accelerating factor or gear ratio dictated by the difference of the refer- ence diameters of the pinion gears 15a, 16.
  • the same gearing is used as a reduction gearing and the first axle 2 serves as a power- out axle, then the same difference of the reference diameters between the pinion gears 15a, 16 dictates the gear ratio of the reduction gearing. If, however, the mutual differences of the diameters of the pinion gears 15a and 16 of the pinion gear assembly 13 and the internally geared ring gears 8a and 9 are changed to opposite, then also the direction of rotation of all the other rotating components of the gearing changes to opposite, only the direction of rotation of the primary unit 8 stays the same.
  • the mentioned power transmission unit 21 a rotates a traditional planet carrier 54 of the planet gears coupled to the second end of the transmission unit 21 a with a groove fastening corresponding the groove fastening 52, the planet carrier 54 having flanges 55a and 55b joined together with bridges of the same cast-steel construction and corresponding to the bridges shown for example in Figs. 7 and 8, which bridges are, however, for the sake of clarity not shown in Fig. 10.
  • the planet shafts 58 have been fitted according to the traditional way for example with a groove joint through the flanges 55a and 55b of the planet carrier 54, and between the flanges through the planet gears 57 equipped with bearings 61 . This way the planet gears 57 can freely rotate in their spaces between the support bridges.
  • the internally geared ring gear 59 of the planet gearing comprising the planet gears 57 is, for example, non-rotary fastened with a screw-fastening 60 at the second end of the housing 1 of the gearing.
  • the sun gear 42 belonging as an essential part to the planet gearing is the same steel with the second axle 3 acting now as a power-out axle, or is, for example, groove fastened to the mentioned second axle 3.
  • Both the internally geared ring gear 59 fastened non-rotary to the housing 1 and the sun gear 42 are in meshing contact with the planet gears 57 on the shafts 58.
  • the entity formed by the sun gear 42 and the second axle 3 is bearing-mounted at its first end on the second end of the power transmission unit 21 a with a bearing 53, and at its second end with a bearing 5 on the second end flange 1c of the housing 1 of the gearing.
  • the housing 1 of the gearing can be assembled for instance in a way that a part of the first end flange 1 b of the housing 1 of the gearing, a part of the second internally geared ring gear 19, a part of the flange 43a, and a part of the internally geared ring gear 59 of the planet gearing form together a cylindrical frame 1 a of the gearing where all the aforementioned parts are tightly fastened to each other with screws 60.
  • the pinion gear assemblies 13 When rotating counter-clockwise around the central axis of their own support shafts 14 the pinion gear assemblies 13 revolve simultaneously as a unity circumferentially towards right around the central axis of the whole gearing. Through the bearings 36, 37 the pinion gear assemblies 13 carry and force the whole transmission unit 21 a to revolve right at the gear ratio dictated by the difference of the reference diameter of the pinion gears 15a and 16. Consequently, for example: If the primary axle rotates 10 rpm and the difference of the reference diameter of the pinion gears 15a and 16 dictates the gear ratio of 1 :35, then the power transmission unit 21 a rotates 350 rpm.
  • the planet carrier 54 of the traditional planet gearing is fastened to the power transmission unit 21 a with a groove fastening corresponding the groove fastening 52, which power transmission unit therefore revolves the planet carrier 54 and the planet gears 57 rotatably bearing mounted in relation to the planet carrier to the right. Because the internally geared ring gear 59 of the planet gearing is non- rotatably screw-fastened to the housing 1 , the meshing contact between the internally geared ring gear 59 and the planet gears 57 forces these to the right circumferentially revolving planet gears 57 to a simultaneous fast counter-clockwise rotation around the central axis of their own planet shafts 58.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Retarders (AREA)
  • Gear Transmission (AREA)

Abstract

L'invention concerne un système de transmission de puissance comprenant au moins un ensemble de type engrenage qui présente un premier axe (2) tournant autour de son axe central et un second axe (3, 3b) tournant autour de son axe central ainsi qu'au moins deux ensembles pignons satellites (13) comportant au moins deux pignons satellites (15, 17) ayant des diamètres de référence différents les uns des autres et qui sont fixés coaxialement sur le même arbre (14) de support rotatif. Ledit ensemble de type engrenage comprend en outre des couronnes de trains planétaires (18-20) à engrenage intérieur qui s'engrènent avec les pignons satellites (15, 17), une couronne de trains planétaires (18, 19) à la fois étant montée de manière à être bloquée fixe de manière à ne pas tourner par rapport au carter (1). Les pignons satellites (15-17) tournent à la même vitesse les uns par rapport aux autres et dans la même direction avec leurs arbres de support (14). Au moins un pignon satellite (15a, 17) de chaque ensemble pignons satellites (13) est agencé de manière à s'engrener avec la couronne à trains planétaires (18a, 20) à engrenage intérieur.
EP12840552.9A 2011-10-12 2012-10-03 Système de transmission de puissance, procédé de transmission de puissance dans un système de type engrenage et utilisation d'un système de transmission de puissance Withdrawn EP2802791A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/FI2011/050886 WO2013053981A1 (fr) 2011-10-12 2011-10-12 Agencement de transmission de puissance et procédé et utilisation d'agencement de transmission de puissance
PCT/FI2012/050947 WO2013053988A2 (fr) 2011-10-12 2012-10-03 Système de transmission de puissance, procédé de transmission de puissance dans un système de type engrenage et utilisation d'un système de transmission de puissance

Publications (2)

Publication Number Publication Date
EP2802791A2 true EP2802791A2 (fr) 2014-11-19
EP2802791A4 EP2802791A4 (fr) 2016-03-02

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EP12840552.9A Withdrawn EP2802791A4 (fr) 2011-10-12 2012-10-03 Système de transmission de puissance, procédé de transmission de puissance dans un système de type engrenage et utilisation d'un système de transmission de puissance

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WO (2) WO2013053981A1 (fr)

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EP3971446A1 (fr) * 2020-09-16 2022-03-23 Siemens Aktiengesellschaft Modes générateur, chaine cinématique, éolienne et produit programme informatique
CN113431875B (zh) * 2021-05-13 2024-08-16 西安方元明科技股份有限公司 一种轴型作动设备

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DD255649A (fr) *
US707672A (en) * 1901-12-03 1902-08-26 George Samuel Baker Wheel-gear.
US1009954A (en) * 1908-07-28 1911-11-28 Jose Luis De Briones Speed-changing mechanism.
AT136892B (de) * 1931-10-02 1934-03-26 Ernst Alexander Dipl I Gessner Umlaufräderwechselgetriebe.
GB718645A (en) * 1951-05-16 1954-11-17 Ciotat La Improvements in or relating to transmission devices
GB948368A (en) * 1961-08-18 1964-02-05 Schwermaschb Karl Liebknecht Improvements in or relating to epicyclic gears
US3370832A (en) * 1966-01-12 1968-02-27 Ingersoll Rand Co Hoists
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ES8402646A1 (es) * 1983-02-19 1984-02-16 Parraga Garcia Julian Transmisiones para vehiculos y sus equipos y de aplicacion en la industria en general.
EP0125365A1 (fr) * 1983-02-19 1984-11-21 Julián PARRAGA GARCIA Transmission pour véhicules et applications industrielles
KR19990086790A (ko) * 1998-05-29 1999-12-15 배명순 내접 유성치차를 이용한 감속장치
JP2000027954A (ja) * 1998-07-09 2000-01-25 Sony Corp 遊星歯車用支持部材および遊星歯車の支持方法
FI115318B (fi) * 2001-08-13 2005-04-15 Interbak Ltd Sähkömekaaninen vaihteisto
KR100524255B1 (ko) * 2003-12-23 2005-11-01 조문행 복합 유성 기어 세트 및 이를 갖는 기어 트레인
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KR100947355B1 (ko) * 2008-02-12 2010-03-15 윤근수 다중기어열을 갖는 유성기어를 이용한 동력 전달장치 및 그이용방법

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WO2013053988A3 (fr) 2013-08-15
WO2013053981A1 (fr) 2013-04-18
WO2013053988A2 (fr) 2013-04-18
EP2802791A4 (fr) 2016-03-02

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