CN103370536A

CN103370536A - Step-up mechanism for wind-powered generator

Info

Publication number: CN103370536A
Application number: CN2011800636007A
Authority: CN
Inventors: 原一敬; 桥本笃; 佐藤泰正; 小西敏之; 兼光雅宏; 伊奈拓郎
Original assignee: Sumitomo Heavy Industries Ltd; SEISA Gear Ltd
Current assignee: Sumitomo Heavy Industries Ltd; Sumitomo Heavy Industries Gearbox Co Ltd
Priority date: 2011-02-07
Filing date: 2011-11-21
Publication date: 2013-10-23
Anticipated expiration: 2031-11-21
Also published as: WO2012108086A1; CN103370536B; JP2012163033A; JP5676293B2

Abstract

Obtained by the present invention is a step-up mechanism for a wind-powered generator that is compact, lightweight, low-cost, and has high reliability and long life. The step-up mechanism (50) for a wind-powered generator comprises the following: a first helical pinion (helical gear) (90) that is provided in the power transmission system of the step-up mechanism (50); a second intermediate axle (92) that is assembled with the first helical pinion (90); and a buffer mechanism (110) that allows the second intermediate axle (92) to move in the axial direction when a thrust load greater than or equal to a predetermined size acts on the second intermediate axle (92).

Description

The used for wind power generation speed increaser

Technical field

The present invention relates to a kind of used for wind power generation speed increaser.

Background technique

For example in patent documentation 1, disclose such as Fig. 6～used for wind power generation speed increaser shown in Figure 8.

In Fig. 6 and Fig. 7, wind generating unit 1 has: pillar 2, and setting is arranged on the base station 6; Nacelle 3 is arranged at the upper end of pillar 2; And rotor head 4, be assembled into respect to 3 rotations of this nacelle freely.Multi-disc (in the illustrated example being 3) air vane (awe) 5 is installed on the rotor head 4.In the inside of nacelle 3, be connected with speed increaser 20 and generator 11 at rotor head 4.

If wind is to air vane 5, then rotor head 4 rotations, the rotation of this rotor head 4 with by the state transfer of speed increaser 20 speedups to generator 11.Thus, although rotor head 4(can be had torque) slow rotation speedup to 100 times about speed, and can effectively obtain generating output from generator 11.

As shown in Figure 8, described speed increaser 20 possesses planetary gears 22 elementary, and possesses parallel-

axes gears mechanism

24,26 at middle rank and rear class.Elementary planetary gears 22 mainly comprises: wheel carrier 32, and integrated with input shaft 28; Planet pin 34 is fixed in this wheel carrier 32; Planetary pinion 36 is supported on this planet pin 34 in rotation mode freely; Reach internal gear 38, sun gear 40, these planetary pinion 36 while and its engagements.In this example, sun gear 40 is integrated with the output shaft 42 of planetary gears 22, and internal gear 38 is integrated with shell 44.The parallel-axes gears mechanism 24 of middle rank and rear class, 26 adopts the parallel axes speed increasing mechanism that uses " spur gear ".Output shaft 30 links at speed increaser 20 have described generator 11.

In addition, symbol 12 shown in Figure 7 is transformer, and 13 is controller, and 14 is inverter, and 15 is the inverter cooling unit, and 16 is lubricant oil cooling apparatus.

Patent documentation

Patent documentation 1: TOHKEMY 2009-144533 communique (Fig. 6～Fig. 8)

It is about 20 years that wind power plant is designed to its service life.Therefore, also require basically to guarantee life-span about 20 years for speed increaser.

But wind power plant is the equipment that is arranged under the physical environment, therefore is subject to sometimes the attack of blast or strong wind.If this high wind puts on air vane, then cause speed increaser to become the state that is applied in huge load from input side.Therefore, each interior one of speed increaser is become fault by the state of too fast rotating speed pressure rotation reason also can occur in (even designing according to design code) sometimes.

In a single day speed increaser breaks down, and then its loss is serious, therefore needs to pay attention to guaranteeing of reliability.Usually, guarantee that most importantly the effective countermeasure of the reliability of speed increaser increases the safety coefficient (safety coefficient) of each important document when design.But if increase the safety coefficient of each important document, then natural speed increaser integral body becomes and maximizes and weight also becomes greatly, produces the problem of causing manufacture cost, construction cost increase.

The present invention finishes in order to address this is that, and its basic assignment is newfound by overcoming " middle problem (aftermentioned) " provides small-sized, lightweight, low cost and reliability is high, the life-span is long used for wind power generation speed increaser.

Summary of the invention

The present invention solves above-mentioned problem by being made as following structure, i.e. a kind of used for wind power generation speed increaser, and it possesses: spiral gear possesses the power-transmission system in this speed increaser; Axle is assembled with this spiral gear; And damping mechanism, when acting on this axle, the above thrust load of predefined size allows moving axially of this axle.

Because described middle problem of the present invention and solution principle thereof are not known content, therefore at this this centre problem and solution principle thereof that the present invention has in mind are elaborated.

If not wind moment of Chang Qiang puts on the air vane of wind power plant, then produce very strong accelerating torque with this each one at speed increaser.Yet, since the front end of speed increaser link High Rotation Speed is arranged generator as load (inertia), therefore, each important document of speed increaser can't be followed this accelerating torque moment because of inertia and be increased speed.Its result, when the rising of accelerating torque was rapid, it sharply rises accelerating torque (as on being applied to each static important document) moment all put on each parts.

The present invention with by overcome following in the middle of problem solve above-mentioned original problem and create as design.Infer the larger torque that applies continuously when to be not only high wind, produce considerable influence because of the reason larger load that moment (peak value) produces on each important document of speed increaser of above-mentioned " strong wind " etc. or the fault of impacting for the used for wind power generation speed increaser on the contrary, thereby will relax the load of this strong moment or impact conduct " middle problem " and process.

In used for wind power generation speed increaser involved in the present invention, in its drive system, be equipped with the axle that is assembled with spiral gear.In addition, the concept that comprises " helical pinion " in the concept of " spiral gear " of the present invention.

The tooth muscle of spiral gear is the spiral winding line, the axle that therefore is assembled with spiral gear when transmitting torque in the axial direction with the generation thrust load of this transmitting torque with being in proportion.Usually, the axle that is assembled with spiral gear for example bears this thrust load by " thrust-bearing ", and axle is provided the reaction force that is equivalent to thrust load and prevents that axle is mobile vertically.But, in the present invention, this transmitting torque and the relation of the thrust load that produces by this transmitting torque are used in dexterously the buffering of peak torque.That is, in the present invention, in power-transmission system, be equipped with and be assembled with the axle of spiral gear, and possess the axially movable damping mechanism of allowing this axle when the above thrust load of predefined size acts on the axle that is assembled with this spiral gear.

Rapid torque occurs and rises in moment on spiral gear if wind-force increases suddenly, then increases severely at the thrust load that axle produces with this, and its result allows that move vertically by moment for the function of axle by damping mechanism.Thus, the impacting force between the flank of tooth of the spiral gear that produces for transmitting torque moves and weakens with this axle, the suppressed amount that weakens of rapid property of the rising of the peak torque by the spiral gear transmission.

Its result can prevent effectively that strong load torque moment from putting on each important document in the speed increaser, and can prevent the frangible portion breakage etc. in the speed increaser, and can prolong the life-span of speed increaser integral body.

When used for wind power generation speed increaser involved in the present invention is assembled in and is arranged on high wind area or wind direction unstable region and is the wind power plant in the larger area of blast, especially effectively play a role.

The invention effect

A kind of small-sized, lightweight, low cost and reliability is high, the life-span is long used for wind power generation speed increaser can be provided according to the present invention.

Description of drawings

Fig. 1 is the integrally-built sectional view of used for wind power generation speed increaser of an example of expression embodiments of the present invention.

Fig. 2 is the sectional view of major component of the speed increaser of presentation graphs 1.

Fig. 3 is the summary description figure of the effect of the above-mentioned mode of execution of signal explanation.

Fig. 4 is the sectional view of the major component of the related used for wind power generation speed increaser of expression another embodiment of the present invention.

Fig. 5 is the sectional view of the major component of the related used for wind power generation speed increaser of expression another other mode of executions of the present invention.

Fig. 6 is the plan view of an integrally-built example that represented in the past the wind power plant of (and the present invention).

Fig. 7 is the stereogram of internal structure of nacelle of the wind power plant of presentation graphs 6.

Fig. 8 is the sectional view that expression is arranged at an example of the in the past used for wind power generation speed increaser in the nacelle of wind power plant of Fig. 6.

Embodiment

Below, with reference to the accompanying drawings an example of embodiments of the present invention is elaborated.

Basic structure about the wind power plant that is assembled with speed increaser involved in the present invention is identical with the structure of utilizing Fig. 6 and Fig. 7 explanation, therefore omits repeat specification, below the structure of speed increaser itself is elaborated.

Fig. 1 is the whole sectional view of used for wind power generation speed increaser 50 of an example of expression embodiments of the present invention, and Fig. 2 is the sectional view of its major component of expression.

At first, with reference to figure 1, this used for wind power generation speed increaser 50 possesses planetary gears 52 elementary, and possesses the 1st parallel-axes gears mechanism 54, the 2nd parallel-axes gears mechanism 56 at middle rank and rear class.From the rotation of the rotor head (identical with rotor head 4 in the past: with reference to figure 6 and Fig. 7) of input shaft 58 input by amounting to 3

grades gear mechanism

52,54,56 speedups, and from output shaft 60 outputs.In output shaft 60 links generator (identical with generator 11 in the past: with reference to figure 7) is arranged, and be scheduled to generating.

The present invention be applicable to be assembled with the 1st parallel-axes gears mechanism 54 wherein the 1st helical pinion (spiral gear) 90 the 2nd jack shaft 92(after describe in detail).

Described planetary gears 52 mainly comprises: wheel carrier 62, and integrated with input shaft 58; Planet pin 64 is supported at both ends in this wheel carrier 62; 3 (only illustrating 1 among Fig. 1) planetary pinions 68 are supported on this planet pin 64 in rotation mode freely; Internal gear 70, this planetary pinion 68 simultaneously with its in mesh; And

sun gear

72,68 whiles and its outer gearing of planetary pinion.

In this embodiment, sun gear 72 directly is formed at the output shaft 80 of planetary gears 52, internal gear 70 and housing 74 integrated (fixing).And the rotation that constitutes the rotor head (4) that is produced by wind-force from input shaft 58 integrated wheel carriers 62 inputs, and via the rotation of sun gear 72 after the output shaft 80 output speedups of planetary gears 52.

The output shaft 80 of planetary gears 52 is linked to the 1st jack shaft 84 by coupling 82.By key 88 links the 1st spiral gear 86 is arranged at the 1st jack shaft 84.The 1st spiral gear 86 and the 1st helical pinion (being equivalent to spiral gear involved in the present invention) 90 engagements.The 1st spiral gear 86 and the 1st helical pinion 90 consist of described the 1st parallel-axes gears mechanism 54.

The 1st helical pinion 90 vertical cuts are formed at the 2nd jack shaft 92.The 2nd spiral gear 94 is attached at the 2nd jack shaft 92 in the circumferential direction of the circle through key 96.The 2nd spiral gear 94 is clamped between the formation difference of height 90A and retaining ring 98 of the 1st helical pinion 90, and also integrated with the 2nd jack shaft 92 in the axial direction.The 2nd

spiral gear

94 and 100 engagements of the 2nd helical pinion.The 2nd helical pinion 100 vertical cuts are formed at the output shaft 60 of this speed increaser 50.The 2nd spiral gear 94 and the 2nd helical pinion 100 consist of described the 2nd parallel-axes gears mechanism 56.Output shaft 60 is supported as moving vertically by housing 74 by bearing 103,105.

In this embodiment, the 1st spiral gear 86 and the 1st helical pinion 90 are with by intermeshing and set torsional direction in the mode that the 2nd jack shaft 92 produces (helical spring 112 directions) thrust load Sa.And, constitute and make the 1st helical pinion 90 that is assembled in the 2nd jack shaft 92 identical with the torsional direction of the 2nd spiral gear 94, thereby make the direction direction opposite with described thrust load Sa of the thrust load Sb that produces by the 2nd

spiral gear

94 and 100 engagements of the 2nd helical pinion.Since thrust load Sa＞thrust load Sb, the thrust load (Sa-Sb) that therefore finally produces after synthesizing at the 2nd jack shaft 92.

Below, with reference to Fig. 1, Fig. 2 near the structure the 2nd jack shaft 92 is elaborated in the lump.

The 2nd jack shaft 92 is supported at both ends in housing 74 by a pair of the 1st radial bearing 102, the 2nd radial bearing 104 in the mode that can only move vertically.In addition, near the 2nd jack shaft 92, housing 74 constitutes at the assembled block 74B of the part of housing main body 74A formation housing 74 and inaccessible piece 74C integrated by bolt (omitting diagram: only represent center line).Be screwed with inaccessible lid 74C1 at inaccessible piece 74C.

Support described the 1st radial bearing 102 of a side of the 2nd jack shaft 92 shown in the enlarged view of Fig. 2, constitute inner ring 102B and roller 102C and can (only) slide vertically with respect to outer ring 102A.More specifically, the outer ring 102A of the 1st radial bearing 102 is fixed in shell 74 with the state between the assembled block 74B of the part of the upper jut 74A1 that forms of the main body 74A that is clamped in shell 74 and formation shell.The roller 102C of the 1st radial bearing 102 is to move axially the periphery that is embedded in inner ring 102B by the state of the jut 102B1 of inner ring 102B restriction.Inner ring 102B is pressed into and is fixed in the 2nd jack shaft 92.

The 2nd radial bearing 104 that supports the opposite side of the 2nd jack shaft 92 has basically the structure identical with the 1st radial bearing 102, and omits detailed icon, but with can make the 2nd jack shaft 92 vertically mobile mode support the 2nd jack shaft 92.

According to above structure, the 2nd jack shaft 92 can be with respect to the main body 74A of housing 74() (only) mobile vertically.And allowing and controlling the axially movable of the 2nd jack shaft 92 is damping mechanism 110.

In this embodiment, damping mechanism 110 also possesses slide plate 114 and (also have as the function of radial bearing) tapered roller bearing 116 except the function with thrust-bearing except helical spring (buffer body) 112.

Described helical spring (buffer body) 112 is with the state assembling than natural length compression, the active force that the thrust load that produces when applying with 90 rotation of the 1st helical pinion to the 2nd jack shaft 92 is resisted mutually (with the active force of the opposite direction direction of the movement of allowing the 2nd jack shaft 92: the direction power of pressing the 2nd jack shaft 92 to the left among Fig. 2).

Slide vertically in the hollow portion 74B1 that described slide plate 114 can form on the assembled block 74B of housing 74 vertically (movement).Slide plate 114 is subject to the active force of this helical spring 112 from a side (the helical spring 112 sides) 114A of this slide plate 114,114B is subject to the thrust load of the 2nd jack shaft 92 from opposite side (the 2nd jack shaft 92 sides), by this balance, be positioned the precalculated position in the hollow portion 74B1.In addition, the local 114B1 of the opposite side of this slide plate 114 can with the protuberance 74B2 butt of assembled block 74B.Therefore, constitute when from the thrust load of the 2nd jack shaft 92 (being the right load among Fig. 2) during less than predetermined value So, even the active force specific thrust load of helical spring 112 is strong, slide plate 114 also can't be than this protuberance 74B2 more to the 2nd jack shaft 92 side shiftings.Thus, the thrust load that produces at the 2nd jack shaft 92 is during less than predetermined value So, the 2nd jack shaft 92 only is subject to the reaction force that equates with this thrust load from slide plate 114 sides via tapered roller bearing 116, therefore the larger stress more than the thrust load that produces of the transmission of the rotating torques by the 2nd jack shaft 92 can't result from the 2nd jack shaft 92.

Described tapered roller bearing 116 is configured between the 92A of difference of height section of slide plate 114 and the 2nd jack shaft 92, thereby has the function as " thrust-bearing " that the thrust load of the 2nd jack shaft 92 is passed to slide plate 114.Namely, in this embodiment, born nearly all radially torque of helical spring 112 sides of the 2nd jack shaft 92 by the 1st radial bearing 102, therefore this tapered roller bearing 116 has the function (particularly, adopting the periphery of tapered roller bearing 116 that idle design is slightly arranged) as radial bearing hardly.In this sense, tapered roller bearing 116 can replace to special bearing thrust load " thrust-bearing ".Structurally, for example can also be made as the metal bearing with rolling element.Such as this mode of execution, consist of with different bearings respectively if will bear the tapered roller bearing 116 of the 1st radial bearing 102 of radial load and bearing thrust load, then make the 2nd jack shaft 92(can not produce the axle runout) " only " excellent on the mobile this point vertically.But, in the present invention, be not to forbid being made as following structure, namely for example (replace the 1st radial bearing 102 and tapered roller bearing 116) and assemble the single bearing that bears radial load and thrust load both sides.

Then the effect of the related used for wind power generation speed increaser 50 of this mode of execution described.

The rotation of air vane (5) is delivered to the input shaft 58 of speed increaser 50.The rotation of input shaft 58 is input to planetary gears 52 via wheel carrier 62 as the revolution of planetary pinion 68, by this relative rotation of planetary pinion 68, internal gear 70, sun gear 72, the rotation of speedup output shaft 80 outputs of 52 from sun gear 72 to planetary gears.

The rotation of the output shaft 80 of planetary gears 52 is delivered to the 1st jack shaft 84 of the 1st parallel-axes gears mechanism 54 via coupling 82, be delivered to the 1st spiral gear 86 via key 88.The rotation of the 1st spiral gear 86 is delivered to the 1st helical pinion 90, thus the 2nd jack shaft 92 rotations.

Shown in the schematic diagram of Fig. 3, if a certain input torque T is from input shaft 58 inputs now, then by the 1st

spiral gear

86 and 90 engagements of the 1st helical pinion of the 1st parallel-axes gears mechanism 54, produce (helical spring 112 directions) thrust load Sa at the 2nd jack shaft 92.And, in this embodiment, the torsional direction that is assembled in the 1st helical pinion 90 of the 2nd jack shaft 92 and the 2nd helical pinion 94 is made as identical, cancels out each other thereby constitute the thrust load Sb and the described thrust load Sa that produce by the 2nd

spiral gear

94 and 100 engagements of the 2nd helical pinion.Its result, thrust load Sa＞thrust load Sb if therefore from input shaft 58 inputs input torque T is arranged on the 2nd jack shaft 92, then produces the thrust load (Sa-Sb) after synthesizing.

Act on the thrust load (Sa-Sb) of the 2nd jack shaft 92 with increase and decrease interlock and the ratio increase and decrease of input torque T.If input torque T is during for (can not become problem on the intensity) smaller T1, the thrust load that produces (Sa1-Sb1) is also less than predetermined value So, large (the So＜Fc) of the directed force F c side of helical spring 112, therefore as shown in Figure 2, slide plate 114 becomes the state with the protuberance 74B2 butt of assembled block 74B.Therefore, the 2nd jack shaft 92 bears thrust counterforce with the thrust load that produces (Sa-Sb) equal sizes via tapered roller bearing 116 all the time, and its result keeps not mobile vertically state.

Effect when being common so far.

But, if input torque T becomes suddenly larger T2 because of strong wind etc., the thrust load that produces (Sa2-Sb2) surpasses predetermined value So, overcome the directed force F c(So of helical spring 112 〉=Fc), then helical spring 112 is compressed, its result, slide plate 114 moves to till the position of the directed force F c' that increased and thrust load (Sa2-Sb2) balance along helical spring 112 directions.

Its result, performance as following effect.

That is, the output shaft 60 at speed increaser 50 is connected with the larger generator of inertia (11).Therefore, if (not being made as the structure such as present embodiment) is even from this torque T2 that increases suddenly of input shaft 58 inputs, the rotating speed of output shaft 60 can not accelerated suddenly thereupon yet, so each important document of speed increaser 50 is had to just like the mode of accepting at the state that stops is accepted the torque that this moment increases.

Yet, in this embodiment, if producing this rapid torque, (referring again to Fig. 3 describes) increase, then as previously mentioned the 2nd jack shaft 92 itself vertically to helical spring 112 side shiftings, thereby flank of tooth 90A moment of the 1st helical pinion 90 is moved (with reference to dotted line: in fact can not separate) towards the direction away from the flank of tooth 86A of the 1st spiral gear 86, therefore weakens the rapid rising of transmitting torque.Change the speech and it, should be delivered to speed increaser 50 the downstream side torque a part as the compression damping mechanism 110 helical spring (buffer body) 112 energy and consume.

On the other hand, in the engaging piece of the 2nd spiral gear 94 and the 2nd helical pinion 100, the 2nd spiral gear 94 is driven for driving the 2nd helical pinion 100, therefore 92 moments of the 2nd jack shaft move to helical spring 112 sides, thereby still obtain weakening the effect of the rapid rising of transmitting torque, suppress thus to be delivered to from the 2nd jack shaft 92 generation of the peak torque of output shaft 60.That is, the 2nd jack shaft 92 moves axially along (direction of helical spring 112), thereby can effectively reduce moment at the load (peak torque) of each generation of speed increaser 50 by the utmost point.

The structure that present embodiment is related when continuing (continuously) input stronger torque is arranged from input shaft 58 sides, can't reduce the torque that this continues input, but the frequent generation situation of bearing stronger load because of the reason such as strong wind moment of wind power plant.Therefore, the effect of rising of peak torque that can suppress this moment property is very big, and life is made larger contribution.

The present invention can consider various changes.

For example, in the above-described embodiment, adopted and used helical spring 112 as the device of damping mechanism, as long as become predefined size when above but damping mechanism involved in the present invention acts on the thrust load of the axle that is assembled with spiral gear, allow that moving axially of this axle gets final product, and can adopt various structures.For example, as shown in Figure 4, can also use belleville spring 150 as buffer body.In addition, in this example, the shape that thereupon compares inaccessible piece 74D and inaccessible lid 74D1 with before mode of execution changes slightly.In addition, when adopting buffer body such as " spring system " of helical spring 112 or belleville spring 150 as the sort buffer body, be configured to array if for example a plurality of springs that spring constant is different directly (or be clipped in the middle slide plate), then can become the wider design of useable width (when applying the peak torque of which kind of degree, moving it (slip) which kind of degree) that makes with respect to peak torque.Another structure is identical with before mode of execution, so among the figure position identical on identical or the function is composed and add identical symbol.

And, for example as shown in Figure 5, also can consist of damping mechanism (also can be the pneumatic cylinder body mechanism) by oil pressure (hydraulic pressure) cylinder mechanism 160, described oil pressure (hydraulic pressure) cylinder mechanism possesses: the 74E1 of cylinder body section consists of in inaccessible piece 74E; And piston 156, can in the 74E1 of this cylinder body section, slide, and integrated with slide plate 114.At this moment, appropriate combination switching valve 162 or flow controller 164 etc., thus can set up the oil pressure circuit that can more critically adjust the mobile moment that begins or shift motion etc.In addition, the description of Fig. 5 is that the utmost point has represented this situation and not in full accord with actual oil pressure circuit simply.

In addition, in the above-described embodiment, adopted and allowed with respect to the 2nd jack shaft 92 axially movable structures, but as narrate, allow that in the present invention axially movable axle is not limited to this example, for example, with regard to the structure of above-mentioned mode of execution, also can constitute and make the 1st jack shaft or output shaft mobile vertically.And, also can constitute and make a plurality of axles (for example the 1st jack shaft and the 2nd jack shaft, the 2nd jack shaft and output shaft, the 1st jack shaft and output shaft or the 1st jack shaft and the 2nd jack shaft and output shaft are whole) mobile vertically.Constitute when a plurality of axles are moved, for example, change (staggering) each axle and begin mobile threshold value, thereby can enlarge the target zone of the peak torque that wish will suppress.

And, in the above-described embodiment, only obtain the assimilation effect of thrust load with respect to the single-way moving of the 2nd jack shaft 92, but for example also can be in the identical structure of the two ends of 1 axle assembling (or constitute can in the two-way thrust of one-sided absorption), thereby can be at the assimilation effect of two-way performance thrust load.Namely in the speed increaser of wind power plant, (usually make the nose cone of nacelle towards the driftage control of the direction of facining the wind, therefore) air vane seldom carries out contrary rotation.But, even air vane is towards equidirectional rotation (sense of rotation of the input shaft of speed increaser is identical), when slowing down (when slowing down especially suddenly) opposing torque plays a role by the inertia of generator.At this moment, driving the direction that produces thrust load with driven relation reverse also becomes in the other direction.At this moment, the impact that exists (so big even the absolute value of the opposing torque that produces itself does not have) to be reversed by sideshake and produce can have influence on the life-span.Make the axle can reverse movement and can cushion this impact by being made as in advance.

In addition, in the present invention, at the power-transmission system of speed increaser 50 configuration spiral gear, and ingenious utilization reduces peak torque because of the thrust load that the engagement of this spiral gear produces.Wherein, as the gear that produces thrust load because of engagement, except spiral gear, also have such as bevel gear or hypoid gear etc.But if wherein a side axle is mobile vertically for these gears, then " toe joint touches " itself becomes greatly different, therefore not preferred.But so long as possess the axle that is assembled with spiral gear at power-transmission system, then the structure of speed increasing mechanism itself is not limited to above-mentioned mode of execution, also can be any structure.

Utilizability on the industry

The present invention can be used in the speed increaser of wind power plant.

The full content of specification, accompanying drawing and claims of the Japanese publication 2011-023560 of application on February 7th, 2011 is applied in this specification by reference.

The explanation of symbol:

The 1-wind power plant, 3-nacelle, 4-rotor head, the 5-air vane, the 11-generator, 50-speed increaser, 52-planetary gears, 54-the 1st parallel-axes gears mechanism, 56-the 2nd parallel-axes gears mechanism, 58-input shaft, 60-output shaft, 86-the 1st spiral gear, 90-the 1st helical pinion (spiral gear), 92-the 2nd jack shaft (axle), 94-the 2nd spiral gear, 100-the 2nd helical pinion, 102,104-the 1st, the 2nd radial bearing, 110-damping mechanism, 112-helical spring (buffer body), the 114-slide plate, the 116-tapered roller bearing.

Claims

1. used for wind power generation speed increaser is characterized in that possessing:

Spiral gear possesses in the power-transmission system of this speed increaser;

Axle is assembled with this spiral gear; And

Damping mechanism is allowed moving axially of this axle when the thrust load that this axle effect had more than the predefined size.

2. used for wind power generation speed increaser according to claim 1 is characterized in that,

Described damping mechanism constitute by spring to described axle apply to the active force of the direction of the opposite direction of allowing described movement.

3. used for wind power generation speed increaser according to claim 1 is characterized in that,

Described damping mechanism constitute by the oil hydraulic cylinder with flow controller or pneumatic cylinder to described axle apply to the active force of the direction of the opposite direction of allowing described movement.

4. each described used for wind power generation speed increaser is characterized in that according to claim 1～3,

Described damping mechanism possesses:

Slide plate can be along the thrust load that moves axially and bear described axle of described axle; And

Thrust-bearing is disposed between this slide plate and the described axle, and the thrust load of this axle is passed to described slide plate.

5. used for wind power generation speed increaser according to claim 4 is characterized in that,

Described thrust-bearing is tapered roller bearing, and

Except this tapered roller bearing, described used for wind power generation speed increaser also possesses a pair of radial bearing, and the inner ring of this a pair of radial bearing itself and rolling element can be together mobile vertically with described axle.