CN105008715B - It is used in the deceleration device of wind power plant - Google Patents

Abstract

The present invention provides the deceleration device (G1~G4) that one kind is used in wind power plant (10),Wherein,A part as power-transmission system,Possesses the hollow shaft (66) of hollow structure,The interior bonds of the hollow shaft (66) have the connection shaft i.e. power transmission member (70) towards next stage,The one end (66A) of the hollow structure of the hollow shaft (60) can expose from preceding-stage side shell (45),Linking part (70) is set to compared with the miscellaneous part for forming power-transmission system easily produce the frangible portion of specific change during in passing power,And,The connection shaft (70) is set to that the connecting shaft (70) can be taken out outside from the one end (66A) of hollow shaft (66) to preceding-stage side shell (45) in the state of the deceleration device (G1) is assemblied in wind power plant (10) in itself.Thus, obtain more easily carrying out the deceleration device for being used in wind power plant of attended operation in narrow nacelle.

Description

It is used in the deceleration device of wind power plant

Technical field

The present invention relates to a kind of deceleration device for being used in wind power plant.

Background technology

There is the deceleration device for being used in wind power plant disclosed in patent document 1.

Have as the deceleration device for being used in wind power plant：For the nacelle (hair for the topmost for making to be arranged on pillar Electric room) driftage (Yaw) driving deceleration device for rotating in the horizontal plane, or the pitch of the angle for changing air vane (Pitch) driving deceleration device etc..

The nacelle of wind power plant only ensures there is very narrow space positioned at position very high from the ground.Separately On the one hand, each deceleration device for being used in wind power plant is respectively provided with sizable weight.Therefore, move into nacelle or Operation after moving into etc. is fairly cumbersome.

Therefore, have disclosed in patent document 1 and be set to be separated into comprising orthogonal gear mechanism by the shell of deceleration device High-speed side shell body and low speed side shell body comprising final reduction mechanism, and respective lubricating oil is enclosed into each shell body Structure.Thereby, it is possible to further improve the operability of deceleration device.

Conventional art document

Patent document

Patent document 1：Japanese Unexamined Patent Publication 2011-231749 publications (Fig. 2~Fig. 4)

The summary of invention

The invention technical task to be solved

However, the equipment under natural environment is disposed on due to wind power plant, sometimes by blast or stronger Strong wind.In this condition, can produce " power backflow phenomena " that huge wind load inputs from the outlet side of deceleration device. Therefore, deceleration device etc. sometimes in very severe state, also needing to be safeguarded sometimes.

According to the technology disclosed in patent document 1, because shell can be divided into high-speed side shell body and low speed side shell body, because This only can separate (dismounting) high-speed side shell body and safeguarded in the state of low speed side shell body is assemblied in nacelle.But It is actually nonetheless, to operate also not light.

The present invention in order to solve the problems, such as it is this completed in the past, its problem be to provide it is a kind of can be narrow The deceleration device for being used in wind power plant of attended operation is more easily carried out in nacelle.

For solving the means of technical task

The present invention solves above-mentioned problem, a kind of deceleration dress for being used in wind power plant by being arranged to following structure Put, wherein, the part as power-transmission system possesses the hollow shaft of hollow structure, has court in the interior bonds of the hollow shaft To the power transmission member of next stage, the one end of the hollow structure of the hollow shaft can expose from shell, the power Transferring element easily produces the crisp of specific change when being set to compared with the miscellaneous part for forming power-transmission system in passing power Weak portion, also, the power transmission member be set to can in the state of the deceleration device is assemblied in wind power plant in itself from The one end of the hollow shaft takes out the power transmission member to outside shell.

In the present invention, possesses the hollow shaft of hollow structure as the axle for forming power-transmission system.Also, in the hollow shaft Interior bonds have power transmission member towards next stage.Compared with forming the miscellaneous part of power-transmission system, power passes Pass part and be specially set to frangible portion, if being in the presence of sternness in power transmission, make the power transfering part of the composition frangible portion Part produces specific change.

On the other hand, the one end of the hollow structure of hollow shaft can expose from shell.Also, produced in power transmission member , can be in the state of deceleration device be assemblied in wind power plant in itself from described one end of hollow shaft after having given birth to the specific change The power transmission member is taken out to outside shell in portion.Therefore, very comfortable is safeguarded.

Invention effect

In accordance with the invention it is possible to obtain a kind of use that attended operation can be more easily carried out in narrow nacelle In the deceleration device of wind power plant.

Brief description of the drawings

Fig. 1 is the entirety of the deceleration device for being used in wind power plant involved by one of embodiments of the present invention Sectional view.

Fig. 2 is Fig. 1 major part amplification view.

Exploded view when Fig. 3 is the taking-up power transmission member of Fig. 1 above-mentioned deceleration device.

Fig. 4 is the stereogram for showing schematically the state that above-mentioned deceleration device is assembled with above-mentioned wind power plant.

Fig. 5 is the sectional view of the deceleration device equivalent to Fig. 1 involved by one of another embodiment of the present invention.

Fig. 6 is Fig. 5 major part amplification view.

Fig. 7 is the major part amplification view equivalent to Fig. 2 involved by one of another embodiment of the invention.

Exploded view when Fig. 8 is the taking-up power transmission member of Fig. 7 deceleration device.

Embodiment

Hereinafter, refer to the attached drawing is to the deceleration for being used in wind power plant involved by one of embodiments of the present invention The structure of device is described in detail.

In present embodiment, the present invention fills suitable for the deceleration used the yaw drive system of wind power plant Put.Explanation is proceeded by from the overall schematic configuration of wind power plant.

With reference to figure 4, the wind power plant 10 has in the topmost of cylinder pillar (main body of wind power plant 10) 11 Standby nacelle (power compartment) 12.The over-assemble of nacelle 12 has driftage (Yaw) drive system 14 and pitch (Pitch) drive system 16.Partially Drive system 14 of navigating controls angle of revolution of the nacelle 12 relative to cylinder pillar 11.The control of pitch drive system 16 is installed on radome fairing The propeller pitch angle of 18 3 air vanes 20.

Yaw drive system 14 possess 4 with motor 22 and deceleration device G1~G4 of output pinion 24 and 1 with (swiveling gear 28 is interior to be inscribed for output pinion 24 in this example embodiment for the swiveling gear 28 that each output pinion 24 engages Gear is but it is also possible to be for the external external gear of output pinion 24).Each deceleration device G1~G4 is via (the reference chart of bolt 29 1) it is individually fixed in the structure 12A of nacelle 12 precalculated position.

According to the structure, if making each output pinion 24 simultaneously by being attached to each deceleration device G1~G4 motor 22 Rotate, then the output pinion 24 (refers to while being engaged with swiveling gear 28 relative to the center 36 of the swiveling gear 28 Fig. 4) revolved round the sun.As a result, nacelle 12 can be made to be relatively moved relative to the swiveling gear 28 for being fixed on cylinder pillar 11, and And by reaction, it can make nacelle 12 is overall to be turned round around the center 36 for the swiveling gear 28 for being fixed on cylinder pillar 11.Thus, Radome fairing 18 can be made towards desired direction (such as direction windward), and can effectively bear blast.

Because deceleration device G1~G4 of the yaw drive system 14 is respectively provided with identical structure, therefore at this to slowing down Device G1 is illustrated.

Fig. 1 is the yaw drive system 14 for being used in wind power plant involved by one of embodiments of the present invention Deceleration device G1 entirety sectional view, Fig. 2 is Fig. 1 major part amplification view.

It is parallel that deceleration device G1 is configured with motor 22, orthogonal gear reducing gear the 40, the 1st successively in power transfer path The planetary gear reducing mechanism 44 of axle reducing gear 41, the 2nd parallel axle speed reducing machine structure 42 and eccentric oscillating-type.Wherein, positive interlocking tooth Wheel reducing gear 40, the 1st parallel axle speed reducing machine structure 41, the 2nd parallel axle speed reducing machine structure 42 are contained in preceding-stage side shell 45.

In present embodiment, preceding-stage side shell 45 possesses the side cover 45A as motor cover, preceding-stage side housing main body 45B, lid The body 45C and relaying shell 45D as the bridge between rear-stage side shell 48, and be integrally formed by bolt 43.Preceding-stage side The inner space P1 of shell 45 is sealed by oil sealing (seal member) 71A~71C, and inner space P1 is sealed with lubricant.

The motor drive shaft 46 of motor 22 double as orthogonal gear reducing gear 40 input shaft, front end in a manner of vertical cut formed with Hypoid pinion 47.In addition, possessing brake apparatus in the end of the side opposite with load of the motor drive shaft 46 (saves sketch map Show).

Orthogonal gear reducing gear 40 possesses hypoid pinion 47 and hypoid gear 50.1st parallel axes slows down Mechanism 41 possesses spur pinion 54 and spur gear 56.2nd parallel axle speed reducing machine structure 42 possesses spur pinion 60 and spur gear 64.Just Gear 64 is fixed on the hollow shaft (output shaft of the 2nd parallel axle speed reducing machine structure 42) 66 of hollow structure.

In this way, the power-transmission system of the embodiment possesses the hollow shaft 66 of hollow structure in one part.Also, The interior bonds of the hollow shaft 66 have the connection shaft (power transmission member) 70 towards next stage.

For the structure near hollow shaft 66 and connection shaft 70, hereafter it is described in detail, herein first to configuring in hollow shaft 66 and the planetary gear reducing mechanism 44 of eccentric oscillating-type of rear class of connection shaft 70 illustrate.

Planetary gear reducing mechanism 44 is the Eccentrically rocking type reduction gear structure of so-called centre-crank formula, and it possesses：Via The input shaft 73 that connection ring part 79 links with connection shaft (power transmission member) 70；Turn into one via key 75 and the input shaft 73 2 eccentric bodies 74 of body；It is assembled in the periphery of the eccentric body 74 and 2 external gears 76 swung by the eccentric body 74； And the external gear 76 swing while internal messing internal gear 78.

In addition, planetary gear reducing mechanism 44 is contained in rear-stage side shell 48.Rear-stage side shell 48 is mainly by the 1st shell body 48A, the 2nd shell body 48B, load reverse side cover body 48C and load-side cover body 48D are formed, and are fixed on nacelle via bolt 29 12 structure 12A.The inner space P2 of rear-stage side shell 48 is sealed by oil sealing (seal member) 71D, 71E, and inside this Space P2 is sealed with lubricant.

The internal gear 78 includes：The internal tooth wheel body 78A that is integrally formed with the 1st shell body 48A therein, rotate freely Ground is held in the internal tooth wheel body 78A and plays the cylindric export trade 78B of the effect of internal tooth.The internal tooth quantity of internal gear 78 (export trade 78B quantity) is slightly more (in the example only more 1) than the external tooth quantity of external gear 76.

Multiple (being 12 in the example) domestic 80 together run through external gear with sliding promoting member 81 on same circumference 76.Domestic 80 are integrally formed with output flange (wheel carrier) 82, and the output shaft 84 of the output flange 82 and deceleration device G1 turns into one Body.

Supported in addition, each domestic 80 each end is pressed plate 86, pressing plate 86 is across very small gap and with bearing The end difference 48C1 for carrying opposite side cover body 48C is opposed so that only when the pressing plate 86 is by stronger radial load with the rank Terraced portion 48C1 contacts.

Output shaft 84 is assembled in the self-aligning roller bearing 85 of the 2nd shell body 48B inner circumferential and is configured at the 1st shell The roller 83 of body 48A inner circumferential supports.The export trade 78B arranged coaxials of roller 83 and internal gear 78, pass through supporting and output The output flange 82 that axle 84 is integrally formed, rotatably support one end of output shaft 84.

Be linked with above-mentioned output pinion 24 through spline 87 on output shaft 84, the output pinion 24 be set to it is stated that Swiveling gear 28 (Fig. 4) engagement structure.

Here, it is the hollow shaft 66 to the output shaft of the 2nd parallel axle speed reducing machine structure 42 and is linked to the hollow shaft 66 Structure near the internal connection shaft 70 illustrates.

In the lump with reference to figure 2, the one end 66A that hollow shaft 66 is set to hollow structure can expose from preceding-stage side shell 45.Tool For body, hollow shaft 66 be set to axially through hollow bulb 66C hollow structure.Hollow shaft 66 is through a pair of ball sealer axles Hold 88,90 and be rotatably freely supported on preceding-stage side shell 45, than one seal ball bearing 88 of one end 66A of the hollow structure is more To axially external extension.As a result, the one end 66A of hollow shaft 66 can expose outside to preceding-stage side shell 45.

In addition, in the embodiment, the actually one end 66A of the hollow shaft 66 is by dust-proof with the transparent envelope of cover 67 Firmly.But it is possible to simply dismantle the cover 67 by laying down bolt 68, one end 66A can easily expose.And And on " can expose ", without making one end 66A be protruded more laterally than shell side, one end 66A can also be located at than The position of shell side more in the inner part.

There is the connection shaft (power transmission member) 70 towards next stage in the interior bonds of hollow shaft 66.

Specifically, connection shaft 70 possesses the 1st linking part 70A linked with hollow shaft 66 at one end near portion 66A, and The connecting shaft 70 is linked to the inside of hollow shaft 66 at the 1st linking part 70A.In present embodiment, the 1st linking part 70A warps The one end 66A of hollow shaft 66 inner side is arranged at by bushing 63.Also, connection shaft 70 is from the other end of the hollow shaft 66 The part that 66B is protruded is the eccentric oscillating-type planetary gear reducing gear 44 via the part of connection ring part 79 and next stage Input shaft 73 link.

First, the structure from the inside that connection shaft 70 is linked to hollow shaft 66 proceeds by detailed description.

In the embodiment, not connection shaft 70 and hollow shaft 66 itself are directly linked, but make bushing 63 between two Between person.That is, in present embodiment, possesses the bushing 63 engaged in a rotational direction with the inner circumferential of hollow shaft 66 via key 69 (cartridge), connection shaft 70 with the bushing 63 by linking to be linked to the inside of hollow shaft 66.Specifically, connection shaft 70 It is integrally formed as the single component A1 comprising back-up ring 77 with bushing 63, and is engaged by key 69 with hollow shaft 66.That is, serve as a contrast Set 63 and the link of hollow shaft 66 are to make use of " the gap cooperation " of key 69.

On the other hand, the company between the 1st linking part 70A of connection shaft 70 and (being integrally formed with hollow shaft 66) bushing 63 Knot is carried out by " interference fit ".Interference fit is realized by press-in or shrink fit.The interference fit is that the 1st links Portion 70A by more than the 1st predetermined value S1 torque when, in the range of elastic deformation, between connection shaft 70 and hollow shaft 66 Produce the relative interference fit slided.

1st predetermined value S1 is set to will be greater than the nominal torque equivalent load of motor 22 and is less than the pre- of the scope of extreme value load Fixed load is converted into the value of the load of the 1st linking part 70A parts.The motor 22 that nominal torque equivalent load represents connected is defeated The load of output shaft 84 is put on when going out nominal torque.Extreme value load refers in service life (in the deceleration of wind power plant It is 20 years in the case of device) during, 1 load that will not be also destroyed only is applied to output shaft 84.Extreme value load is in this reality 2 times that (although scope is slightly wide) is slightly larger than rated output torque equivalent load are applied in mode.

In the embodiment, the 1st linking part 70A of connection shaft 70 is involved in the present invention " with forming power conveying system The miscellaneous part of system compares the frangible portion that specific change is easily produced in passing power ".Wherein, " specific change " refers to " dynamic This by more than given torque during the torque of (being more than the 1st predetermined value S1 in the example), can not being subject to by force transmission member The change that torque is directly transmitted ".In the embodiment, it is interference fitted due to using, therefore, if connection shaft 70 is predetermined by the 1st More than value S1 torque, then " relative to slide " can be produced in the 1st linking part 70A, the torque will be unable to directly transmit.Therefore, should " relative slide " equivalent to specific change, being configured to (compared with the miscellaneous part of power-transmission system), easily to produce this relative The 1st linking part 70A slided is equivalent to " frangible portion ".Conversely, the 1st linking part 70A due to connection shaft 70 can also be regarded as Form " frangible portion " involved in the present invention, therefore connection shaft 70 becomes easily to produce specific change (with sky in passing power The relative slip of mandrel 66).

In addition, in present embodiment, possessing can be from the caused detection of the external detection specific change (relative to slide) Mechanism D1.Specifically, the end face 63A for the bushing 63 being integrally formed with hollow shaft 66 and the end face 70D of connection shaft 70 substantially match somebody with somebody Put in same plane, testing agency D1 is (continuous by such as red-label radially described across two end faces 63A, 70D Mark) form and (or line can also be marked with the sharp object in front end or thinner copper cash etc. is across two end faces 63A、70D).Due to that can observe to obtain the mark via transparent cover 67, if thus hollow shaft 66 (bushing 63) with Specific change (relative to slide) is produced between connection shaft 70, and then the mark will misplace, and can obtain producing the spy from external observation Situation about changing surely.

Then, to the part of connection shaft 70 and next stage it is link between the input shaft 73 of planetary gear reducing mechanism 44 Structure illustrates.

Connection shaft 70 possesses the 2nd linking part 70B in the end of the part of the other end 66B protrusions from hollow shaft 66, should Connection shaft 70 links via the input shaft 73 that the 2nd linking part 70B and next stage part are planetary gear reducing mechanism 44.Tool For body, the link is carried out via connection ring part 79.Connection ring part 79 possesses internal spline 79A.2nd linking part 70B possesses External splines 70B1, and engage with a part of 79A1 of the side of hollow shaft 66 in the internal spline 79A of connection ring part 79 axial direction.Separately On the one hand, the end of the input shaft 73 of the eccentric oscillating-type planetary gear reducing gear 44 of next stage, should formed with external splines 73A The external splines 73A of input shaft 73 is another with side opposite with hollow shaft 66 in the internal spline 79A of connection ring part 79 axial direction A part of 79A2 engagings.Therefore, in the embodiment, power directly links via connection ring part 79 the 2nd of connection shaft 70 the Transmitted between portion 70B and input shaft 73.That is, it is not set to " frangible portion ".

In addition, the axial length of connection ring part 79 is set to longer, to be wrapped by hollow shaft 66 and connection ring part 79 Enclose the overall length of connection shaft 70.

In addition, in present embodiment, (linking with hollow shaft 66) the 1st linking part 70A of connection shaft 70 external diameter is d1, (linking with next stage part) the 2nd linking part 70B external diameter is d2.Also, with the linking part of the link of hollow shaft 66 and with A diameter of d3 of pars intermedia 70C between the linking part that one-level links, and d2 ＞ d1 ＞ d3.That is, the 1st linking part 70A and the 2nd connects Pars intermedia 70C between knot 70B is set to the small diameter d3 of outside diameter d 1 than each linking part 70A, 70B, d2.

Also, the space P3 in the hollow bulb 66C of hollow shaft 66 is subtracted by oil sealing 71B, 71C (seal member) with this The space P1 isolation of inclosure lubricant in speed variator G1 preceding-stage side shell 45.That is, in present embodiment, hollow shaft 66 runs through Preceding-stage side shell 45.Oil sealing 71B, 71C, the sky of the preceding-stage side shell 45 are configured between hollow shaft 66 and preceding-stage side shell 45 Between lubricant in P1 cannot be introduced into the space P3 in hollow shaft 66.Also, rear-stage side shell 48 is also configured to, in itself and pressure Enter from rear-stage side shell 48 protrude input shaft 73 periphery bushing 72 between be configured with oil sealing 71D, rear-stage side shell 48 The space P4 that interior lubricant cannot be introduced into connection ring part 79.As a result, the space P3 and connection ring part in hollow shaft 66 Space P4 in 79 is completely isolated by oil sealing 71B, 71C, 71D and deceleration device G1 space P1, P2 for being sealed with lubricant, Deceleration device G1 lubricant will not be adhered on connection shaft 70.

In addition, in the embodiment, the axial dimension of hollow shaft 66 is L1.On the other hand, connection shaft 70 and hollow shaft 66 One end 66A nearby link, and be from the part of the other end 66B of the hollow shaft 66 protrusion and the part of next stage The input shaft 73 of planetary gear reducing mechanism 44 links.Therefore, the overall length L2 of connection shaft 70 is considerably long.Also, as described above, even Tie axle 70 the 1st linking part 70A and the 2nd linking part 70B between pars intermedia 70C outside diameter d 3 be set to than each linking part 70A, 70B outside diameter d 1, d2 are small.

Why connection shaft 70 is set to this structure, be in order that the connection shaft 70 when meeting predetermined condition to rotation side To the predetermined torsional deformation amount of only torsional deformation (rotation angular phase difference).

Because the structure is not known, thus slightly describe in detail.

Connection shaft 70 involved by the embodiment turns into the load for acting on output pinion 24 to be less than and the described 1st During more than the 2nd predetermined value S2 of load corresponding predetermined value S1, to direction of rotation torsional deformation and each deceleration device G1~G4 In output pinion 24 relative to respective " difference of sideshake " of swiveling gear 28 suitable predetermined angular more than.

Here, " acting on the load of output pinion 24 turns into the less than the load corresponding with the 1st predetermined value S1 the 2nd During more than predetermined value S2 " " the 2nd predetermined value S2 " by consider " when being applied with stronger wind load, in the 1st linking part 70A Produce the stage before specific change (relative slide), equably bearing load avoids load from only collecting by making each deceleration device In on specific deceleration device." this point and determine.

Specifically, the nominal torque equivalent load of output pinion 24 is put on when motor 22 exports nominal torque to be turned into 1 index.In addition, the 2nd predetermined value S2 can also be relatively low, but if being set to begin to produce torsional deformation from too low grade, Response when being then not only driven by motor 22 is deteriorated, and is difficult to ensure that necessary intensity, therefore when motor 22 exports The value that output pinion 24 is put on during the torque of fatigue-equivalent load (half of nominal torque of motor or so) is actually several Turn into lower limit.

In addition, for " difference of sideshake ", it is generally desirable to which the sideshake between swiveling gear 28 and output pinion 24 is most The difference of the sideshake amount of the deceleration device of the sideshake amount of small deceleration device and sideshake maximum.More specifically, it is that " nacelle 12 is logical Cross wind load to be rotated, until with maximum side after thus the sideshake of the minimum deceleration device of sideshake blocks and (turns into 0) Untill the sideshake of the deceleration device of gap disappears, there is the angle that the output pinion 24 of the deceleration device of the maximum sideshake is rotated Degree ".

But because the connection shaft 70 of the minimum deceleration device of sideshake distorts, therefore when the small deceleration device of sideshake second Output pinion 24 when being engaged with swiveling gear 28, only this can obtain based on 2 deceleration devices etc. distribution effects, and And because the connection shaft 70 of 2 deceleration devices distorts, thus when the output pinion 24 and rotary teeth of next deceleration device During the engagement of wheel 28, it the distribution effects such as can further obtain.Consequently, it is possible to " difference of sideshake " can be interpreted as any 2 after all The difference of sideshake in platform deceleration device.

In addition, and sideshake difference " suitable angle " refer to according to turn into object connection shaft 70 on power-transmission system Position and be multiplied by speed reducing ratio (being speed increasing ratio when from output pinion) amount angle.For example, from defeated in the embodiment The speed increasing ratio for going out the planetary gear reducing mechanism 44 when little gear 24 is observed is 43, therefore as the angle after 43 times.

In addition, the formation in Fig. 1~Fig. 3 is when connection shaft 70 is difficult to extract in the end face 70D of connection shaft 70 screw 70T When, the part that is screwed togather for the screw of extraction fixture.

Then, the effect to deceleration device G1 illustrates.

With reference to figure 1, the rotation of the motor drive shaft 46 of motor 22 passes through the hypoid pinion of orthogonal gear reducing gear 40 47 and hypoid gear 50 engagement slowed down by primary after, slow down via the 1st parallel axle speed reducing machine structure 41 and the 2nd parallel axes Mechanism 42 is transferred to hollow shaft 66.

The rotation of hollow shaft 66 is transferred to the input shaft of eccentric oscillating-type planetary gear reducing gear 44 via connection shaft 70 73.Effect for the part, is described in detail afterwards.

If the input shaft 73 of eccentric oscillating-type planetary gear reducing gear 44 rotates, external gear 76 is (in internal gear 78 While connecing) via the swing rotary of eccentric body 74.As a result, input shaft 73 often rotates 1 time, external gear 76 is swung 1 time, relative to The phase of internal gear 78 deviates the amount (be produced from change into point) of the amount of difference (number of teeth) 1 tooth every time.

By exporting the rotation point from output shaft 84 through slip promoting member 81, domestic 80 and output flange (wheel carrier) 82 Amount, the deceleration in planetary gear reducing mechanism 44 can be achieved.

The rotation of output shaft 84 is transferred to output pinion 24 through spline 87.Output pinion 24 is nibbled with swiveling gear 28 Close, also, the swiveling gear 28 is fixed on cylinder pillar 11.Therefore, by reaction, phase while 24 rotation of output pinion Revolved round the sun for the center 36 of swiveling gear 28, nacelle 12 relative to the swiveling gear 28 of the side of cylinder pillar 11 axle center 36 Rotate (revolution) in the horizontal direction.

Here, for example, it is assumed that produced " wind load " that makes the forced revolving of cabin 12 because of strong wind etc..The wind load is inverse To driving yaw drive system 14, and the output pinion 24 through the deceleration device G1 to be made of swiveling gear 28 rotates.If the wind-force Load be it is generally contemplated that in the range of (being less than the 1st predetermined value S1) torque, then connection shaft 70 and hollow shaft 66 (with its into The bushing 63 being integrated) between will not produce and relative slide (specific change will not be produced).That is, the torque is directly through hollow shaft 66 Continue the side of the 2nd parallel axle speed reducing machine structure 42 transmission to deceleration device G1, be finally attached to the braking (not shown) of motor 22 Device prevents.As a result, reliably braked by the activity of wind-induced nacelle 12.Certainly, including comprising deceleration device G1 Each portion of yaw drive system 14 will not produce special anomaly.

But the equipment under natural environment is provided in due to wind power plant, sometimes by very strong blast Or strong wind.When typically blowing high wind, deceleration device G1~G4 each rotation important document is by being arranged on the opposite with load of motor 22 The brake apparatus of side and as the state that can not rotate, prevent that nacelle 12 from being turned round because of high wind with non-control state.Cause This, almost the front in the state of stopping receives to be somebody's turn to do each component parts comprising the yaw drive system 14 including deceleration device G1 Stronger wind load, in the state of being in very severe.

Therefore, if offhand any countermeasure, some portion of the yaw drive system 14 including deceleration device G1 is included The position that can not bear the wind load in point may produce plastic deformation.Now, if plastic deformation position is for example, inclined Swiveling gear 28 for drive system 14 of navigating etc., then the scale of its repair is very huge, needs costly cost.

However, according to present embodiment, connection shaft 70 (the 1st linking part 70A) is expressly set to, with forming power transmission The miscellaneous part of system easily produces " frangible portion " of specific change (the relative slip with hollow shaft 66) when comparing passing power. Therefore, because wind load applies from the side of output pinion 24, if thus the 1st linking part 70A institutes torque suspension of connection shaft 70 surpass Go out the 1st predetermined value S1, then in the 1st linking part of (before producing some changes when miscellaneous part is in the passing power) connection shaft 70 " the relative slip with hollow shaft 66 " as specific change is produced between 70A and hollow shaft 66.

So, the 1st linking part 70A will not transmit torque more than 1st predetermined value S1, therefore can be automatically prevented from going off course All constitutive requirements of drive system 14 are by the torque more than torque corresponding with the 1st predetermined value S1.

That is, in present embodiment, when wind load is excessive, in each part of power-transmission system, linking at first Axle 70 produces " the relative slip with hollow shaft 66 " as specific change, therefore will not produce so-called substantial spoilage, first From this point it is known that easily being safeguarded.

In present embodiment, even if detecting the generation of specific change, (as a result of the interference fit in elastic deformation Thus) after the excessive wind load disappears, in most cases, can (with produce specific change before in the same manner as) continue to make With connection shaft 70.However, (or after generating specific change several times) after generating this specific change, connection shaft 70 may Some abnormal signs can be showed, therefore preferably takes out connection shaft 70 and actual inspection is carried out to it.

Now, in present embodiment, as shown in figure 3, dismantling cover 67 by unloading bolt 68, you can make hollow shaft The one end 66A of 66 hollow structure exposes outside to preceding-stage side shell 45.Further, it is possible to (assembled in itself in deceleration device G1 In the state of the nacelle 12 of wind power plant 10) from the one end 66A connection shaft 70 is taken out to outside preceding-stage side shell 45. That is, connection shaft 70 can just be taken out completely without decomposition preceding-stage side shell 45 and rear-stage side shell 48.

Also, if inspection result has no problem, then the connection shaft 70 after the inspection can be used directly, if noting abnormalities, New replacing part then can be assembled from the one end 66A of the hollow structure of the hollow shaft 66 of extraction.Therefore, come from this point See, safeguard quite easy.

In addition to this basic action effect, in above-mentioned embodiment, as described above, especially since using with The 1st linking part 70A that hollow shaft 66 links is set to frangible portion, and as specific change between connection shaft 70 and hollow shaft 66 The relative structure slided is produced, therefore each part of yaw drive system 14 can not only be protected from the influence of excessive torque, And connection shaft 70 itself also (even if having frangible portion, and generates specific change) and need not changed immediately.

Also, in above-mentioned embodiment, passed through using the 1st linking part 70A linked with hollow shaft 66 of connection shaft 70 It is full of and coordinates structure into joining line, therefore by being set to maintain the respective of the connection shaft 70 based on the interference fit and hollow shaft 66 Elastic deformation structure, even in slide midway, also can the 1st linking part 70A maintain equivalent to the 1st predetermined value S1 turn The transmission of square.Thus, for example, the method for completely cutting through the power transmission in deceleration device compared to simple closing clutch etc., It can further prevent nacelle 12 from swinging out of orderly (brakeless function and the direction state indefinite with wind direction).

Also, in above-mentioned embodiment, possesses the bushing (cylindrical portion engaged in a rotational direction with the inner circumferential of hollow shaft 66 Part) 63, connection shaft 70 is linked by being interference fitted with the bushing 63.Thereby, it is possible to obtain lot of advantages.I.e., it is desirable to hollow When the inside of axle 66 directly links connection shaft 70 by being interference fitted, especially by the connection shaft 70 temporarily taken out from hollow shaft 66 again , it is necessary to by being interference fitted into also to be assembled while joining line when linking again in secondary insertion hollow shaft 66, this will With many difficulties.However, the connection shaft 70 involved by present embodiment is rotating in the 2nd linking part 70B simply by spline Be connected together ring component 79 and bushing 63 on direction, thus, for example when taking out, by " the component A1 " of connection shaft 70 and bushing 63 Together extracted together with back-up ring 77, so as to easily take out connection shaft 70 (with reference to figure 3).

Also, the result checked after extracting, when connection shaft 70 has no special exception and re-assemblied, or find It is some abnormal and when being changed with new product, as long as reusing key 69 (coordinating by gap) by component A1 from hollow shaft 66 Hollow structure one end 66A insertion be assembled in preceding-stage side shell 45 hollow shaft 66 inside until back-up ring 77 engage untill .Therefore, re-assembly and change very comfortable.Especially, advance " with appropriate interference fit " can be manufactured in factory Connection shaft 70, therefore can extremely accurate realize the 1st predetermined value S1 management (sliding the management for starting torque).

In addition, coordinate the structure in insertion hollow shaft 66 to produce fretting by gap component A1, but i.e. Make to produce fretting etc. between hollow shaft 66 and bushing 63 and become to be difficult to extract, in present embodiment, can also utilize Form the screw 70T in the end of connection shaft 70 and easily extract connection shaft 70 using fixture (not shown).

In addition, in above-mentioned embodiment, connection shaft 70 is set to link near the one end 66A with hollow shaft 66, and In the part of the other end 66B protrusions from the hollow shaft 66 and the input shaft of eccentric oscillating-type planetary gear reducing gear 44 The structure that (part of next stage) 73 links.It is accordingly possible to ensure the overall length L2 of connection shaft 70 is longer, and can be applied The distribution effects such as the load of " torsional deformation ".

It is known not to be due to the action effect, is slightly described in detail.

As described above, when typically blowing high wind, each rotation important document of yaw drive system 14 by be arranged on motor 22 with The brake apparatus (not shown) of opposite side is loaded as the state that can not be rotated, prevents nacelle 12 because of high wind and with non-control State processed is turned round.

Therefore, in conventional yaw drive system, in fact, being intended to by " only 1 " drive system because of nacelle 12 Activity and deceleration device that sideshake is filled at first (for the sake of convenient, being set to the 1st deceleration device G1) prevent the swiveling gear 28 Further rotate, therefore the output pinion 24 that other deceleration devices G2~G4 be present maintains the side between swiveling gear 28 The state that gap is not filled, and can not from the side joint of swiveling gear 28 by wind load the problem of.

However, according to present embodiment, first, if the output pinion for the 1st deceleration device G1 that sideshake is filled at first 24 load from swiveling gear 28 by more than the 2nd predetermined value S2, then pass through the load, the torsional deformation of connection shaft 70.Therefore, (although deceleration device G1~G4 each rotation important document is in by brake apparatus rotates the situation stopped substantially) passes through connection shaft 70 torsional deformation, output pinion 24 can continue to rotate, and swiveling gear 28 can also follow it and continue to rotate.

As a result, the part for being applied only to the 1st deceleration device G1 load from the side of swiveling gear 28 in the past is divided It is fitted on the 2nd deceleration device G2.Also, the 2nd deceleration device G2 and the 3rd deceleration device G3 also can torsional deformation, therefore pass through The torsional deformation of each deceleration device G1~G4 connection shaft 70, eventually become each deceleration device G1~G4 respective connection shaft 70 Bear the state of roughly equal reaction force.

Sum it up, this represent, such as yaw drive system 14 as in the present embodiment by 4 deceleration device G1~ In the case that G4 is formed, actually (compared with the past) can obtain substantially being decreased to wind load 1/4 situation identical Action effect.Conversely, connection shaft 70 is started the wind load rotated against with hollow shaft 66 (with the 1st predetermined value S1 really Fixed relevant wind load) it can improve to substantially 4 times.

But the power transmission member actively utilizes " torsional deformation " and obtains the structure of " distribution effects such as load ", It is not necessarily in the present invention necessary.When not using the structure, the wind load for only putting on specific deceleration device is fast Speed exceeds the 1st predetermined value, easily produces sliding phenomenon, but in for example above-mentioned embodiment, due to being produced in the 1st linking part 70A Slide, thus wind load can automatically be successively applied over the deceleration device of the big sideshake with the 2nd (afterwards the 3rd ...), therefore, Finally the distribution effects such as load are obtained at the time of all deceleration devices produce slip.

Also, in present embodiment, connection shaft 70 is set to the pars intermedia between the 1st linking part 70A and the 2nd linking part 70B Outside diameter d 1 of the 70C outside diameter d 3 less than each linking part 70A, 70B, d2.Therefore, even same overall length L2 also can be larger Above-mentioned torsional deformation is ensured, as a result, the overall miniaturizations of deceleration device G1 can be realized.Also, when connection shaft 70 is lost, The less pars intermedia 70C of the diameter is clamped by using appropriate fixture, so as to clamp the link for remaining in the side of input shaft 73 The remainder (omit diagram) of axle 70 and extracted.

In addition, in present embodiment, possesses the caused detection that can go out specific change (relative to slide) from external detection Mechanism D1, therefore preceding-stage side shell 45 need not be decomposed and be just able to confirm that whether generate specific change.Specifically, sight can be passed through Examine the end face 63A for the bushing 63 being integrally formed with hollow shaft 66 and the end face 70D of connection shaft 70 across deceleration device G1 tops And whether the red-label (continuous mark) radially described misplaces to be confirmed whether to generate relative slip.Safeguarded When, if specific change can not be produced on connection shaft 70 to confirm by the observation, it can omit and specially take out the company The work for tying axle 70 to be checked is in itself.In view of having to deceleration device is carried out in the space of very narrow nacelle 12 During the situation of G1 maintenance, the effect is actually very big.

Also, in present embodiment, the one end 66A of hollow shaft 66 is covered part 67 and sealed, therefore can prevent rubbish Etc. being mixed into hollow shaft 66, and it is able to maintain that the easiness of observation.Especially, in the embodiment, cover 67 is by transparent Part is made, therefore need not remove cover 67 and also be able to confirm that whether there is specific change, therefore convenience is especially high.

In addition, in present embodiment, the space P3 of hollow shaft 66 and the space P4 of connection ring part 79 by oil sealing 71B, 71C, 71D isolate with the deceleration device G1 space P1, P2 for being sealed with lubricant, therefore, when extracting connection shaft 70, without load Heart lubricant drippage etc..

In addition, in above-mentioned embodiment, show be configured with motor 22 successively in power transfer path, orthogonal gear subtracts Fast mechanism 40, the 1st parallel axle speed reducing machine structure 41, the deceleration dress of the 2nd parallel axle speed reducing machine structure 42 and planetary gear reducing mechanism 44 G1 (~G4) is put, but in the present invention, the concrete structure of the reducing gear for deceleration system of going off course is not particularly limited to above-mentioned knot Structure.

Show come the orthogonal gear in the embodiment before replacing to subtract using worm gear reducer mechanism 110 in Fig. 5, Fig. 6 The deceleration device G1a of fast mechanism 40, the 1st parallel axle speed reducing machine structure 41 and the 2nd parallel axle speed reducing machine structure 42 configuration example.Other 3 Individual deceleration device (omitting diagram) is also set to and deceleration device G1a identical structures.

In addition, in the embodiment, motor is installed towards the direction orthogonal with paper, but in the Fig. 5, does not show that motor Itself, and merely illustrate the mounting hole 114 of motor.

Worm gear reducer mechanism 110 is made up of worm screw 116 and worm gear 118.Worm gear 118 is (for the defeated of the worm gear reducer mechanism 110 Shaft) it is integrally formed with worm screw output shaft 120.Worm screw output shaft 120 is hollow, and with embodiment before The identical structure of hollow shaft 66 of 2nd parallel axle speed reducing machine structure 42.Connection shaft 70 with embodiment identical before by connecting Junction structure is linked to the inside of worm screw output shaft 120.Also, connection shaft 70 is with identical with the connection shaft 70 of embodiment before Structure and the part of next stage be that the rotary shaft 133 of sun gear 132 of the 1st simple planetary reducing gear 130 links.

1st simple planetary reducing gear 130 possesses sun gear 132, planetary gear 134 and internal gear 136, fixed star Gear 132 plays a role as input block, and the wheel carrier 138 of planetary gear bearing 134 plays a role as output block.

The 2nd simple planetary reducing gear 140 is linked with the rear class of the 1st simple planetary reducing gear 130.The 2 simple planetary reducing gears 140 possess sun gear 142, the planetary gear linked through spline 139 and the wheel carrier 138 144 and internal gear 146, sun gear 142 plays a role as input block, and the wheel carrier 148 of planetary gear bearing 144 is as defeated Go out part to play a role.

In addition, in the embodiment, in the absence of the oil sealing of the oil sealing 71D equivalent to embodiment before, hollow shaft 66 Inside do not isolate with being sealed with the space P5 of lubricant.

In the embodiment, worm screw output shaft 120, connection shaft 70 also have with the hollow shaft 66 of embodiment before, The identical structure of connection shaft 70, therefore embodiment identical action effect preceding therewith can be obtained.Pair therefore, with before Embodiment practically identical position mark and embodiment identical symbol before, and omit repeat specification.

In the embodiment, the speed reducing ratio of worm gear reducer mechanism 110 is set as more than 30 (being preferably more than 40).If by snail The speed reducing ratio of wheel reducing gear 110 is set as more than 30, then can utilize self-locking possessed by the worm gear reducer mechanism 110 itself Function (load of the obstructed self-supported side that comes and rotate function) is used as " brake apparatus ".Therefore, it is possible to the reality before omitting The brake apparatus of motor 22 is attached to necessary to applying in mode, cost can be reduced accordingly.

Also, one of another embodiment of the invention is shown in Fig. 7, Fig. 8.Deceleration device G1b basic structure It is identical with the deceleration device G1 involved by Fig. 1~Fig. 3 embodiment.

Unlike, in embodiment before, bushing 63 is between hollow shaft 66 and connection shaft 70, but this implementation In mode, connection shaft 70 is directly linked to the inside of hollow shaft 66 by key 169.Due to also without back-up ring (77), therefore save Slightly.

Because the 1st linking part 70A linked with hollow shaft 66 uses the link based on key 169, thus with implementation before Mode carries out disengaging of the connection shaft 70 from the one end 66A of hollow shaft 66 by " gap cooperation " in the same manner, therefore more light Pine.But due to using the link based on key 169, therefore, even if being applied with excessive wind load, also will not in the part Produce relative slide.That is, in the embodiment, the 1st linking part 70A does not form frangible portion.

And in the embodiment, the 1st linking part 70A linked with hollow shaft 66 of connection shaft 70 external diameter be with before Embodiment identical d1, with next stage link the 2nd linking part 70B external diameter also be and embodiment identical before D2, in contrast, before the external diameter of the pars intermedia 70Ca between the 1st linking part 70A and the 2nd linking part 70B is d3a and ratio The outside diameter d 3 of embodiment is slightly smaller, and the part be pars intermedia 70Ca between the 1st linking part 70A and the 2nd linking part 70B in itself As " frangible portion ".That is, when having excessive wind load input, the pars intermedia 70Ca of the connection shaft 70 itself produces plasticity and become Shape.In other words, in the embodiment, the specific change of connection shaft (power transmission member) 70 is the connection shaft 70 plasticity of itself Deformation.

In this embodiment, also can be by being confirmed whether to generate spy with embodiment identical structure before Fixed change.But it is different from embodiment before, when confirming the generation of specific change, connection shaft 70 is changed immediately.

As described above, the taking-up of connection shaft 70, re-assemblying or changing very comfortable.Also, as practical problem, apply Having makes connection shaft 70 be enough the situation of the wind load of degree that is plastically deformed and infrequently, on the other hand, " if plastic deformation It is possible for this imagination of connection shaft 70 ", therefore can also lays in advance, therefore from the aspects of practicality, it is not so much Obstacle, especially from the point of view of it can reduce initial cost (construction cost of wind power plant) this point, the reality than Fig. 1~Fig. 3 It is excellent to apply mode.

Other parts are identical with the embodiment of Fig. 1~Fig. 3 before, therefore are only limitted in figure to same or similar Part mark identical symbol, and omit repeat specification.

It is as described above, in the present invention, for which of power transmission member is partly set into the frangible portion of which kind of form, It is not particularly limited.For example, instead of the 1st linking part, or in addition to the 1st linking part, the 2nd linking part can also be set to fragile Portion.Also, in the case where linking the 1st linking part or the 2nd linking part using key, it is also contemplated that using being easily plastically deformed The methods of elongated key.Specific change now is the plastic deformation of digital.

In this way, the formation of frangible portion is not necessarily defined to be made only at 1 or species is only a kind.If the knot of frangible portion Structure is different, then the specific change shown can also change, therefore in order that the specific change of some power transmission members must It must be produced before the damage at other positions etc., effectively possess multiple frangible portions.At this point it is possible to it is set to that specific change exists Produced under identical wind load, can also specially be set to generation of somewhat staggering.Such as following 2 level structure can be used, i.e. , also specially will even in addition to forming the 1st frangible portion based on interference fit of the 1st linking part in Fig. 1~Fig. 3 structure The intensity of the pars intermedia of knot is set to relatively low and forms the 2nd frangible portion, and in the 1st linking part for certain reason such as adhesion Relative slip when not playing a role correctly, connection shaft is plastically deformed in itself under the setting value more slightly higher than its.

Also, as illustrated, the structure of the reducing gear of deceleration device also and is not particularly limited, for example, can also use from The position of the axle center skew of internal gear has multiple eccentric body synchronizations for possessing the eccentric shaft of eccentric body, and making each eccentric shaft Rotation, so that the eccentric oscillating-type planetary gear reducing gear for being referred to as distribution formula that external gear is swung.Also, it can also use Taper reducing gear and replace hypoid reducing gear.Can certainly independent assortment these reducing gears.

Industrial applicability

The present invention can similarly be applied to pitch driving and use in addition to it can be applied to driftage driving deceleration device Deceleration device.

Specification, accompanying drawing and the claim of 2 months 2013 Japanese patent applications filed in 28 days the 2013-040127th Full content disclosed in book by reference to being applied in this specification respectively.

Symbol description

10- wind power plants, 11- cylinder pillars, 12- nacelles (power compartment), 14- yaw drive systems, 16- pitches drive Dynamic system, 18- radome fairings, 20- air vanes, 22- motors, 24- output pinions, 44- planetary gear reducing mechanisms, 66- are empty Mandrel, 70- connection shafts (power transmission member), the linking parts of 70A- the 1st, the linking parts of 70B- the 2nd, 70C- pars intermedias, 73- inputs Axle, 76- external gears, 78- internal gears, 84- output shafts, G1~G4- deceleration devices.

Claims (10)

1. A kind of 1. deceleration device for being used in wind power plant, it is characterised in that

   As power-transmission system a part and possess the hollow shaft of hollow structure,

   There is the power transmission member towards next stage in the interior bonds of the hollow shaft,

   The one end of the hollow structure of the hollow shaft can expose from shell,

   The power transmission member easily produces when being set to compared with the miscellaneous part for forming power-transmission system in passing power The frangible portion of specific change, and

   The power transmission member is set to can be in the state of the deceleration device be assemblied in the wind power plant in itself from institute The one end for stating the hollow structure of hollow shaft takes out the power transmission member to outside shell.
2. 2. the deceleration device according to claim 1 for being used in wind power plant, it is characterised in that

   In the power transmission member, the linking part for the part link being integrally formed with the hollow shaft or with the hollow shaft is set to The frangible portion,

   The specific change is between the power transmission member and the hollow shaft or the part being integrally formed with the hollow shaft It is relative to slide.
3. 3. the deceleration device according to claim 2 for being used in wind power plant, it is characterised in that

   The linking part is linked by being interference fitted.
4. 4. the deceleration device for being used in wind power plant according to Claims 2 or 3, it is characterised in that

   The deceleration device is also equipped with the cartridge engaged in a rotational direction with the inner circumferential of the hollow shaft,

   The power transmission member is linked by interference fit and the cartridge.
5. 5. the deceleration device according to claim 1 for being used in wind power plant, it is characterised in that

   The specific change of the power transmission member is the plastic deformation of the power transmission member in itself.
6. 6. the deceleration device according to claim 1 or 2 for being used in wind power plant, it is characterised in that

   The power transmission member near the one end of the hollow structure of the hollow shaft with linking, and from the sky The part that the other end of mandrel protrudes links with the next stage.
7. 7. the deceleration device according to claim 6 for being used in wind power plant, it is characterised in that

   In the power transmission member, between the linking part linked with the hollow shaft and the linking part linked with the next stage External diameter be set to smaller than the external diameter of each linking part.
8. 8. the deceleration device according to claim 1 or 2 for being used in wind power plant, it is characterised in that

   The deceleration device is also equipped with can be from the caused testing agency of specific change described in external detection.
9. 9. the deceleration device according to claim 1 or 2 for being used in wind power plant, it is characterised in that

   The one end of the hollow structure of the hollow shaft is covered part and sealed.
10. 10. the deceleration device according to claim 1 or 2 for being used in wind power plant, it is characterised in that

    The inside of the hollow shaft is isolated by seal member with the space for being sealed with lubricant of the deceleration device.