CN104781584A - Transmission unit comprising coupled planetary gear stages - Google Patents
Transmission unit comprising coupled planetary gear stages Download PDFInfo
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- CN104781584A CN104781584A CN201380057244.7A CN201380057244A CN104781584A CN 104781584 A CN104781584 A CN 104781584A CN 201380057244 A CN201380057244 A CN 201380057244A CN 104781584 A CN104781584 A CN 104781584A
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- 230000005540 biological transmission Effects 0.000 title abstract description 18
- 230000008878 coupling Effects 0.000 abstract description 3
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- 238000005859 coupling reaction Methods 0.000 abstract description 3
- 238000010276 construction Methods 0.000 description 6
- 238000005304 joining Methods 0.000 description 6
- 230000002349 favourable effect Effects 0.000 description 5
- 238000009826 distribution Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
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Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
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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)
Abstract
The invention relates to a transmission unit (1), in particular for a wind turbine, said unit comprising a first planetary gear stage (2) on the input side, a second planetary gear stage (3) and a third planetary gear stage (4) on the output side, each gear stage having a central sun gear (5; 6; 7), a ring gear (14; 15; 16) surrounding the sun gear and planetary gears (11; 12; 13) situated radially between the sun gear and ring gear, said planetary gears being rotatably mounted in a planetary carrier (8; 9; 10). The gear stages are coupled together using means, which can rotate about a rotational axis oriented in the longitudinal direction of the transmission unit (1), in such a way that the input speed of the transmission unit (1) can be increased on the output side. According to the invention, the means for coupling the first and second planetary gear stages (2; 3) comprise an output connection (21) which couples the sun gear (6) or the ring gear (15) of the second planetary gear stage (3) to the planetary carrier (10) or the ring gear (16) of the third planetary gear stage (4) in a rotationally fixed manner.
Description
Technical field
The present invention relates to a kind of gear unit as the form of specific definition in claim 1 preamble.
Background technique
Transmission device in particular for wind power plant is used for the conversion of the torque and rotational speed between transmission input shaft and transmission device output shaft.At this, high torque (HT) lower for rotating speed on transmission input shaft is converted to rotating speed on transmission device output shaft higher, the torque that reduces.In principle, this transmission device can be divided into the epicyclic gear stage having and connect successively or the transmission type with epicyclic gear stage in parallel.Comprise so-called differential attachment transmission device in a rear type, it is generally made up of three epicyclic gear stages.The favourable torque distribution on these two epicyclic gear stages can be realized by the suitable connection of the first two gear stage.Superimposed in third planet gear stage make it possible to realize power merge (Leistungszusammenf ü hrung) and accompany therewith, the high transmission ratio scope of corresponding displaying.
Summary of the invention
Realize based on the feature of object of the present invention by claim 1.Other favourable design proposals are drawn by dependent claims and accompanying drawing.
The present invention proposes a kind of gear unit in particular for wind power plant, it has first, second, and third epicyclic gear stage.First planet gear stage is at driving side, and at slave end, the second epicyclic gear stage is preferably placed in first in gear unit and the region between third planet gear stage third planet gear stage.These epicyclic gear stages have central sun gear, respectively around the gear ring of this sun gear and the planetary pinion that is arranged radially between both.Planetary pinion remains in planet carrier rotationally with being supported.The sun gear of epicyclic gear stage, planet carrier and/or gear ring can circumferentially constructing at gear unit rotationally or regularly.When the latter, it connects rigidly with the housing of gear unit or is configured to the part of housing.Three epicyclic gear stages and device is associated with one another like this connects: the rotating speed of the driving side of gear unit can be enhanced at slave end.The spin axis of these devices orientation in the longitudinal direction of gear unit constructs rotationally.These devices can have the medial axis of common axis of rotation line, especially gear unit or also can have the spin axis of self respectively.These spin axiss are directed in parallel with each other.Preferably these spin axiss are directed coaxially with each other at least partly.In order to connect second and third planet gear stage, these devices comprise driven connection set.The gear ring of the gear ring of the second epicyclic gear stage or sun gear and third planet gear stage or planet carrier preferably torsionally connect by this driven connection set.Therefore, these device configurations become the unit that can rotate around common axis of rotation line.Thus, gear unit can closely construct.In addition, the construction cost of gear unit is lowered, thus makes its manufacture become more favourable.
Favourable as follows: when the device for connecting the first and second epicyclic gear stages comprises driving connection set.Thus, the first and second epicyclic gear stages can so associated with one anotherly connect: the element (sun gear, planet carrier and/or gear ring) connect associated with one another can be rotated around common axis of rotation line as a unit.Thus, very can realize gear unit, because reduce constructions cost cost efficient.In addition can save costliness and troublesome bearing device, thus reduce the failure risk of gear unit.
Preferably, by means of driving connection set, the sun gear of an epicyclic gear stage in two epicyclic gear stages is torsionally connected with the planet carrier of another epicyclic gear stage.Make the sun gear of the planet carrier of the planet carrier of the sun gear of first planet gear stage and the second epicyclic gear stage or first planet gear stage and the second epicyclic gear stage by driving connection set to be torsionally connected thus.Alternatively or additionally, can connect torsionally associated with one another for two of a first and second epicyclic gear stages gear ring by means of driving connection set.The transmission of torque from first planet gear stage to the second epicyclic gear stage can be realized thus.Advantageously can be implemented to higher velocity ratio at a high speed thus.In addition, the structural volume of this gear unit is reduced by the connection of the first and second epicyclic gear stages, because easy break-down and the bearing device of costliness have been removed.
When the device for connecting the first and second epicyclic gear stages comprises two driving connection sets, higher velocity ratio at a high speed especially can be implemented to.At this, the different elements (sun gear, planet carrier and/or gear ring) of two epicyclic gear stages is coupled to each other by preferred each driving connection set.Like this, when first in two driving connection sets drive connection set the sun gear of the planet carrier of first planet gear stage and the second epicyclic gear stage is configured to each other by the planet carrier of the sun gear of first planet gear stage and the second epicyclic gear stage, second driving connection set respectively torsionally joining unit time, gear unit especially can realize simple structure.Alternatively, first drive that connection set connects two gear rings of the first and second epicyclic gear stages and second drives connection set to connect the sun gear of first planet gear stage and the planet carrier of the second epicyclic gear stage.In both of these case, gear unit can closely be formed.In addition higher velocity ratio at a high speed can be implemented in the simple situation of structure.Also can advantageously reducing effect to the torque on the first and second epicyclic gear stages, thus these epicyclic gear stages be constructed with saving very much structure space, because it need only carry less torque.
When device comprises total connection set of first, second, and third epicyclic gear stage rigid joint each other, then especially can reduce construction cost and the manufacture cost thus of gear unit.Three epicyclic gear stages are coupled to each other by this total connection set like this: the element of each epicyclic gear stage (sun gear, planet carrier and/or gear ring) is correspondingly configured to jointly can around the unit that circumferentially rotate of common axis of rotation line at gear unit.
When total connection set by the sun gear of first planet gear stage and second or third planet gear stage sun gear and when being torsionally connected with another the gear ring in these two epicyclic gear stages, lower absolute rotating speed and relative rotation speed and corresponding lower planetary gear set moment can be guaranteed.Total connection set connects the sun gear of first planet gear stage and the sun gear of the second epicyclic gear stage and the planet carrier of third planet gear stage thus.Or alternatively, total connection set connects the sun gear of first planet gear stage and the planet carrier of the second epicyclic gear stage and the sun gear of third planet gear stage.To very high velocity ratio at a high speed when can be implemented advantageously in the installing space of minimum gear unit thus.The advantage listed above of total connection set is especially present in the situation of following gear unit: wherein the torque of driving side is not assigned with, but enters into first planet gear stage completely.
Alternatively, be that tool is advantageous when the gear ring of first planet gear stage torsionally connects with the sun gear of the second epicyclic gear stage and the planet carrier of third planet gear stage by total connection set.Therefore, the planet carrier formation of the gear ring of first planet gear stage, the sun gear of the second epicyclic gear stage and third planet gear stage can around the co-rotational unit of spin axis.Thus, planetary gear set moment can be kept lower, because the torque of driving side can be assigned on all three epicyclic gear stages.Therefore, when the torque of driving side can be assigned on all epicyclic gear stages of gear unit, the advantage of the above-described connection of total connection set can especially be realized.Thus, gear unit can be configured to save very much structure space, because three epicyclic gear stages need only carry less point torque respectively.
Also advantageously, the gear ring of first, second, and third epicyclic gear stage is torsionally coupled to each other by total connection set.The constructions cost of gear unit can be reduced thus, thus make it possible to more manufacture gear unit cost efficient.
When the device for connecting first and third planet gear stage comprises bridge-type connection set, the rotating speed of gear unit driving side can be made effectively to improve at slave end.Preferably, this bridge-type connection set connects the sun gear of first planet gear stage and the planet carrier of third planet gear stage like this: enable them rotate around common axis of rotation line as a unit.In addition, gear unit also can be made thus closely to form.
Especially favourable when driving side torque is very high: to connect when epicyclic gear stage is associated with one another, the torque of driving side can be assigned at least two epicyclic gear stages, especially the first and second epicyclic gear stages and in third planet gear stage can merged time.Alternatively, the torque of driving side can also be made especially to be assigned on all three epicyclic gear stages when using total connection set.They the size of these epicyclic gear stages can be made thus less, because only must carry less torque.Therefore, the structural volume of gear unit is made to reduce.
When driving connection set or total connection set is configured to live axle at driving side or is torsionally connected with live axle, can structure space be saved and simple structure realize the torque distribution of driving side on multiple epicyclic gear stage.
When gear unit, especially, there is when being introduced in the torque of the driving side in first planet gear stage completely two devices, especially driven connection set, when driving connection set and/or total connection set, gear unit can be made with less constructions cost, more cost efficient ground, easily, with lower absolute rotating speed and relative rotation speed, extraordinary meshing efficiency, realize to the high transmission ratio of high speed and compact structure mode.
When the torque of driving side is assigned on multiple epicyclic gear stage, when gear unit has three devices, when especially driven connection set, driving connection set, bridge-type connection set and/or total connection set, especially can realize previously mentioned advantage.
Gear unit can structurally simply and firmly realize, when the sun gear of total support and live axle and/or third planet gear stage and driven shaft are connected.Live axle and driven shaft are arranged especially coaxially each other and/or are had identical sense of rotation.
Also advantageously, when third planet gear stage, be especially connected by means of its sun gear and cylindrical gears level (Stirnradstufe) time.Additionally can improve rated speed thus.Cylindrical gears level can be configured to, gear unit can be applied in the high-speed applications in wind energy generating plant.At this, for this reason set generator runs with the rated speed of about 1.5501/min.Alternatively, also cylindrical gears level so can be configured for middling speed application, wherein use generator speed obviously larger generator that is less, that be approximately 4501/min.In these two kinds of mode of executions, can both complete implementation structure form is compact, firm while realizing high transmission ratio advantage.
Accompanying drawing explanation
Below, by accompanying drawing, the invention will be further described.Wherein:
Fig. 1 and Fig. 2 shows the different mode of execution of two kinds of the gear unit with two driving connection sets and a driven connection set with the form of schematic half figure,
Fig. 3 partly illustrates the 3rd mode of execution with the gear unit driving connection set, bridge-type connection set and driven connection set with schematic,
Fig. 4 and Fig. 5 partly illustrates with schematic the 4th and the 5th mode of execution having total connection set, drive the gear unit of connection set and driven connection set,
Fig. 6 and Fig. 7 partly illustrates the 6th and the 7th mode of execution with the gear unit driving connection set and driven connection set with schematic, and
Fig. 8, Fig. 9 and Figure 10 are schematically partly to illustrate the 8th, the 9th and the tenth mode of execution of the gear unit with total connection set and driven connection set.
Embodiment
The different mode of execution of gear unit 1 is respectively illustrated in Fig. 1 to 10.Gear unit 1 especially arranges and is used for wind power plant and correspondingly has first planet gear stage 2, second epicyclic gear stage 3 and third planet gear stage 4.First planet gear stage 2 is arranged in the region of live axle 12 at driving side an.Third planet gear stage 4 constructs in the region of driven shaft 18 at slave end ab.Second epicyclic gear stage 3 is arranged between first planet gear stage 2 and third planet gear stage 4.Each in these three epicyclic gear stages 2,3,4 has a central sun gear 5,6,7 and the gear ring 14,15,16 around this sun gear respectively.Radial direction is furnished with multiple planetary pinion between both, and they engage with sun gear 5,6,7 and engage with gear ring 14,15,16 in radial outer region in inner radial region.According to schematically partly scheming, in the planetary pinion 11,12,13 of each epicyclic gear stage 2,3,4 is only shown in the drawings respectively.Planetary pinion 11,12,13 is kept in the radial direction of gear unit 1 by means of planet carrier 8,9,10 in each epicyclic gear stage 2,3,4.Planetary pinion 11,12,13 is contained in corresponding planet carrier 8,9,10 rotationally with being supported.Three epicyclic gear stages 2,3,4 are coupled to each other, and make the lower high torque (HT) of the rotating speed of driving side be converted into the higher low torque of the rotating speed of slave end.
Mode of execution shown in Fig. 1 to 10 difference is to each other its corresponding element (that is its corresponding sun gear 5,6,7; Planet carrier 8,9,10 and gear ring 14,15,16) between difference connect.These connections are coordinated, gear unit 1 is formed with saving very much structure space.Make the weight of gear unit less thus, thus make it especially can be used in the situation of wind power plant with flying colors.In addition, the feature of the different mode of executions of gear unit 1 is lower constructions cost, makes manufacture cost reduce thus.In addition, high transmission ratio is at a high speed implemented to when the current connection concept of gear unit 1 makes it possible at good meshing efficiency, lower absolute rotating speed and relative rotation speed and lower planetary gear set moment.
The mode of execution of the gear unit shown in Fig. 1 to 5 forms first group, and planetary gear set 2,3,4 is so associated with one another wherein connects: at least two that make the torque of driving side be assigned in epicyclic gear stage 2,3,4.At slave end, the torque be assigned with is at the second epicyclic gear stage (Fig. 1 and Fig. 2) or merged in third planet gear stage.
The mode of execution of the gear unit 1 shown in Fig. 6 to 10 forms second group, and the torque of driving side wherein is not assigned on multiple epicyclic gear stage 2,3,4.Alternatively, the torque of total in these embodiments driving side is introduced in first planet gear stage 2.
Gear unit shown in Figure 1 has three for connecting the device of three epicyclic gear stages 2,3,4.Correspondingly, the first and second epicyclic gear stages 2,3 and first drive connection set 19 and second to drive connection set 20 is associated with one another to be connect.First drives connection set 19 to connect the first row carrier 8 of first planet gear stage 2 and the second sun gear 6 of the second epicyclic gear stage 3.Second drives connection set 20 to connect the first sun gear 5 of first planet gear stage 2 and the second planet carrier 9 of the second epicyclic gear stage 3.In order to connect the second epicyclic gear stage 3 and third planet gear stage 4, gear unit 1 has the 3rd connection being configured to driven connection set 21.Driven connection set 21 connects the second gear ring 15 of the second epicyclic gear stage 3 and the third line carrier 10 of third planet gear stage 4.First drives connection set 19, second to drive connection set 20 and driven connection set 21 to be correspondingly configured to can substantially at the unit circumferentially rotated of gear unit 1.Therefore, corresponding epicyclic gear stage 2,3,4 correspondingly for this reason joining element with the circumferentially rotation of identical rotating speed at gear unit 1.
According to Fig. 1, first drives connection set 19 and live axle 17 are connected or are configured to live axle in the region of its driving side.Because first drives connection set 19, on the first row carrier 8 that the torque of driving side is assigned to the first and second epicyclic gear stages 2,3 and the second sun gear 6.Thus, two epicyclic gear stages 2,3 can be formed with saving very much structure space, because it need only carry less power.First gear ring 14 of first planet gear stage 2 constructs regularly.For this reason, the unshowned in FIG housing of itself and gear unit 1 is connected or is configured to this housing.Based on the partial torque be incorporated into by means of the first driving connection set 19 in first planet gear stage 2, the first row carrier 8 is placed in rotation, make first planet gear 11 rolling (abrollen) in the first fixing gear ring 14 be supported on rotationally wherein, make radial the first sun gear 5 connected in inside thus be placed in relative drive shaft 17 rotating Vortex.
Because second to drive connection set 20, second planet carrier 9 therefore in relative the first row carrier 8, the sense of rotation of relative drive shaft 17 identical orientation to be moved.Second planet carrier 9 due to the velocity ratio in first planet gear stage 2 faster than first drive connection set 19 and therewith joining second sun gear 6 rotate.Thus, in the region of radially outer, the second gear ring 15 be in joint is placed in and drives in the rotating of connection set 20 identical orientation relative to second with the second planetary pinion 12.Because the second gear ring 15 is connected with the third line carrier 10 by means of driven connection set 21, so third planet gear 13 so rolls in the 3rd fixing gear ring 16 of third planet gear stage 4
, the 3rd sun gear 7 be in third planet gear 13 in joint in the region of inner radial is placed in the rotation of relative drive shaft 17 identical orientation.3rd sun gear 7 is connected at slave end and driven shaft 18 or is configured to driven shaft.
In the connection concept of gear unit 1 shown in figure 2, the first and second epicyclic gear stages 2,3 drive connection sets 19,20 to be connected by means of first and second equally.First drives connection set 19 be torsionally connected with live axle 17 similarly or be configured to live axle 17 at driving side.
In addition, second is also effectively connected with driven connection set 21 with third planet gear stage 3,4.Be different from first embodiment shown in Figure 1, first drives connection set to comprise the first sun gear 5 and the second planet carrier 9.Therefore, the torque of driving side is introduced in gear unit 1 via live axle 17, and at this, first drives connection set 19 by torque distribution on the first and second epicyclic gear stages 2,3.Second drives connection set 20 torsionally to be connected with the second gear ring 5 of the second epicyclic gear stage 3 by first gear ring 14 of first planet gear stage 2.Connect as the 3rd, gear unit 1 comprised driven connection set 21 as previously implemented, and the second sun gear 6 of the second epicyclic gear stage 3 torsionally connects with the third line carrier 10 of third planet gear stage 4 by it.In addition, the first row carrier 8 of first planet gear stage 2 and the 3rd gear ring 16 of third planet gear stage 4 construct regularly.Thus, live axle 17, first drives connection set 19 and driven connection set 21 to rotate in a same direction.Second drives connection set 20 to rotate in contrast to this.
Therefore, according to Fig. 2, the first sun gear 5 and the second planet carrier 9 are placed in rotation by means of the torque on live axle 17, and at this, this torque is assigned on the first and second epicyclic gear stages 2,3.Because the first row carrier 8 is configured in first planet gear stage 2 regularly, therefore the effect of first planet gear 11 makes the sense of rotation of the first gear ring 14 relative drive shaft 17 move on the contrary.This is equally applicable to drive connection set 20 and the first gear ring 14 torsionally joining second gear ring 15 by means of second.Therefore, the second planet carrier 9 and the second gear ring 15 rotate each other in the opposite direction, make the rotating speed of the second sun gear 6 engaged with the second planetary pinion 12 improve thus.Due to driven connection set 21, second sun gear 6 by superimposed transmission of torque in the third line carrier 10.This makes third planet gear 13 roll in the 3rd fixing gear ring 16 and therefore make the 3rd sun gear 7 be placed in the rotation compared to the third line carrier 10 identical orientation.
There are in the alternate embodiments of gear unit 1 shown in Figure 3 three connections equally.The first driving connection set 19 be coupled through between the first row carrier 8 of first planet gear stage 2 and the second sun gear 6 of the second epicyclic gear stage 3 is formed.Connection set 19 and live axle 17 is driven to be connected or to form live axle at driving side.Therefore, the torque of driving side is assigned on the first row carrier 8 and the second sun gear 6.At slave end, gear unit 1 has the driven connection set 21 between the second epicyclic gear stage 3 and third planet gear stage 4, its by second and third planet gear stage 3,4 second and the 3rd gear ring 15,16 be torsionally coupled to each other.3rd connection of gear unit 1 constructs by means of bridge-type connection set 22, and therefore its cross-over connection second epicyclic gear stage 3 also connects first planet gear stage 2 and third planet gear stage 4.Bridge-type connection set 22 comprises the first sun gear 5 of first planet gear stage 2 at driving side and comprises the third line carrier 10 of third planet gear stage 4 at slave end.
Thus, the torque be introduced at driving side is assigned on the first row carrier 8 and the second sun gear 6 by means of driving connection set 19.Due to the first fixing gear ring 14, first planet gear 11 rolls, and the first sun gear 5 is placed in the rotation of relative drive shaft 17 identical orientation.Based on bridge-type connection set 22, the third line carrier 10 is rotated thus equally in the same rotational direction.In the region of the second epicyclic gear stage 3, the second planet carrier 9 constructs regularly.To be driven by the second sun gear 6 by the second planetary pinion 12 supported rotationally wherein, the second gear ring 15 is placed in and drives contrary the rotating of connection set 19 relative to first.3rd gear ring 16 is placed in the rotating of the second gear ring 15 identical orientation due to driven connection set 21.Therefore, the 3rd gear ring 16 and the third line carrier 10 are rotated each other in the opposite direction, thus the rotating speed of radial the 3rd sun gear 7 in inside engagement is significantly improved.Substitute embodiment shown in Figure 3, when exchanging the connection on the planet carrier and gear ring of the second epicyclic gear stage simultaneously, also the second epicyclic gear stage can be embodied as positive planetary gear set (Plus-Planetensatz), so that is like this gear ring of positive planetary gear set is fixing, so and planet carrier be connected with the gear ring of third planet gear stage.
Fig. 4 illustrates an embodiment of gear unit 1, and wherein, three epicyclic gear stages 2,3,4 are similar to and connect associated with one another connecing by means of three in the foregoing embodiments.Gear unit 1 has driving connection set 19, and it connects first planet gear stage 2 and second epicyclic gear stage 3.Drive connection set 19 to comprise the first sun gear 5 and the second planet carrier 9 for this reason.In addition, between second and third planet gear stage 3,4, be configured with driven connection set 21, two gear rings 15,16 of second and third planet gear stage 3,4 are connected by it.As the 3rd linkage member, gear unit 1 has total connection set 23, and the first gear ring 14, second sun gear 6 and the third line carrier 10 are configured to a unit that can rotate around spin axis by it.Total connection set 23 is configured to live axle 17 at driving side or is connected with live axle 17.
Thus, the torque of driving side is assigned on first, second, and third epicyclic gear stage 2,3,4 by total connection set 23.Drive first planet gear 11 based on fixing the first row carrier 8, first gear ring 14, make the first sun gear 15 or drive connection set 19 to rotate in the opposite direction compared to live axle 17.This is equally applicable to by means of joining second planet carrier 9 of driving connection set 19.Therefore in the second epicyclic gear stage 3, the second planet carrier 9 and the second sun gear 6 rotate in the opposite direction, thus the rotating speed of the second planetary pinion 12 is improved.Second planetary pinion 12 is engaged to again in the second gear ring 15 arranged in radial direction outer portion.Because driven connection set the 21, three gear ring 16 rotates in the opposite direction compared to the third line carrier 10, the rotating speed of third planet gear 13 is made again to be enhanced thus.Therefore based on the 3rd sun gear 7 engaged with third planet gear 13, the rotating speed of driven shaft 18 is obvious compared to live axle 17 higher.
Embodiment shown in Figure 5 is with embodiment is roughly the same shown in figure 2.Its difference is, the in Fig. 2 second driven connection set 20 is substituted by total connection set 23 in Figure 5.All three gear rings 14,15,16 of three epicyclic gear stages 2,3,4 are coupled to each other by this total connection set, thus are configured to a rotating unit.Therefore in the embodiment shown in fig. 5, the 3rd gear ring 16 is placed in rotation equally due to total connection set 23, and it is in contrast to the sense of rotation of driven connection set 21.Therefore, the rotating speed of third planet gear 13 is improved extraly, thus there is the driven shaft 18 rotated more quickly at slave end.
The embodiment of Fig. 6 to Figure 10 cited below does not have the torque distribution at driving side.As an alternative, the torque of driving side is brought in first planet gear stage 2 completely.For this reason, in all five kinds of mode of executions, the first row carrier 8 and live axle 17 are connected or are configured to live axle 17 at driving side.Therefore, rotated in the first fixing gear ring 14 by the first planet gear 11 supported rotationally in the first row carrier 8, the first sun gear 5 be in the region of inner radial in tooth engagement is placed in the rotation relative to the rotation same function of live axle 17.In addition, the embodiment shown in Fig. 6 to Figure 10 only has two connections.
First coupling configuration of gear unit 1 shown in Figure 6 becomes to drive connection set 19, and the first sun gear 5 torsionally connects with the second planet carrier 9 by it.Therefore second planet carrier 9 rotates on the direction identical with live axle 17.Because the second sun gear 6 of the second epicyclic gear stage 3 is formed regularly, the second gear ring 15 is placed in the sense of rotation consistent with the second planet carrier 9 by the second planetary pinion 12 equally.Torque by means of driven connection set 21, second gear ring 15 in the region be arranged between second and third planet gear stage 3,4 is delivered to the third line carrier 10.3rd gear ring 16 of third planet gear stage 4 constructs regularly, thus third planet gear 13 is rolled, and the 3rd sun gear 7 is placed in the rotation of relative drive shaft 17 identical orientation.Torsionally be connected at this driven shaft 18 and the 3rd sun gear 7.
In gear unit 1 shown in Figure 7, the first and second epicyclic gear stages 2,3 and driving connection set 19 are torsionally connected.Second is in effective connection by means of driven connection set 21 with third planet gear stage 3,4.At this, driven connection set 21 connects the first sun gear 5 and the second planet carrier 9.Second planetary pinion 12 is placed in rotation by this second planet carrier, thus makes the rolling in the second fixing gear ring 15 of this second planetary pinion, and the second sun gear 6 is placed in rotation.The torque of the second sun gear 6 is introduced in the third line carrier 10 by means of driven connection set 21.Be placed in rotation by means of third planet gear 13 based on the 3rd fixing sun gear the 7, three gear ring 16.3rd gear ring 16 is configured to driven shaft 18 at slave end or is torsionally connected with driven shaft 18.Live axle 17, driving connection set 19, driven connection set 21 and driven shaft 18 rotate in a same direction.
Embodiment shown in Figure 8 has two connections equally, and wherein, one of them coupling configuration becomes total connection set 23.Total connection set 23 connects the second planet carrier 9 of the first sun gear 5, second epicyclic gear stage 3 and the 3rd sun gear 7 of third planet gear stage 4 of first planet gear stage 2.They correspondingly rotate in the sense of rotation consistent with the sense of rotation of live axle 17.Between the second epicyclic gear stage 3 and third planet gear stage 4, be configured with driven connection set 21, this its, the second sun gear 6 of the second epicyclic gear stage 3 torsionally connected with the third line carrier 10 of third planet gear stage 4.Second gear ring 15 of the second epicyclic gear stage 3 constructs regularly, thus the second planetary pinion 12 be placed in rotation by means of total connection set 23 is rolled in the second gear ring 15, the second sun gear 6 be in the region of inner radial in tooth engagement is placed in rotation.At this, the sense of rotation of the second sun gear 6 conforms to the sense of rotation of live axle 17.Therefore, the 3rd sun gear 7 and the third line carrier 10 rotate in a same direction.Based on the velocity ratio in the second epicyclic gear stage 3, the third line carrier 10 rotates faster compared to the 3rd sun gear 7, thus the 3rd gear ring 16 is placed in rotation on the direction relative to live axle 17 identical orientation.3rd gear ring 16 is torsionally connected with driven shaft 18 or is configured to driven shaft 18 at slave end.
The alternative connection concept of gear unit 1 shown in Figure 9 haply with gear unit 1 shown in Figure 8 connection concept consistent.Difference is, driven connection set 21 is configured between the second sun gear 6 and the 3rd gear ring 16.Therefore, the 3rd gear ring 16 and the 3rd sun gear 7 rotate in a same direction.But because driven connection set 21 rotates faster compared to total connection set 23, therefore the third line carrier 10 is placed in the rotation relative to live axle 17 identical orientation.
According to the tenth embodiment shown in Figure 10, three epicyclic gear stages 2,3,4 connect by means of total connection set 23 is associated with one another equally.This total connection set comprises the first sun gear 5, second sun gear 6 and the third line carrier 10.They correspondingly rotate in the sense of rotation of relative drive shaft 17 identical orientation as unit.Second epicyclic gear stage 3 and third planet gear stage 4 are connected by driven connection set 21, and the second gear ring 15 and the 3rd gear ring 16 are torsionally connected to each other by it.Second planet carrier 9 of the second epicyclic gear stage 3 constructs regularly, thus the second gear ring 15 or driven connection set 21 are placed in contrast in the rotation of total connection set 23.Therefore also rotate in the opposite direction based on driven connection set the 21, three gear ring 16 and the third line carrier 10.Thus, third planet gear 13 or the rotating speed of the 3rd sun gear 7 that engages therewith are enhanced.Driven shaft 18 is served as at this 3rd sun gear 7.
In all ten embodiments, when to change planet carrier connection and gear ring and connect and the absolute value of fixed drive ratio improves 1 simultaneously, the place of associativity (Bindbarkeit) all single or multiple negative planetary gear set (Minus-Planetensatz) can be converted to positive planetary gear set in all permissions.In addition, motor or other the energy/power source can be set on each axle.Similarly, also additional epicyclic gear stage and/or cylindrical gears level can be set in the downstream of third planet gear stage.
The present invention is not limited to embodiment that is shown and that describe.Various change schemes are within the scope of the present invention possible equally, such as, by the combination of feature, even if its be illustrate in various embodiments and describe.
Reference numerals list
1. gear unit
2. first planet gear stage
3. the second epicyclic gear stage
4. third planet gear stage
5. the first sun gear
6. the second sun gear
7. the 3rd sun gear
8. the first row carrier
9. the second planet carrier
10. the third line carrier
11. first planet gears
12. second planetary pinions
13. third planet gears
14. first gear rings
15. second gear rings
16. the 3rd gear rings
17. live axles
18. driven shafts
19. first drive connection set
20. second drive connection set
21. driven connection sets
22. bridge-type connection sets
23. total connection sets
Claims (12)
1. a gear unit (1), in particular for the actuator unit (1) of wind power plant, have the third planet gear stage (4) of the first planet gear stage (2) of driving side, the second epicyclic gear stage (3) and slave end, these epicyclic gear stages have central sun gear (5 respectively; 6; 7), around the gear ring (14 of this sun gear; 15; 16) and be arranged radially between both, remain on planet carrier (8 with supporting rotationally; 9; 10) planetary pinion (11 in; 12; 13), and the device constructed rotationally with directed spin axis in the longitudinal direction being centered around described gear unit (1) is associated with one another connects, the rotating speed of the driving side of described gear unit (1) is improved at slave end, it is characterized in that, for connecting described first and second epicyclic gear stages (2; 3) device comprises driven connection set (21), and the gear ring (16) of the sun gear (6) of described second epicyclic gear stage (3) or gear ring (15) and described third planet gear stage (4) or planet carrier (10) torsionally connect by it.
2. gear unit according to claim 1, is characterized in that, described for connecting described first and second epicyclic gear stages (2; 3) device comprises at least one and drives connection set (19; 20), it is by two epicyclic gear stages (2; 3) one of them sun gear (5 in; 6) with the planet carrier (8 of another epicyclic gear stage; 9) or by described epicyclic gear stage (2; 3) two gear rings (14; 15) be torsionally coupled to each other.
3., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described for connecting described first and second epicyclic gear stages (2; 3) device comprises two driving connection sets (19; 20).
4., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described for connecting described first, second, and third epicyclic gear stage (2; 3; 4) device comprises total connection set (23).
5. any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described total connection set (23) is by the sun gear (5) of described first planet gear stage and described second or third planet gear stage (3; 4) sun gear (6; 7) and with these two epicyclic gear stages (3; 4) another the gear ring (14) in torsionally connects.
6. any one of aforementioned claim or multinomial described gear unit, it is characterized in that, the gear ring (14) of described first planet gear stage (2) torsionally connects with the sun gear (6) of described second epicyclic gear stage (3) and the planet carrier (10) of described third planet gear stage (4) by described total connection set (23).
7., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described total connection set (23) is by described first, second, and third epicyclic gear stage (2; 3; 4) gear ring (14; 15; 16) be torsionally coupled to each other.
8., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, for connecting described first and third planet gear stage (2; 4) device comprises bridge-type connection set (22), and the planet carrier (10) of the sun gear (5) of described first planet gear stage (2) with described third planet gear stage (4) torsionally connects by it.
9., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described epicyclic gear stage (2; 3; 4) so associated with one anotherly connect, that is, the torque of driving side can be assigned at least two epicyclic gear stages (2; 3; 4), especially described first planet gear stage (2) and the second epicyclic gear stage (3), and can be merged in described third planet gear stage (4).
10., any one of aforementioned claim or multinomial described gear unit, it is characterized in that, described driving connection set (19; 20) or described total connection set (23) be configured to live axle (17) at driving side or be torsionally connected with live axle (17).
11. any one of aforementioned claim or multinomial described gear unit, and it is characterized in that, described gear unit (1) has two or three devices.
12. any one of aforementioned claim or multinomial described gear unit, and it is characterized in that, described third planet gear stage (4) and cylindrical gears level are connected.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012221821.1 | 2012-11-29 | ||
| DE102012221821.1A DE102012221821A1 (en) | 2012-11-29 | 2012-11-29 | Gear unit with coupled planetary stages |
| PCT/EP2013/071229 WO2014082783A1 (en) | 2012-11-29 | 2013-10-11 | Transmission unit comprising coupled planetary gear stages |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104781584A true CN104781584A (en) | 2015-07-15 |
| CN104781584B CN104781584B (en) | 2018-01-26 |
Family
ID=49326682
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380057244.7A Expired - Fee Related CN104781584B (en) | 2012-11-29 | 2013-10-11 | Gear unit with joining epicyclic gear stage |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2926031A1 (en) |
| JP (1) | JP2015535582A (en) |
| CN (1) | CN104781584B (en) |
| DE (1) | DE102012221821A1 (en) |
| WO (1) | WO2014082783A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110788846A (en) * | 2019-11-22 | 2020-02-14 | 合肥工业大学 | Energy-saving industrial robot and time-sharing control method of driving unit of energy-saving industrial robot |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3587863A1 (en) * | 2018-06-25 | 2020-01-01 | Flender GmbH | Planetary gear, drive train, wind power plant and industry application |
| EP3599394A1 (en) * | 2018-07-23 | 2020-01-29 | Flender GmbH | Crank drive for wind power plants and industrial applications |
| EP3599393A1 (en) * | 2018-07-23 | 2020-01-29 | Flender GmbH | Crank drive for wind power plants and industrial applications |
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| SU1442755A1 (en) * | 1986-09-04 | 1988-12-07 | И.И.Литвинскнй | Planetary reduction gear |
| JPH0410152U (en) * | 1990-05-18 | 1992-01-28 | ||
| WO2001013007A1 (en) * | 1999-08-12 | 2001-02-22 | Alpha Getriebebau Gmbh | Planetary transmission |
| CN201071904Y (en) * | 2007-08-20 | 2008-06-11 | 重庆齿轮箱有限责任公司 | Differential epicyclic gear box |
| WO2010030724A1 (en) * | 2008-09-10 | 2010-03-18 | The Timken Company | Power train for wind turbine |
| CN201461259U (en) * | 2009-07-16 | 2010-05-12 | 南京高速齿轮制造有限公司 | Speed-increasing gearbox of high-power wind driven generator |
| US20110175363A1 (en) * | 2010-04-30 | 2011-07-21 | Pischel Klaus | Gearbox for a wind turbine |
| KR20120035738A (en) * | 2010-10-06 | 2012-04-16 | 부산대학교 산학협력단 | Gear train for aerogenerator |
| CN102425645A (en) * | 2011-11-03 | 2012-04-25 | 杨新胜 | Speed reducer with large speed reduction ratio |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE7805045U1 (en) * | 1978-02-20 | 1978-06-22 | A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt | Two-stage differential double planetary gear |
| DE19963597A1 (en) * | 1999-12-23 | 2001-07-26 | Mannesmann Ag | Gearboxes, in particular for wind turbines |
-
2012
- 2012-11-29 DE DE102012221821.1A patent/DE102012221821A1/en not_active Withdrawn
-
2013
- 2013-10-11 EP EP13774435.5A patent/EP2926031A1/en not_active Withdrawn
- 2013-10-11 CN CN201380057244.7A patent/CN104781584B/en not_active Expired - Fee Related
- 2013-10-11 WO PCT/EP2013/071229 patent/WO2014082783A1/en active Application Filing
- 2013-10-11 JP JP2015544387A patent/JP2015535582A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1442755A1 (en) * | 1986-09-04 | 1988-12-07 | И.И.Литвинскнй | Planetary reduction gear |
| JPH0410152U (en) * | 1990-05-18 | 1992-01-28 | ||
| WO2001013007A1 (en) * | 1999-08-12 | 2001-02-22 | Alpha Getriebebau Gmbh | Planetary transmission |
| CN201071904Y (en) * | 2007-08-20 | 2008-06-11 | 重庆齿轮箱有限责任公司 | Differential epicyclic gear box |
| WO2010030724A1 (en) * | 2008-09-10 | 2010-03-18 | The Timken Company | Power train for wind turbine |
| CN201461259U (en) * | 2009-07-16 | 2010-05-12 | 南京高速齿轮制造有限公司 | Speed-increasing gearbox of high-power wind driven generator |
| US20110175363A1 (en) * | 2010-04-30 | 2011-07-21 | Pischel Klaus | Gearbox for a wind turbine |
| KR20120035738A (en) * | 2010-10-06 | 2012-04-16 | 부산대학교 산학협력단 | Gear train for aerogenerator |
| CN102425645A (en) * | 2011-11-03 | 2012-04-25 | 杨新胜 | Speed reducer with large speed reduction ratio |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110788846A (en) * | 2019-11-22 | 2020-02-14 | 合肥工业大学 | Energy-saving industrial robot and time-sharing control method of driving unit of energy-saving industrial robot |
| CN110788846B (en) * | 2019-11-22 | 2020-12-29 | 合肥工业大学 | An energy-saving industrial robot and a time-sharing control method for its drive unit |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102012221821A1 (en) | 2014-06-05 |
| JP2015535582A (en) | 2015-12-14 |
| CN104781584B (en) | 2018-01-26 |
| EP2926031A1 (en) | 2015-10-07 |
| WO2014082783A1 (en) | 2014-06-05 |
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