JP6064690B2 - Wind power generator - Google Patents

Description

  The present invention relates to a wind turbine generator that drives a generator by increasing the rotation of a main shaft by wind power using a gearbox.

2. Description of the Related Art Conventionally, there has been known a wind power generator that receives wind power from a blade, rotates a main shaft connected to the blade, and drives the generator by increasing the rotation of the main shaft by a speed increaser.
The speed increaser of the wind power generator is provided with a roller bearing that rotatably supports an output shaft that rotates at high speed. However, this roller bearing has a problem that its life is shortened due to smearing (a phenomenon in which surface seizure occurs) generated on the rolling surface of the roller and the raceway surface of the rotating wheel. Therefore, the present inventor has conducted extensive research on the smearing generation mechanism, and in order to suppress the smearing, a one-way clutch is provided between the output shaft of the speed increaser and the drive shaft of the generator. It has been found that it is effective to provide it, and this has been proposed previously (Japanese Patent Application No. 2011-198354 (however, this application is unpublished at the time of filing of the present application (unknown technology))). A technique in which a one-way clutch is provided between the output shaft of the speed increaser and the drive shaft of the generator is known in Patent Document 3, although the purpose is different.

JP-A-4-344198

The one-way clutch has a rotating body provided on the output shaft side of the speed increaser or the input shaft side of the generator, a ring body fitted to the rotating body, and an engagement member meshing with the ring body. In order to transmit the power from the rotating body to the ring body by the frictional force of the both, it is necessary to connect the two by an interference fit. In this case, if the load for operating the generator is maximized and the power is transmitted between them only by the frictional force due to the interference fit, the tightening margin between the rotating shaft and the ring body is extremely small. The internal stress generated in the ring body becomes excessive, and the service life of the ring body, and hence the life of the one-way clutch, is reduced.
In addition, since the rotating body provided on the output shaft side of the speed increaser or the input shaft side of the generator in the wind turbine generator is very large, processing for the one-way clutch is directly applied to the rotating body. It is difficult. For this reason, normally, a ring body that has been processed separately is assembled to the rotating body, and therefore it is extremely important to solve the above problems.

  The present invention has been made in view of such circumstances, and it is possible to increase the life of a one-way clutch provided between an output shaft of a speed increaser and an input shaft (drive shaft) of a generator. An object is to provide a power generator.

A wind turbine generator according to the present invention has a speed increaser that accelerates rotation of a main shaft generated by wind power and outputs the speed from an output shaft, and an input shaft that rotates using the rotation of the output shaft as an input. A generator that generates electric power with rotation of a rotor that rotates integrally with the output shaft, and the output shaft and the input shaft, and the output shaft in a state in which the rotational speed of the output shaft exceeds the rotational speed of the input shaft. A one-way clutch that connects the shaft and the input shaft so as to be integrally rotatable, and disconnects the connection between the output shaft and the input shaft in a state where the rotational speed of the output shaft is lower than the rotational speed of the input shaft. The one-way clutch is disposed to face a ring body (an inner ring or an outer ring) fitted to a rotating body that rotates together with the output shaft, and a radially outer side or a radially inner side of a circumferential surface of the ring body. , Other peripheral surface provided on the input shaft side A plurality of engagement elements arranged in a space between the two peripheral surfaces, and the engagement elements mesh with the two peripheral surfaces to connect the output shaft and the input shaft so as to be integrally rotatable, and the meshing The connection is cut off by releasing and the maximum transmission torque T1max to be transmitted from the rotating body to the wheel when the load torque for operating the generator is maximum, and the rotation A transmission torque T2 that can be transmitted from the rotating body to the ring body by a tightening force generated by fitting the body and the ring body,
T1max> T2
In relation to
The minimum necessary transmission torque T1 to be transmitted from the rotating body to the ring body in order to operate the generator, and the tightening force caused by the engagement of the engaging element with the peripheral surface of the ring body, from the rotating body. The transmission torque T3 that can be transmitted to the ring body and the transmission torque T2 are:
T1 <T2 + T3
It is characterized by having the relationship.

In addition, the present invention includes a speed increaser that accelerates the rotation of the main shaft generated by wind power and outputs it from the output shaft, and an input shaft that rotates using the rotation of the output shaft as an input, and is integrated with the input shaft. A generator that generates electric power as the rotor rotates, and is provided between the output shaft and the input shaft, and the output shaft and the output shaft in a state in which the rotational speed of the output shaft exceeds the rotational speed of the input shaft. A one-way clutch that connects the input shaft so as to be integrally rotatable, and that disconnects the connection between the output shaft and the input shaft in a state where the rotational speed of the output shaft is lower than the rotational speed of the input shaft. A wind power generator,
The one-way clutch is disposed on the output shaft side so as to be opposed to a ring body fitted to a rotating body that rotates together with the input shaft, and a radially outer side or a radially inner side of a circumferential surface of the ring body. And the output shaft and the input shaft are integrally rotated by engaging the engagement members with the peripheral surfaces. The connection is possible, and the connection is cut off by releasing the engagement;
The maximum transmission torque T1max to be transmitted from the rotating body to the ring when the load torque for operating the generator is maximum, and the tightening force due to the fitting of the rotating body and the ring Transmission torque T2 that can be transmitted from the rotating body to the ring body,
T1max> T2
In relation to
The minimum required transmission torque T1 to be transmitted from the rotating body to the ring body in order to operate the generator, and the tightening force generated by the engagement of the engaging element with the peripheral surface of the ring body, from the rotating body. The transmission torque T3 that can be transmitted to the ring body and the transmission torque T2 are:
T1 <T2 + T3
It is characterized by having the relationship.

  According to this configuration, not only the tightening force (initial tightening force) due to the engagement between the rotating body and the ring body, but also the tightening force (additional tightening force) due to the engagement between the ring body and the engagement element is considered. The transmission torque between the rotating body and the ring body is set so as to satisfy the minimum necessary transmission torque for operating the generator. Therefore, it is not necessary to excessively increase the initial tightening force, and the stress generated in the ring body can be reduced as much as possible. Therefore, it is possible to increase the life of the ring body, and thus the life of the one-way clutch.

In addition, it is preferable that the interference of the said rotary body and the said ring body shall be 10 micrometers or more. Thereby, the transmission torque between the ring body and the rotating body at the initial stage of engagement of the engagement element and the ring body can be sufficiently ensured.
Further, it is preferable that 4 to 8 engagement elements are provided in the circumferential direction.
When the number of the engagement elements exceeds 8, the force applied from the engagement elements to the peripheral surface of the ring body is dispersed, the tightening force due to the engagement between both becomes small, and it becomes difficult to ensure a sufficient transmission torque T3. This is because if the number of engagement elements is less than 4, the transmission torque T3 is excessively increased, and the load on the ring body may increase.

The one-way clutch is preferably incorporated in a shaft coupling device that connects the output shaft and the input shaft so as to be integrally rotatable.
According to this configuration, even in the case where an axial space between the output shaft of the speed increaser and the input shaft of the generator cannot be secured, the shaft coupling device that connects the two shafts is used. A directional clutch can be provided.

  ADVANTAGE OF THE INVENTION According to this invention, the lifetime of the one way clutch provided between the output shaft of a gearbox and the input shaft of a generator can be improved.

1 is a schematic side view of a wind turbine generator according to a first embodiment of the present invention. It is a schematic side view which shows a gearbox and a generator. It is a side view (partial sectional view) showing a shaft coupling device. It is AA arrow sectional drawing in FIG. It is sectional drawing of the shaft coupling apparatus which expands and shows a one-way clutch and a rolling bearing. It is sectional drawing which expands and shows the principal part of a one-way clutch. It is a perspective view which shows the holder | retainer of a one-way clutch. It is explanatory drawing which shows the effect | action of a one way clutch. It is a graph explaining the relationship between load torque and transmission torque. It is explanatory drawing which shows the assembly procedure of a shaft coupling apparatus. It is sectional drawing which shows the roller bearing of a gearbox. It is sectional drawing which expands and shows the connection part of a cover member. It is sectional drawing which shows the shaft coupling apparatus of the wind power generator which concerns on the 2nd Embodiment of this invention. It is sectional drawing which expands and shows the principal part of a one-way clutch. It is a schematic side view which shows the modification of a wind power generator. It is a schematic side view which shows the gearbox and generator in other embodiment. It is sectional drawing of the shaft coupling apparatus which expands and shows the one-way clutch and rolling bearing in other embodiment. It is sectional drawing of the shaft coupling apparatus which expands and shows the one-way clutch and rolling bearing in other embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a schematic side view of a wind turbine generator according to a first embodiment of the present invention.
The wind power generator 1 includes a blade (wind receiving member) 11, a support 12, and a nacelle 13. The blade 11 is constituted by a plurality of blades provided at the tip of the main shaft 2 and rotates the main shaft 2 by receiving wind. The nacelle 13 generates power by using the main shaft 2, a support mechanism 15 for supporting the main shaft 2, a speed increasing device 3 for increasing the rotation of the main shaft 2, and rotational power increased by the speed increasing device 3. The machine 4 and the casing 18 etc. which accommodate these are provided. The support column 12 supports the nacelle 13 so as to be able to turn horizontally around the vertical axis.

FIG. 2 is a schematic side view showing the speed increaser and the generator.
The generator 4 is constituted by, for example, an induction generator, and inputs a rotation speed increased by the speed increaser 3 to be rotated (input shaft) 41, a rotor 42 built in the power generator 4, and an illustration. And a stator that does not. The rotor 42 is coupled to the drive shaft 41 so as to be integrally rotatable, and the generator 4 is configured to generate electric power as the drive shaft 41 rotates and the rotor 42 is driven. The drive shaft 41 is provided with a brake 44 for braking the drive shaft 41.

The speed increaser 3 includes a gear mechanism (rotation transmission mechanism) 30 that inputs the rotation of the main shaft 2 and accelerates the rotation. The gear mechanism 30 includes a planetary gear mechanism 31 and a high-speed gear mechanism 32 that inputs the rotation accelerated by the planetary gear mechanism 31 and further accelerates the rotation.
The planetary gear mechanism 31 includes an internal gear (ring gear) 31a, a plurality of planetary gears 31b held by a planet carrier (not shown) coupled to the main shaft 2 so as to be integrally rotatable, and a sun gear 31c meshing with the planetary gear 31b. have. Accordingly, when the planet carrier rotates together with the main shaft 2, the sun gear 31 c rotates through the planetary gear 31 b, and the rotation is transmitted to the low speed shaft 33 of the high speed gear mechanism 32.

The high speed gear mechanism 32 includes the low speed shaft 33 having a low speed gear 33a, the intermediate shaft 34 having a first intermediate gear 34a and a second intermediate gear 34b, and an output shaft 35 having a high speed gear 35a.
The low speed shaft 33 is a large rotating shaft having a diameter of about 1 m, for example, and is disposed concentrically with the main shaft 2. Both axial ends of the low speed shaft 33 are rotatably supported by roller bearings 36a and 36b.

The intermediate shaft 34 is disposed above the low-speed shaft 33, and both axial ends thereof are rotatably supported by roller bearings 37a and 37b. The first intermediate gear 34a of the intermediate shaft 34 meshes with the low speed gear 33a, and the second intermediate gear 34b meshes with the high speed gear 35a.
The output shaft 35 is disposed above the intermediate shaft 34 and outputs rotational torque. One end portion 35b and the other end portion (output end portion) 35c side of the output shaft 35 are rotatably supported by roller bearings 38 and 39, respectively.

  With the above configuration, the rotation of the main shaft 2 is made in three stages depending on the gear ratio of the planetary gear mechanism 31, the gear ratio between the low speed gear 33a and the first intermediate gear 34a, and the gear ratio between the second intermediate gear 34b and the high speed gear 35a. And the rotational torque is output from the output end portion 35 c of the output shaft 35. That is, the rotation of the main shaft 2 by wind power is increased in three stages by the speed increaser 3 to drive the generator 4.

  FIG. 11 is a cross-sectional view showing a roller bearing of a speed increaser. In FIG. 11, a roller bearing 38 is a cylindrical roller bearing, and is interposed between an inner ring 38a that is externally fitted and fixed to the output shaft 35, an outer ring 38b that is fixed to a housing (not shown), and an inner ring 38a and an outer ring 38b. A plurality of cylindrical rollers 38c arranged so as to be capable of rolling, and an annular cage 38d that holds each cylindrical roller 38c at predetermined intervals along the circumferential direction. The inner ring 38a, the outer ring 38b, and the cylindrical roller 38c are made of, for example, bearing steel, and the cage 38d is made of, for example, a copper alloy.

  The inner ring 38a has an inner ring raceway surface 38a1 formed at the axial center of the outer periphery thereof. The outer ring 38b is disposed concentrically with the inner ring 38a, and has an outer ring raceway surface 38b1 formed at the axially central portion of the inner circumference and a pair of outer ring rods formed on both sides in the axial direction of the outer ring raceway surface 38b1. Part 38b2. The outer ring raceway surface 38b1 is disposed to face the inner ring raceway surface 38a1. The outer ring flange 38b2 is formed to project radially inward from both axial ends of the inner periphery of the outer ring 38b, and the end surface of the cylindrical roller 38c is in sliding contact with the outer ring flange 38b2.

The cylindrical roller 38c is disposed so as to be able to roll between the inner ring raceway surface 38a1 of the inner ring 38a and the outer ring raceway surface 38b1 of the outer ring 38b.
The retainer 38d has a pair of annular portions 38d1 that are disposed apart from each other in the axial direction, and a plurality of retainers 38d that are disposed at equal intervals along the circumferential direction of the annular portion 38d1 and connect the annular portions 38d1 to each other. Column part 38d2. A pocket 38d3 is formed between the pair of annular portions 38d1 and the adjacent column portion 38d2, and each cylindrical roller 38c is disposed in the pocket 38d3. In the large wind power generator 1, a large load is applied to the rolling bearing that supports the output shaft 35 of the speed increaser 3, so that the rigidity is high and the axial expansion and contraction due to the heat of the output shaft 35 is performed. It is preferable to use a roller bearing 38 that can absorb the above. However, a ball bearing or a tapered roller bearing may be used as the rolling bearing.

  In FIG. 2, the wind turbine generator 1 includes a shaft coupling device (coupling device) 9 that connects the output shaft 35 of the speed increaser 3 and the drive shaft 41 of the generator 4 so as to be integrally rotatable. The shaft coupling device 9 includes an input rotating body (inner rotating body) 5, an output rotating body (outer rotating body) 6, a one-way clutch 7, and a rolling bearing 8, and is also configured as a clutch unit. Has been. The shaft coupling device 9 is provided closer to the speed increaser 3 than the brake 44 for the drive shaft 41.

FIG. 3 is a side view (partially sectional view) showing the shaft coupling device. 4 is a cross-sectional view taken along arrow AA in FIG.
The input rotator 5 includes a shaft portion 51 and an input side connecting portion 52 provided at one axial end portion (left end portion in FIG. 3) of the shaft portion 51. The input side connecting portion 52 is connected to the output shaft 35 so as to be integrally rotatable and detachable.
The output rotator 6 is disposed concentrically with the input rotator 5 and is provided at a cylindrical portion 61 formed in a cylindrical shape and the other axial end portion (right end portion in FIG. 3) of the cylindrical portion 61. Output side connecting portion 62. The output side connecting portion 62 is connected to the drive shaft 41 so as to be integrally rotatable and detachable.

  The one-way clutch 7 is disposed between the input rotator 5 and the output rotator 6 and in a portion that overlaps each other in the radial direction. Further, the rolling bearings 8 are disposed between the input rotator 5 and the output rotator 6 on both axial sides of the one-way clutch 7. The one-way clutch 7 is provided to transmit the rotation of the output shaft 35 to the drive shaft 41 via the input rotator 5 and the output rotator 6 so as to be connectable and disconnectable, and the rolling bearing 8 is connected to the output shaft 35 and the drive shaft 41. Are provided to support each other. In the wind power generator 1 of the present embodiment, the rolling bearings 8 are disposed on both axial sides of the one-way clutch 7, but may be disposed only on one axial side of the one-way clutch 7.

  In FIG. 3, the input side connecting portion 52 includes a flange portion 52 a fixed to one end portion of the shaft portion 51, and a bending member 52 b interposed between the flange portion 52 a and the output shaft 35. The shaft portion 51 is formed in a cylindrical shape, and a key groove 51b is formed on the outer peripheral surface of one axial end portion (left end portion in FIG. 3). The flange portion 52a is formed in an annular shape and includes a plurality of (for example, four) protruding portions 52a1 (see FIG. 4) protruding outward in the radial direction at intervals in the circumferential direction. Each protrusion 52a1 is formed with a bolt insertion hole 52a2. A fitting hole 52a3 is formed at the center of the flange portion 52a, and one end of the shaft portion 51 is fitted into the fitting hole 52a3 by press fitting or the like. A keyway 52a4 is formed in the fitting hole 52a3. The shaft portion 51 and the flange portion 52a are coupled so as to be integrally rotatable by attaching a key 53 to the two key grooves 52a4 and 51b.

  The output side connecting portion 62 includes a flange portion 62 a provided at the other axial end portion of the cylindrical portion 61, and a bending member 62 b interposed between the flange portion 62 a and the drive shaft 41. The flange portion 62a is integrally formed at one end portion of the cylindrical portion 61 by forging or the like, protrudes radially outward from the outer peripheral surface of the cylindrical portion 61, and is formed with a bolt insertion hole 62a1 passing therethrough. Moreover, the flange part 62a is provided with two or more (for example, four pieces) at intervals in the circumferential direction similarly to the protrusion part 52a1 of the flange part 52a of the input side connection part 52.

  The bending member 52b of the input side connecting portion 52 is disposed between the flange portion 52a and a flange portion 35c1 provided on the output end portion of the output shaft 35 on the 35c. Further, the bending member 62 b of the output side connecting portion 62 is disposed between the flange portion 62 a and the flange portion 41 a provided at the input end portion of the drive shaft 41. The bending members 52b and 62b are composed of a plurality of link-like members or disk-like members, and are connected to the flange portions 52a, 35c1, 62a and 41a by fasteners 52c and 62c, respectively, which are bolts and nuts.

  The bending members 52b and 62b have a function of absorbing misalignment such as eccentricity and declination (shift of the axial center) between the output shaft 35 and the drive shaft 41 by its own bending (elastic deformation). . The configuration of the deflecting members 52b and 62b and the configuration of the flange portions 52a, 35c1, 62a, and 41a used in combination therewith are not particularly limited. The configurations described in JP 2006-250034 A, JP 2001-349335 A, and the like can be applied. Further, the input side connecting portion 52 may include the flange portion 35c1 on the output shaft 35 side as a component, and the output side connecting portion 62 may include the flange portion 41a on the drive shaft 41 side as a component. .

  Grease (lubricant) for lubricating the one-way clutch 7 and the rolling bearing 8 disposed therein is filled between the shaft portion 51 of the input rotator 5 and the cylindrical portion 61 of the output rotator 6. The The shaft coupling device 9 is provided with a sealing means 10 that forms a sealed space for filling grease between the shaft portion 51 and the cylindrical portion 61, which are accommodation regions of the one-way clutch 7 and the rolling bearing 8. Yes. The sealing means 10 includes an annular seal receiving member 101 fitted on the outer peripheral surface of the shaft portion 51 between the left rolling bearing 8 and the flange portion 52 a of the input rotating body 5, and an outer periphery of the seal receiving member 101. A ring-shaped first seal member 102 provided in a gap between the surface and the inner peripheral surface of the cylindrical portion 61 of the output rotator 6, a lid member 103 that closes an opening on the right end side of the cylindrical portion 61, and the lid member 103 And a second seal member 104 made of an O-ring provided between the end surface of the cylindrical portion 61. The lid member 103 is made of a metal plate formed in a circular shape, and is detachably attached to the base portion of the flange portion 62a by an attachment screw 103a. By providing such a sealing means 10, grease is sealed between the shaft portion 51 of the input rotator 5 and the cylindrical portion 61 of the output rotator 6, and the one-way clutch 7 and the rolling bearing 8 are suitably lubricated. Can do.

  In addition, the arrangement location of the one-way clutch 7 and the arrangement location of the rolling bearing 8 in the sealed space between the shaft portion 51 and the cylindrical portion 61 are communicated in the axial direction, and grease is provided between the one-way clutch 7 and the rolling bearing 8. It is supposed to spread between. Further, since grease tends to be biased radially outward due to centrifugal force, the sealed space communicates with the outer ring inner peripheral surface 72a of the one-way clutch 7 and the outer ring raceway surface 82a side of the rolling bearing 8 as in the present embodiment. It is preferable.

  In addition, an oil supply hole 61a to which a grease nipple (an oil supply port with a check valve) 64 is attached is formed in the outer peripheral portion of the cylindrical part 61 so as to penetrate in the radial direction to the sealed space. The oil supply hole 61 a is provided correspondingly between the one-way clutch 7 and one of the rolling bearings 8. Specifically, the oil supply hole 61 a is formed between the outer ring inner peripheral surface 72 a of the one-way clutch 7 and the outer ring raceway surface 82 a of the rolling bearing 8. Further, the oil supply holes 61a are provided at a plurality of positions in the circumferential direction, for example, at four positions as shown in FIG. 4 at equal intervals, and grease can be supplied into the sealed space from any of the oil supply holes 61a. Yes.

  Further, when grease is supplied from any one of the oil supply holes 61a, the old grease can be discharged from the other oil supply holes 61a by removing the grease nipple 64 of the other oil supply holes 61a. Therefore, the oil supply hole 61a has not only a function as a grease supply part but also a function as a discharge part. The grease can be discharged not only by the oil supply hole 61 a but also by removing the lid member 103 from the output rotating body 6. In this case, since the entire opening at the end of the cylindrical portion 61 can be opened, the grease can be discharged efficiently.

When the output rotating body 6 rotates, the position of the oil supply hole 61a also fluctuates. However, since a plurality of oil supply holes 61a are provided in the circumferential direction, the oil supply hole 61a arranged at a position where oil supply is most easily performed is selected and supplied. be able to. Therefore, the refueling operation can be easily performed.
Moreover, since the oil supply hole 61a is provided correspondingly between the one-way clutch 7 and the one rolling bearing 8, the grease can be reliably supplied to both. The oil supply hole 61 a may be provided between the one-way clutch 7 and the other rolling bearing 8, or provided between the one-way clutch 7 and both the rolling bearings 8. Also good. The grease used for lubricating the one-way clutch 7 is preferably one that is less susceptible to temperature changes using an ester as the base oil and a urea-based one as the thickener, but is limited to this. It is not a thing.

  A gap s2 is formed between the end surface of one end portion in the axial direction of the cylindrical portion 61 (left end portion in FIG. 3) and the end surface of the flange portion 52a of the input rotating body 5 facing the end surface. Further, a gap s <b> 3 is formed between the tip of the shaft portion 51 and the lid member 103. Due to the gaps s 2 and s 3, the output rotator 6 can move to both sides in the axial direction with respect to the input rotator 5 in a state where the output rotator 6 is separated from the drive shaft 41.

FIG. 5 is an enlarged cross-sectional view of the shaft coupling device showing the one-way clutch and the rolling bearing.
As shown in FIGS. 4 and 5, the one-way clutch 7 includes an inner ring 71 and an outer ring 72, and a plurality of rollers (engagement between the outer peripheral surface 71 a of the inner ring 71 and the inner peripheral surface 72 a of the outer ring 72. 73).

  The inner ring 71 is fixed by being fitted to the axially intermediate portion of the shaft portion 51 of the input rotating body 5, and rotates integrally with the shaft portion 51. A region B in the axial direction intermediate portion of the cylindrical portion 61 in the output rotating body 6 is an outer ring 72 of the one-way clutch 7. Accordingly, the inner peripheral surface of the region B of the cylindrical portion 61 constitutes an outer ring inner peripheral surface 72a on which the rollers 73 roll. In this embodiment, the rollers 73 are formed in a cylindrical shape, and eight rollers are provided in the circumferential direction.

The one-way clutch 7 includes an annular retainer 74 that holds each roller 73 at predetermined intervals along the circumferential direction, and a plurality of elastic members (biasing members) that elastically bias each roller 73 in one direction. 75).
FIG. 7 is a perspective view showing a cage of the one-way clutch. In FIG. 7, the retainer 74 is a pair of annular portions 76 facing in the axial direction, and these annular portions 76 are separate from each other, and both ends in the axial direction are fitted into the annular portions 76. A plurality of column portions 77. A pocket 78 is constituted by a space surrounded by both annular portions 76 and a column portion 77 adjacent in the circumferential direction, and each roller 73 is individually accommodated in each pocket 78 (see FIG. 4).

The annular portion 76 is made of a metal material such as carbon steel or aluminum, and has an outer diameter of 300 mm and an axial thickness of 15 mm, for example. A plurality of concave portions 76 a are formed on the inner periphery of the annular portion 76 at predetermined intervals in the circumferential direction.
The column part 77 includes a main body part 77a, a protruding part 77b projecting from one end surface in the circumferential direction of the main body part 77a, and a pair of fitting parts 77c formed at both axial ends of the main body part 77a. Have. And the main-body part 77a, the projection part 77b, and the fitting part 77c are integrally molded by injection-molding a synthetic resin material.

  As shown in FIG. 4, the protrusion 77 b guides (positions) the elastic member 75 accommodated in the pocket 78. Specifically, the protrusion 77b is formed so as to become gradually thinner toward the tip. And the elastic member 75 is loosely fitted from the front end side of the projection part 77b. The elastic member 75 is composed of a compression coil spring that is elongated in the axial direction. However, the elastic member 75 may be another type of spring such as a leaf spring.

  As shown in FIG. 7, the fitting portion 77c is formed to be thinner in the radial direction than the main body portion 77a, and the outer periphery of the annular portion 76 in a state where the fitting portion 77c is fitted in the recess 76a. The thickness of the fitting portion 77c is set so that the surface and the outer peripheral surface of the main body portion 77a are substantially flush with each other.

  As described above, the retainer 74 includes the annular portion 76 and the column portion 77, which are formed separately from each other. Therefore, the annular portion 76 and the column portion 77 can be individually manufactured. it can. Therefore, the retainer 74 can be easily manufactured as compared with the case where the entire retainer 74 is manufactured integrally. In particular, since the retainer 74 used in the wind power generator 1 is large and difficult to manufacture as a whole, it is more beneficial to configure the annular portion 76 and the column portion 77 separately. is there. Further, the strength of the cage 74 can be sufficiently secured by making the annular portion 76 made of metal, and the weight of the cage 74 as a whole can be reduced by making the column portion 77 made of synthetic resin. .

As shown in FIG. 4, the same number (eight) of flat cam surfaces 71a1 as the rollers 73 are formed on the outer peripheral surface 71a of the inner ring 71, and the inner peripheral surface 72a of the outer ring 72 is formed in a cylindrical surface. . Between the cam surface 71a1 of the inner ring 71 and the cylindrical surface 72a of the outer ring 72, a plurality of wedge-shaped spaces S are formed in the circumferential direction (eight locations).
FIG. 6 is an enlarged cross-sectional view showing a main part of the one-way clutch.
The rollers 73 are individually arranged in each wedge-shaped space S. The rollers 73 are urged by the elastic member 75 in the direction in which the wedge-shaped space S is narrowed. The outer peripheral surface of the roller 73 is a contact surface 73a that contacts the cam surface 71a1 of the inner ring 71 and the inner peripheral surface 72a of the outer ring 72, and the contact surface 73a is formed straight in the width direction (axial direction). .

  In the one-way clutch 7 configured as described above, when the rotational speed of the input rotating body 5 exceeds the rotational speed of the output rotating body 6 due to the input rotating body 5 rotating at an increased speed, the inner ring 71 is An attempt is made to rotate relative to the outer ring 72 in one direction (counterclockwise direction in FIG. 4; arrow a direction in FIG. 6). In this case, due to the biasing force of the elastic member 75, the roller 73 slightly moves in the direction in which the wedge-shaped space S is narrowed (the right direction in FIG. 6), and the contact surface 73a of the roller 73 is the outer peripheral surface 71a of the inner ring 71 ( The cam surface 71 a 1; the meshed surface) and the inner peripheral surface (meshed surface) 72 a of the outer ring 72 are pressed against each other, and the roller 73 is meshed between the inner and outer rings 71 and 72. Thereby, the inner and outer rings 71 and 72 can be integrally rotated in the one direction a, and the input rotating body 5 and the output rotating body 6 can be connected so as to be integrally rotatable.

  Further, when the input rotator 5 is rotated at a constant speed after the accelerated rotation and the rotation speed of the input rotator 5 is the same as the rotation speed of the output rotator 6, the rollers 73 are connected to the inner and outer rings 71 and 72. It is held in a state of being engaged with each other. Therefore, the one-way clutch 7 maintains the integral rotation of the inner and outer rings 71 and 72 in the one direction, and the input rotator 5 and the output rotator 6 continue to rotate integrally.

On the other hand, when the rotational speed of the input rotator 5 is lower than the rotational speed of the output rotator 6 due to the input rotator 5 rotating at a reduced speed, the inner ring 71 moves in the other direction (the timepiece of FIG. Rotation direction; direction of arrow b in FIG. In this case, the roller 73 slightly moves in the direction in which the wedge-shaped space S widens against the urging force of the elastic member 75, so that the engagement between the roller 73 and the inner and outer rings 71, 72 is released. . In this way, the connection between the input rotator 5 and the output rotator 6 is cut off by releasing the meshing of the rollers 73.
The outer ring inner peripheral surface 72a forming each wedge-shaped space S is constituted by a part of a cylindrical surface (arc surface) that is continuous in the circumferential direction, but an arc surface that is not continuous in the circumferential direction, for example, the circumferential direction It may be an independent circular arc surface in which a flat surface or an inflection point is interposed between the inner peripheral surface 72a of the outer ring of the wedge-shaped space S adjacent thereto.

  In the input rotating body 5, the inner ring 71 of the one-way clutch 7 is fitted to the shaft portion 51 with an interference with a predetermined interference. Therefore, both of them can be rotated together by the tightening force of the inner ring 71 with respect to the shaft portion 51. Further, the tightening force of the inner ring 71 with respect to the shaft portion 51 is increased by the engagement between the roller 73 and the inner and outer rings 71 and 72. Hereinafter, this operation will be described in detail.

  As shown in FIG. 6, when the inner ring 71 tries to rotate relative to the outer ring 72 in the direction of arrow a in FIG. 6, the roller 73 is engaged with the cam surface 71 a 1 and the outer ring inner peripheral surface 72 a, As shown in FIG. 8, the loads Fa and Fb are received from the inner peripheral surface 72a of the outer ring, and the cam surface 71a1 of the inner ring 71 receives vertical component loads Fa1 and Fb1, which are component forces of the loads Fa and Fb, from the rollers 73. Therefore, the tightening force of the inner ring 71 against the shaft portion 51 is increased by the vertical component loads Fa1 and Fb1.

Therefore, the torque (transmission torque) T2 that can be transmitted from the shaft portion 51 to the inner ring 71 by the tightening force (hereinafter also referred to as “initial tightening force”) due to the fitting between the shaft portion 51 and the inner ring 71 is the wind power generator 1. Than the maximum transmission torque T1max to be transmitted from the shaft portion 51 to the inner ring 71 when the load torque (the power generation torque or inertia torque for rotating the rotor 42 of the generator 4) is maximized. Can be small. That is, T2 and T1max are
T1max> T2 (1)
The relationship can be set.

Also, T2 and T3 when the transmission torque that can be transmitted from the shaft portion 51 to the inner ring 71 by the tightening force (hereinafter also referred to as “additional tightening force”) between the rollers 73 and the inner and outer rings 71 and 72 is T3. Is always larger than the minimum transmission torque T1 necessary for operating the wind turbine generator 1. That is,
T1 <T2 + T3 (2)
In particular, the transmission torque T3max that can be transmitted from the shaft portion 51 to the inner ring 71 with an additional tightening force when the load torque becomes maximum satisfies the following conditions.
T1max <T2 + T3max (3)

The relationship between the above load torque and each of the transmission torques T1 to T3 is as shown in the graph of FIG. The maximum load torque mentioned above refers to the maximum load torque assumed as a design condition for the wind turbine generator 1, and when the wind turbine generator 1 breaks down or due to abnormal weather, sudden fluctuations in wind speed exceeding the assumptions occur. It is not an excessive load torque that occurs when it occurs.
By satisfying the above relationships (1) to (3), the initial tightening force due to the fitting of the shaft portion 51 and the inner ring 71 can be made as small as possible, and the tightening necessary for the fitting of both of them. The allowance can be reduced, and the internal stress (especially the stress in the circumferential direction) generated in the inner ring 71 by the fitting can be reduced. By reducing the internal stress of the inner ring 71, the durability of the inner ring 71 can be improved, and the life of the one-way clutch 7 and thus the shaft coupling device 9 can be increased. In addition, the interference between the shaft part 51 and the inner ring 71 can be set to 10 μm at the minimum.

  If the inner ring 71 of the one-way clutch 7 is omitted and a cam surface is formed directly on the shaft portion 51, stress concentration of the inner ring 71 due to the fitting as described above can be suppressed, which is preferable. However, since the one-way clutch 7 used in the wind turbine generator 1 is large as in this embodiment, it is difficult to form a cam surface directly on the shaft portion 51, which is not realistic. Therefore, it is most effective to set the relationship between the transmission torques T1 to T3 and the load torque as in the above (1) to (3).

  On the other hand, if the tightening force due to the engagement between the rollers 73 and the inner and outer rings 71 and 72 is excessively increased as the load torque is increased, the load on the inner ring 71 is increased, and the durability may be reduced. Therefore, in the present embodiment, as the load torque increases, the increase in the vertical component load applied from the roller 73 to the inner ring 71 (cam surface 71a1) with respect to the increase in the load torque is reduced, and the burden on the inner ring 71 is made possible. Can be made small.

  Specifically, as shown in FIG. 6, the outer ring inner peripheral surface 72 a is formed in an arcuate surface, and thus the wedge angle increases as the wedge-shaped space S becomes narrower. FIG. 8A shows a state in which the wedge-shaped space S is relatively wide and the roller 73 is located in a region where the wedge angle θa is small, and FIG. 8B shows that the wedge-shaped space S is relatively narrow. A state is shown in which the rollers 73 are located in a region where the wedge angle θb is large.

Further, the roller 73 is positioned in a wide area of the wedge-shaped space S because the roller 73 and the inner and outer rings 71 and 72 are engaged at the initial stage, for example, from the non-rotating state to the cut-in wind speed (the minimum wind speed necessary for power generation). ), And when the load torque is small, such as when the rotation is constant and stable at the cut-in wind speed, the roller 73 is positioned in a narrow region of the wedge-shaped space S. This is the case when the load torque is high when the wind speed is higher than the rated wind speed and the rated output is reached. The cut-in wind speed may be an instantaneous wind speed or an average wind speed for a predetermined time.
Therefore, in FIG. 8, the loads Fa and Fb applied to the rollers 73 from the inner peripheral surface 72a of the outer ring are:
Fa <Fb (4)
There is a relationship.

  8 (b), the ratio (Fb / Fb1) of the vertical component load Fb1 to the load Fb applied to the roller 73 from the outer ring inner peripheral surface 72a is the vertical component load relative to the load Fa in FIG. 8 (a). It becomes smaller than the ratio of Fa1 (Fa / Fa1). Therefore, even if the load torque increases, the vertical component load Fb1 does not increase so much, and the burden on the inner ring 71 can be reduced.

The wedge angle θa when the initial load torque of meshing between the rollers 73 and the inner and outer rings 71 and 72 is applied, and the wedge angle θb when the maximum load torque is applied are:
1.0 ° <θb−θa <1.5 ° (5)
The relationship is set.
The wedge angle θa is preferably in the range of 4 ° to 9 °, and the wedge angle θb is preferably in the range of 5.5 ° to 10 °. If the wedge angle θa is smaller than 4 °, the vertical component load Fa1 applied to the cam surface 71a1 from the roller 73 may be increased more than necessary. If the wedge angle θa exceeds 9 °, the other wedge angle This is because θb becomes too large, and the engagement between the roller and both peripheral surfaces may be insufficient. If the wedge angle θb is smaller than 5.5 °, the other wedge angle θa becomes too small, and the vertical component load Fa1 applied from the roller 73 to the cam surface 71a1 may increase more than necessary. This is because if the wedge angle θb exceeds 10 °, the engagement between the rollers 73 and the inner and outer rings 71 and 72 may be insufficient.

The ratio between the wedge angles θa and θb is
1.1 <θb / θa <1.4 (6)
(More preferably, 1.11 <θb / θa <1.38)
Is set to
By setting the wedge angles θa and θb in the relationship as described above, the shaft 51 and the inner ring 71 are in contact between the initial stage of meshing between the roller 73 and the inner ring 71 and the outer ring 72 until the load torque becomes maximum. Torque can be transmitted reliably and the burden on the inner ring 71 can be reduced.

  The above relationships (5) and (6) are related to the inner diameter of the outer ring 72, the outer diameter of the roller 73, and the P.P. C. D, and can be set by adjusting the distance between the inner peripheral surface 72a of the outer ring and the cam surface 71a1. Further, the number of rollers 73 in the one-way clutch 7 is preferably set to 4 to 8. When the number of the rollers 73 exceeds 8, the loads Fa and Fb from the inner peripheral surface 72a of the outer ring to the rollers 73 are dispersed, and the vertical component loads Fa1 and Fb1 from the rollers 73 to the cam surface 71a1 are reduced, so that the shaft portion This is because there is a possibility that sufficient tightening force of the inner ring 71 with respect to 51 cannot be obtained. Further, when the number of rollers 73 is less than four, the tightening force of the inner ring 71 with respect to the shaft portion 51 becomes too large, and the local load on the inner ring 71 is increased.

  In FIG. 5, the pair of rolling bearings 8 are respectively disposed between the shaft portion 51 of the input rotator 5 and the cylindrical portion 61 of the output rotator 6, so that the input rotator 5 and the output rotator 6 are relative to each other. It is rotatably supported. The rolling bearings 8 are arranged adjacent to each other on both sides in the axial direction of the one-way clutch 7 via washers (positioning tools) 91.

The rolling bearing 8 includes an inner ring 81 and an outer ring 82 as raceway rings, a plurality of cylindrical rollers (rolling elements) 83 disposed between the inner ring 81 and the outer ring 82, and a plurality of cylindrical rollers 83. It consists of a cylindrical roller bearing provided with a cage 84 that holds the gap in the direction.
The inner ring 81 has an inner ring raceway surface 81a formed on the outer periphery, and an inner ring flange 81b formed to project radially outward on both axial sides of the inner ring raceway surface 81a. Both end surfaces of the cylindrical roller 83 are in sliding contact with the inner surface of each inner ring collar 81b. Further, the inner ring flange 81b adjacent to the one-way clutch 7 is more than the inner ring 71 of the one-way clutch 7 so that the radially outer end thereof is positioned on the axial direction side of the retainer 74 of the one-way clutch 7. Projects radially outward.

  A region A and a region C at both ends in the axial direction of the cylindrical portion 61 in the output rotator 6 serve as an outer ring 82 of the rolling bearing 8, and an outer ring raceway surface 82 a of the outer ring 82 is formed on each inner peripheral surface of the regions A and C. Is formed. A cylindrical roller 83 is disposed between the outer ring raceway surface 82a and the inner ring raceway surface 81a so as to be able to roll. Therefore, the cylindrical portion 61 of the output rotator 6 serves as the outer ring 72 of the one-way clutch 7 and the outer ring 82 of the rolling bearing 8, and the outer ring inner peripheral surface 72 a of the one-way clutch 7 and the outer ring raceway surface of the rolling bearing 8. 82a has the same inner diameter. In other words, the outer ring 72 of the one-way clutch 7 and the outer ring 82 of the rolling bearing 8 are integrally formed.

  The washer 91 is formed by forming a metal thin plate material such as SPCC into a ring shape, and the axial thickness dimension of the cross-sectional shape is smaller than the radial width dimension. The washer 91 is fitted (freely fitted) to the outer peripheral surface of the shaft portion 51 of the input rotator 5 and is sandwiched between the inner ring 71 of the one-way clutch 7 and the inner ring 81 of the rolling bearing 8. Further, the washer 91 protrudes radially outward from the inner ring 71 of the one-way clutch 7 and can come into contact with the axial side surface of the cage 74 of the one-way clutch 7.

  Therefore, the retainer 74 of the one-way clutch 7 is positioned with respect to the axial direction by the washer 91. Moreover, since the washer 91 is arrange | positioned between the holder | retainer 74 of the one-way clutch 7 and the holder | retainer 84 of the rolling bearing 8, both do not contact directly. Therefore, it is possible to prevent wear and seizure associated with the contact between the two retainers 74 and 84. Further, by holding the washer 91 between the inner ring 71 of the one-way clutch 7 and the inner ring 81 of the rolling bearing 8, even if the washer 91 is loosely fitted to the shaft portion 51, the washer 91 is firmly fixed. be able to. Therefore, the washer 91 can be formed as thin as possible, and the retainer 74 can be positioned reliably. Further, the flange 81b formed on the inner ring 81 of the rolling bearing 8 protrudes radially outward from the inner ring 71 of the one-way clutch 7 and is disposed on the axial direction side of the retainer 74. The washer 91 can be backed up by the collar portion 81b, and the washer 91 can be supported more firmly. Therefore, the washer 91 can be formed thinner, and an increase in the axial dimension of the one-way clutch 7 accompanying the provision of the washer 91 can be suppressed.

  The washer 91 is disposed with a gap serving as a grease passage between the cylindrical portion 61 so as not to hinder the flow of grease between the one-way clutch 7 and the rolling bearing 8.

FIG. 10 is an explanatory view showing an assembly procedure of the shaft coupling device.
Hereinafter, the assembly procedure of the shaft coupling device 9 will be described with reference to FIG. First, as shown in FIG. 10A, one rolling bearing 8, a washer 91, an inner ring 71 of the one-way clutch 7, and an annular portion 76 of the retainer 74 are formed on the outer peripheral surface of the shaft portion 51 of the input rotating body 5. The column portion 77, the annular portion 76, the washer 91, and the other rolling bearing 8 are attached in sequence. At this time, the rolling bearing 8 is in a state in which the cage 84 and the cylindrical roller 83 are assembled to the inner ring 81 in advance. The inner ring 81 of the rolling bearing 8 and the inner ring 71 of the one-way clutch 7 are attached by being fitted to the outer peripheral surface 51a of the shaft portion 51 by shrink fitting or cold fitting. Therefore, the inner rings 81 and 71 are firmly fitted to the shaft portion 51 with an interference fit with a predetermined allowance. The retainer 74 is attached by first loosely fitting one annular portion 76 to the outer peripheral surface of the inner ring 71, and one fitting portion of the column portion 77 in each recess 76 a (see FIG. 7) of the annular portion 76. 77c (see FIG. 7) is fitted, and then the other annular portion 76 is loosely fitted to the inner ring 71 while the concave portion 76a is fitted to the other fitting portion 77c of the column portion 77.

  Next, as shown in FIG. 10B, the seal receiving member 101 is fitted to the outer peripheral surface of the shaft portion 51 by shrink fitting or the like. Further, the elastic member 75 and the roller 73 of the one-way clutch 7 are attached to the cage 74.

  Next, as shown in FIG. 10C, the cylindrical portion 61 of the output rotator 6 is mounted on the radially outer side of the cylindrical roller 83 of the rolling bearing 8 and the roller 73 of the one-way clutch 7 mounted on the input rotator 5. To do. At this time, as shown in FIG. 6, the roller 73 of the one-way clutch 7 is pressed by the elastic member 75 in the pocket 78 and is positioned on the end side of the cam surface 71 a 1. The inner circumferential surface of the cylindrical portion 61, that is, the outer ring inner circumferential surface 72 a of the one-way clutch 7 protrudes radially outward. Therefore, when the cylindrical portion 61 is fitted to the outer side in the radial direction of the roller 73, the elastic member 75 is in a state where the tip end portion (lower end portion in the drawing) of the cylindrical portion 61 is in contact with the end portion of the roller 73. The cylindrical portion 61 is rotated in a direction opposite to the direction in which 73 is urged.

As a result, the roller 73 can be moved back inward in the radial direction while moving to the center side of the cam surface 71 a 1, and the inner peripheral surface of the cylindrical portion 61 can be easily fitted to the outer side in the radial direction of the roller 73. Become.
Moreover, since the wind power generator 1 is large and the individual components of the shaft coupling device 9 are also enlarged, the assembly work is performed in an unstable state in which the components are suspended by a crane. Therefore, when the cylindrical portion 61 of the output rotator 6 is mounted on the radially outer side of the roller 73 of the one-way clutch 7 mounted on the input rotator 5, the tip of the cylindrical portion 61 and the roller 73 of the one-way clutch 7 are mounted. It becomes difficult to align the position with the end of the. Since the roller 73 is pressed by the elastic member 75 and is positioned on the circumferential end side of the cam surface 71a1, the roller 73 is attached to the cylindrical portion 61 on the radially outer side of the roller 73. Although it is necessary to bring it closer to the center in the circumferential direction of the cam surface 71a1, the assembling work becomes extremely difficult when it is difficult to align the tip of the cylindrical portion 61 and the end of the roller 73 of the one-way clutch 7. In the present embodiment, a tapered surface 61 b that expands the inner diameter is formed on the inner peripheral surface of the tip of the cylindrical portion 61. The tapered surface 61 b is pressed against the end of the roller 73 to facilitate alignment with the end of the cylindrical portion 61 and the end of the cylindrical portion 61, and the end of the cylindrical portion 61 is brought into contact with the end of the roller 73. Easy to bite. Further, since the cylindrical portion 61 can be easily held in a state where the tapered surface 61b is pressed against the end portion of the roller 73, the roller 73 can be easily moved to the center side in the circumferential direction of the cam surface 71a1. The attachment can be performed more easily.

The outer peripheral edge 73e at the axial end of the roller 73 of the one-way clutch 7 is preferably formed with a tapered surface so that it can be easily aligned with the tapered surface 61b when the cylindrical portion 61 is assembled. Further, by forming a taper surface or an R surface on the outer peripheral surface of the axial end portion of the shaft portion 51 and the inner peripheral surface of the axial ends of the inner rings 71 and 81 fitted to the shaft portion 51, Centering and assembly can be easily performed.
Finally, as shown in FIG. 10 (d), the key 53 is attached to the key groove 51 b of the shaft portion 51, and the flange portion 52 a is fitted to the outer peripheral surface 51 a of the shaft portion 51.

  As a method of assembling the one-way clutch 7, first, one rolling bearing 8 is assembled to the outer peripheral portion of the shaft portion 51 of the input rotating body 5, and then the cylindrical portion 61 of the output rotating body 6 is assembled. A method of inserting a pre-assembled one-way clutch between the cylindrical portion 61 is conceivable. However, since the one-way clutch used in the wind power generator 1 is large, it is very difficult to insert the one-way clutch into the narrow space between the shaft portion 51 and the cylindrical portion 61 in a state where the one-way clutch is assembled in advance. It is. In addition, the roller 73 protrudes radially outward from the inner peripheral surface 72a of the cylindrical portion 61 by the action of the elastic member 75 and the cam surface 71a1, so that the one-way clutch 7 must be inserted into the cylindrical portion 61 inside. The roller 73 must be pressed inward in the radial direction, and the operation becomes extremely complicated.

  On the other hand, in the assembling method of this embodiment described with reference to FIG. 10, the one-way clutch 7 and the rolling bearing 8 except for the outer rings 72 and 82 are output in a state where they are assembled to the shaft portion 51 of the input rotating body 5. Since the rotating body 6 is assembled and the plurality of rollers 73 can be simultaneously retracted radially inward by rotating the cylindrical portion 61 of the output rotating body 6 during the assembly, the shaft coupling device 9 can be easily operated. Can be assembled.

  In the large-scale wind turbine generator 1 with a rated output exceeding 1 MW, the shaft diameters of the output shaft 35 of the speed increaser 3 and the drive shaft 41 of the generator 4 are also increased, and the weight of the shaft coupling device 9 is inevitably required. Become bigger. Therefore, when assembling the shaft coupling device 9, it is very difficult for a person to lift and work directly. For example, in the wind turbine generator 1 having a 2 MW class generator 4, the weight of the shaft coupling device 9 may exceed 100 kg, and components suspended by a crane are assembled in an unstable state or a special jig is used. For example, the labor required for the assembly work becomes very large. Therefore, assembling the shaft coupling device 9 as described above is extremely effective.

  In addition, the assembly procedure until it reaches FIG.10 (c) can be changed suitably. For example, the inner ring 81, the cage 84, and the cylindrical roller 83 of the rolling bearing 8 may be separately assembled to the shaft portion 51.

  As shown in FIG. 1, the wind turbine generator 1 of the present embodiment is provided with a cover member (shielding means) 92 that covers the shaft coupling device 9. The cover member 92 is made of elastically deformable synthetic resin, rubber, or the like. As shown in FIG. 3, the cover member 92 is formed in a cylindrical shape, provided with connecting portions 93 and 94 at both ends in the axial direction, and a bellows portion 95 between the connecting portions 93 and 94. Is provided. One connecting portion 93 is fixed to the outer peripheral surface of drive shaft 41 (or may be flange portion 41a) by a fixing band or the like. The other connecting portion 94 is connected by engaging with the flange portion 35 c 1 of the output shaft 35. The bellows portion 95 can be expanded and contracted in the axial direction and bent or bent in the radial direction.

FIG. 12 is an enlarged cross-sectional view of the connecting portion of the cover member.
The connecting portion 94 includes a cored bar 94a having an L-shaped cross section and an elastic member 94b bonded to the outer surface of the cored bar 94a. In addition, a sliding member 94c that contacts the side surface of the flange portion 35c1 on the side of the speed increaser 3 is provided at the distal end portion of the connecting portion 94. As the sliding member 94c, a member having a small sliding resistance with respect to the flange portion 35c1, for example, a member having a friction coefficient reduced by coating the surface of a metal plate is used. The sliding member 94c is pressed against the flange portion 35c1 by the force that the bellows portion 95 contracts in the direction of the arrow c, and the flow of the airflow inside and outside the cover member 92 is suppressed by the sealing action of the sliding member 94c. ing.

  The wind power generator 1 installed on the coast or on the ocean operates by receiving a wind containing a large amount of salt. However, if an external air current enters the equipment in the nacelle, problems such as metal corrosion due to salt damage occur, resulting in a large durability. Affect. In the wind turbine generator 1 of the present embodiment, the shaft coupling device 9 is covered with a cover member 92, and entry of foreign matter and airflow into the shaft coupling device 9 is suppressed. Therefore, it is possible to prevent deterioration of the function of the shaft coupling device 9 due to salt damage or the like, particularly deterioration of the function of the one-way clutch 7.

  The cover member 92 has one end in the axial direction fixed to the drive shaft 41, but the other end in the axial direction is connected to the output shaft 35 so as to be relatively rotatable, so that the cover member 92 is driven with the output shaft 35 by the one-way clutch 7. The cover member 92 is not twisted by the relative rotation of the shaft 41. Further, since the sliding member 94c of the connecting portion 94 is pressed against the flange portion 35c1 by utilizing the elastic deformation (contraction) of the bellows portion 95, relative rotation of both is allowed while suppressing intrusion of foreign matter and airflow. be able to.

  According to the wind power generator 1 of the present embodiment, the wind turbine generator 1 is disposed between the input rotator 5 that rotates together with the output shaft 35 of the speed increaser 3 and the output rotator 6 that rotates together with the drive shaft 41 of the generator 4. When the rotational speed of the input rotator 5 falls below the rotational speed of the output rotator 6 by the one-way clutch 7, the connection between the input rotator 5 and the output rotator 6 can be disconnected. That is, even if the rotational speed of the output shaft 35 rapidly decreases via the main shaft 2 due to a decrease in wind power, the rotation due to the inertia of the rotor 42 of the generator 4 is transmitted to the output shaft 35 via the drive shaft 41. Can be prevented. As a result, it is possible to suppress a reduction in the radial load acting on the roller bearing 38 supporting the output shaft 35 and a rotation delay of the cylindrical roller 38c associated therewith. Accordingly, when the rotational speed of the main shaft 2 suddenly increases due to a change in wind force from this state and a high load is applied to the cylindrical roller 38c, the cylindrical roller 38c becomes difficult to slip on the contact surface with the inner ring 38a. Smearing can be effectively suppressed.

Further, by preventing the rotation due to the inertia of the rotor 42 from being transmitted to the output shaft 35, the load acting on the roller bearings 36a, 36b, 37a, 37b, 38, 39, etc. of the speed increaser 3 can be reduced. Can do. As a result, the gears 31b and 31c of the planetary gear mechanism 31 and the shafts 33 to 35 of the high-speed gear mechanism 32 and the roller bearings 36a, 36b, 37a, 37b, 38, and 39 can all be downsized. The speed increaser 3 can be reduced in weight and can be manufactured at low cost.
Further, by disconnecting the connection between the input rotator 5 and the output rotator 6, the rotor 42 of the generator 4 continues to rotate due to inertia without suddenly decelerating, so the average rotational speed of the rotor 42 is increased. Can do. Thereby, the power generation efficiency of the generator 4 can be improved.

  Further, since a rolling bearing 8 is disposed between the input rotator 5 and the output rotator 6 so as to be relatively rotatable with each other, the roller 73 and the inner and outer rings 71 and 72 in the one-way clutch 7 are arranged. When the gap between the roller 73 and the inner and outer rings 71 and 72 is generated in the wedge-shaped space S, the input rotating body 5 and the output rotating body 6 are radially connected to each other by the rolling bearing 8. It is possible to prevent relative movement. Therefore, it is possible to prevent the input rotator 5 and the output rotator 6 from rattling in the radial direction during the operation of the wind turbine generator 1.

  The outer ring inner peripheral surface 72a of the one-way clutch 7 and the outer ring raceway surface 82a of the rolling bearing 8 are formed on the inner peripheral surface of the cylindrical portion 61 of the output rotating body 6 that is a common member. Therefore, the output rotating body 6 can be used as the outer ring 72 of the one-way clutch 7 and the outer ring 82 of each rolling bearing 8. Thereby, the structure of the wind power generator 1 whole can be simplified.

  The output rotator 6 is detachably fixed to the drive shaft 41 of the generator 4 and is movably disposed in the axial direction with respect to the input rotator 5, so that the output rotator 6 is connected to the drive shaft. The output rotator 6 can be removed from the input rotator 5 by removing it from 41 and moving it in the axial direction relative to the input rotator 5. Thereby, since the outer ring 72 of the one-way clutch 7 and the outer ring 82 of the rolling bearing 8 can be removed at the same time, the maintenance work of the one-way clutch 7 and the rolling bearing 8 can be easily performed. At this time, since the generator 4 does not need to be moved, the maintenance work can be performed more easily.

  As shown in FIG. 5, the input rotator 5 and the output rotator 6 are provided with gaps s2 and s3, and the engagement element 73 of the one-way clutch 7 and the rolling element 83 of the rolling bearing 8 are made of cylindrical rollers. Relative movement in the axial direction is allowed due to the fact that the outer ring inner circumferential surface 72a and the outer ring raceway surface 82a on which the cylindrical rollers 73 and 83 roll are formed on a cylindrical surface (arc surface). Has been. Therefore, even if the output shaft 35 and the drive shaft 41 expand and contract in the axial direction due to a change in the surrounding state, for example, a temperature change (the axial distance between both axes varies), the axis between the input rotator 5 and the output rotator 6 The expansion and contraction can be absorbed by relative movement in the direction. Thereby, it is possible to suppress an axial load from being applied to a member (such as a rolling bearing) that supports the output shaft 35 and the drive shaft 41.

  Further, the relative movement in the axial direction between the input rotator 5 and the output rotator 6 causes the outer ring inner peripheral surface 72 a of the one-way clutch 7 and the outer ring raceway surface 82 a of the rolling bearing 8 to move in the axial direction with respect to the cylindrical rollers 73 and 83. When moved, the outer ring inner circumferential surface 72a and the outer ring raceway surface 82a are displaced in the axial direction. In particular, since the wind power generator 1 is large, the amount of displacement is inevitably large. In order to deal with such a positional deviation, the inner peripheral surface of the cylindrical portion 61 is previously subjected to the necessary surface treatment on the outer ring cylindrical surface 72a and the outer ring raceway surface 82a within a range including the assumed positional deviation amount. Is preferred. In addition, this positional deviation amount assumes a temperature change region (for example, −40 ° C. to 60 ° C.) from the environmental temperature in which the wind power generator 1 is used, the temperature in the nacelle in consideration of the heat generation amount of the generator 4 and the like. The amount of expansion and contraction of each member in this temperature change region can be estimated by calculating or experimenting. In addition, the gaps s2 and s3 are preferably set to dimensions larger than the axial extension amount of each axis at the upper limit (maximum temperature) of the assumed temperature change range. Further, as the surface treatment of the outer ring inner peripheral surface 72a and the outer ring raceway surface 82a, for example, surface modification treatment such as carbonitriding treatment, coating treatment such as blackening treatment or DLC coating may be used. Further, it may be a heat treatment such as quenching or tempering.

  As shown in FIG. 2, in the case where a brake 44 for braking the drive shaft 41 is provided, the one-way clutch 7 and the shaft coupling device 9 incorporating this are arranged between the speed increaser 3 and the brake 44. It is preferred that Assuming that the one-way clutch 7 is disposed between the brake 44 and the generator 4, even if the brake 44 is applied during rotation, the rotation on the gearbox 3 side only decelerates, and the generator 4 side This is because the rotation is continued and idled by the one-way clutch 7 and it is difficult to quickly stop the generator 4 when the generator 4 is abnormal.

  However, the one-way clutch 7 and the shaft coupling device 9 are not necessarily provided between the brake 44 and the generator 4, and are provided between the brake 44 and the generator 4 as shown in FIG. 16. It may be. When the brake for the output shaft 35 and the brake for the drive shaft 41 are provided, the one-way clutch 7 and the shaft coupling device 9 may be provided between the two brakes.

FIG. 13 is a cross-sectional view showing a shaft coupling device according to a second embodiment of the present invention, and FIG. 14 is an enlarged cross-sectional view showing a main part of the same-direction clutch 7.
In the shaft coupling device 9 of the present embodiment, a sprag is used as the engagement element 73. Further, the inner ring of the one-way clutch 7 is configured by the shaft portion 51 of the input rotating body 5, and the outer peripheral surface 71 a of the inner ring is configured by the outer peripheral surface 51 a of the shaft portion 51. The inner ring outer peripheral surface 71a is not formed with a cam surface as in the first embodiment, but is formed in a cylindrical surface.

The inner ring of the rolling bearing 8 is also constituted by the shaft portion 51 of the input rotating body 5, and the outer peripheral surface 81 a of the inner ring is constituted by the outer peripheral surface 51 a of the shaft portion 51.
One annular portion 76 in the retainer 74 of the one-way clutch 7 is formed with a protrusion 76b that protrudes radially outward. The protruding portion 76b is slidably fitted in a circumferential groove 61c1 formed on the inner peripheral surface of the cylindrical portion 61 of the output rotator 6, whereby the axial position of the cage 74 is regulated. Has been.

  Similarly, a protrusion 86b that protrudes radially outward is also formed on one annular portion 86 of the cage 84 of the rolling bearing 8. The protruding portion 86b is slidably fitted in a circumferential groove 61c2 formed on the inner peripheral surface of the cylindrical portion 61, whereby the axial position of the cage 84 is regulated.

  The sprag 73 includes a first contact surface 73b that contacts the outer peripheral surface 51a (inner ring outer peripheral surface 71a) of the shaft portion 51, and a second contact surface 73c that contacts the inner peripheral surface 72a of the outer ring 72 (cylindrical portion 61). The first contact surface 73b and the second contact surface 73c are each formed in a convex and substantially arc shape. Further, the distance between the first contact surface 73b and the second contact surface 73c that are in contact with the outer peripheral surface 51a of the shaft portion 51 and the inner peripheral surface 72a of the outer ring varies depending on the inclination of the sprag 73, and the shaft portion 51 is When rotated in the direction of arrow a, the sprag 73 tilts in the direction of arrow e, and the distance between the first contact surface 73b and the second contact surface 73c increases. Conversely, when the shaft 51 rotates in the direction of arrow b, the sprag 73 tilts in the direction opposite to the arrow e, and the distance between the first contact surface 73b and the second contact surface 73c decreases.

  When the distance between the first contact surface 73b and the second contact surface 73c is increased, the sprag 73 is engaged with the outer peripheral surface 51a of the shaft portion 51 and the inner peripheral surface 72a of the outer ring 72. When the distance between the contact surface 73b and the second contact surface 73c is reduced, the engagement between the sprag 73 and the outer peripheral surface 51a of the shaft portion 51 and the inner peripheral surface 72a of the outer ring 72 is released. Accordingly, when the shaft 51 is about to rotate relative to the outer ring 72 in the direction of the arrow a, the shaft 51 and the outer ring 72 are connected so as to be integrally rotatable, and the shaft 51 is connected to the outer ring 72 in the direction of the arrow b. When the shaft rotates relatively, the connection between the shaft 51 and the outer ring is cut off.

  In the present embodiment, in addition to the same effects as the first embodiment, it is not necessary to form a cam surface on the inner ring (shaft portion 51) of the one-way clutch 7, so that the manufacturing cost can be reduced. Further, since the shaft portion 51 can be used as the inner ring, the manufacturing cost can be further reduced, and the structure of the one-way clutch 7 can be simplified and the radial direction can be reduced. In addition, since the sprag 73 has higher rigidity and higher torque capacity than the roller, the radial and axial dimensions of the sprag 73 itself can be reduced. Therefore, the size in the radial direction and the axial direction of the one-way clutch 7 can be reduced, and the size can be reduced. Thus, by reducing the size of the one-way clutch 7, the entire shaft coupling device 9 can be reduced in the radial direction and the axial direction. Therefore, even when the space between the output shaft 35 of the speed increaser 3 and the drive shaft 41 of the generator 4 is narrow, the shaft coupling device 9 can be suitably arranged.

In the second embodiment, the sprag 73 and the cylindrical roller 83 are movable in the axial direction on the outer peripheral surface 51 a of the shaft portion 51, whereby the shaft between the input rotating body 5 and the output rotating body 6. Relative movement in the direction is allowed. Further, due to this relative movement, the inner ring outer peripheral surface 71a and the inner ring raceway surface 81a corresponding to the sprag 73 and the cylindrical roller 83 are displaced in the axial direction, but the inner ring outer peripheral surface 71a and the inner ring raceway surface 81a are assumed to have positions. It is preferable to perform necessary surface treatment (surface modification treatment, coating treatment, heat treatment, etc.) within a range including the deviation amount.
In the second embodiment, the inner ring may be fitted to the outer peripheral surface of the shaft portion 51 and the sprag 73 may be engaged with the outer peripheral surface of the inner ring. In this case, it is preferable that the shaft portion 51 and the inner ring are fitted with an interference fit so as to satisfy the above formulas (1) to (3).

The present invention is not limited to the above embodiment and can be implemented with appropriate modifications.
For example, although the output rotator 6 is disposed on the radially outer side of the input rotator 5, it may be disposed on the radially inner side of the input rotator 5, as shown in FIG. Specifically, the output rotator 6 may be provided with the shaft portion 65, the input rotator 5 may be provided with the cylindrical portion 54, and the cylindrical portion 54 may be disposed concentrically outside the shaft portion 65 in the radial direction. Further, the inner peripheral surface of the cylindrical portion 54 is used as an outer peripheral surface of the outer ring of the one-way clutch 7 and an outer ring raceway surface of the rolling bearing 8, and the one-way clutch 7 and the inner rings 71 of the rolling bearing 8 are connected to the shaft portion 65 of the output rotating body 6. 81 may be fitted.
In this case, the one-way clutch 7 may have an inner peripheral surface of the outer ring as a cam surface and an outer peripheral surface of the inner ring as a cylindrical surface. Further, in this case, an outer peripheral surface of the inner ring may be formed on the outer peripheral surface of the shaft portion 65 of the output rotating body 6, and the shaft portion 65 may also be used as the inner ring.

Furthermore, although the output rotating body is the outer ring of the one-way clutch and the outer ring of the rolling bearing, these outer rings may be provided as separate members with respect to the output rotating body.
Further, the rolling bearing disposed between the input rotator and the output rotator is a cylindrical roller bearing for moving the output rotator in the axial direction. However, when the output rotator is not moved in the axial direction, It may be a ball bearing.

The cage of the one-way clutch may be one in which the annular portion and the column portion are integrally formed of the same material, and the material may be a metal or a synthetic resin. As the synthetic resin material forming the cage, phenol resin, polyamide resin, PEEK (polyether ether ketone) resin, or the like can be used.
The wind power generator of the present invention is not limited to the horizontal axis type shown in FIG. 1, but may be the vertical axis type shown in FIG. Even in this case, a shaft coupling device 9 including a one-way clutch can be provided between the speed increaser 3 and the generator 4.

  The lid member 103 constituting the sealing means 10 may be attached to the shaft portion 51 of the input rotating body 5 by a fixing screw 103b as shown in FIG. In this case, the lid member 103 is not only configured as the sealing means 10, but also functions as a “detachment prevention member” that prevents the input rotating body 5 and the output rotating body 6 from coming off in the axial direction. By providing such a disengagement prevention member 103, the shaft coupling device 9 is assembled with a crane when the shaft coupling device 9 is assembled between the speed increaser 3 and the generator 4 or when the shaft coupling device 9 is transported for shipment. When the joint device 9 is lifted, the input rotator 5 and the output rotator 6 can be prevented from separating. Further, when only a function as a detachment preventing member is required, the seal member 104 can be omitted.

The present invention is not limited to one in which the output shaft 35 of the speed increaser 3 and the drive shaft 41 of the generator 4 are connected via the shaft coupling device 9, but one directly between the output shaft 35 and the drive shaft 41. The structure which assembled | attached the direction clutch 7 may be sufficient.
Further, the output shaft 35 in the present invention can include a portion connected to the output shaft 35 in the shaft coupling device 9, and similarly, the drive shaft 41 is a portion connected to the drive shaft 41 in the shaft coupling device 9. Can be included.

  1: wind power generator, 3: booster, 4: generator, 5: input rotor (inner rotor), 6: output rotor (outer rotor), 7: one-way clutch, 35: output shaft, 41: drive shaft, 71: inner ring (ring body), 71a: inner ring outer peripheral surface, 72a: outer ring inner peripheral surface, 73: engagement element (roller, sprag)

Claims (5)

A speed increaser that accelerates rotation of the main shaft generated by wind power and outputs it from the output shaft, and an input shaft that rotates using the rotation of the output shaft as an input, and rotation of the rotor that rotates integrally with the input shaft A generator that generates electric power and the output shaft and the input shaft are provided between the output shaft and the input shaft, and the output shaft and the input shaft are integrated in a state where the rotational speed of the output shaft exceeds the rotational speed of the input shaft. A one-way clutch that is rotatably connected and that disconnects the connection between the output shaft and the input shaft in a state where the rotational speed of the output shaft is lower than the rotational speed of the input shaft;
The one-way clutch is disposed opposite to a ring body fitted to a rotating body that rotates together with the output shaft and a radially outer side or a radially inner side of a peripheral surface of the ring body, and is provided on the input shaft side. And the output shaft and the input shaft are integrally rotated by engaging the engagement members with the peripheral surfaces. The connection is possible, and the connection is cut off by releasing the engagement;
The maximum transmission torque T1max to be transmitted from the rotating body to the ring when the load torque for operating the generator is maximum, and the tightening force due to the fitting of the rotating body and the ring Transmission torque T2 that can be transmitted from the rotating body to the ring body,
T1max> T2
In relation to
The minimum required transmission torque T1 to be transmitted from the rotating body to the ring body in order to operate the generator, and the tightening force generated by the engagement of the engaging element with the peripheral surface of the ring body, from the rotating body. The transmission torque T3 that can be transmitted to the ring body and the transmission torque T2 are:
T1 <T2 + T3
A wind power generator characterized by the following relationship. A speed increaser that accelerates rotation of the main shaft generated by wind power and outputs it from the output shaft, and an input shaft that rotates using the rotation of the output shaft as an input, and rotation of the rotor that rotates integrally with the input shaft A generator that generates electric power and the output shaft and the input shaft are provided between the output shaft and the input shaft, and the output shaft and the input shaft are integrated in a state where the rotational speed of the output shaft exceeds the rotational speed of the input shaft. A one-way clutch that is rotatably connected and that disconnects the connection between the output shaft and the input shaft in a state where the rotational speed of the output shaft is lower than the rotational speed of the input shaft;
The one-way clutch is disposed on the output shaft side so as to be opposed to a ring body fitted to a rotating body that rotates together with the input shaft, and a radially outer side or a radially inner side of a circumferential surface of the ring body. And the output shaft and the input shaft are integrally rotated by engaging the engagement members with the peripheral surfaces. The connection is possible, and the connection is cut off by releasing the engagement;
The maximum transmission torque T1max to be transmitted from the rotating body to the ring when the load torque for operating the generator is maximum, and the tightening force due to the fitting of the rotating body and the ring Transmission torque T2 that can be transmitted from the rotating body to the ring body,
T1max> T2
In relation to
The minimum required transmission torque T1 to be transmitted from the rotating body to the ring body in order to operate the generator, and the tightening force generated by the engagement of the engaging element with the peripheral surface of the ring body, from the rotating body. The transmission torque T3 that can be transmitted to the ring body and the transmission torque T2 are:
T1 <T2 + T3
A wind power generator characterized by the following relationship.   The wind turbine generator according to claim 1 or 2, wherein a tightening margin between the rotating body and the ring body is 10 µm or more.   The wind power generator according to any one of claims 1 to 3, wherein four to eight engagement elements are provided in a circumferential direction.   The wind turbine generator according to any one of claims 1 to 4, wherein the one-way clutch is incorporated in a shaft coupling device that connects the output shaft and the input shaft so as to be integrally rotatable.

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