JP5857561B2 - Power generator - Google Patents

Description

  The present invention relates to a power generator that drives a generator by increasing the rotation of a main shaft by an external force with a speed increaser.

  2. Description of the Related Art Conventionally, as a wind power generator, there is a wind power generator that uses a speed increasing device to drive a generator by receiving wind power from a blade, rotating a main shaft connected to the blade, and increasing the rotation speed of the main shaft. . As shown in FIG. 5, the speed increaser 202 inputs the rotation of the planetary gear mechanism 203 that receives the rotation of the main shaft 200 and increases the rotation, and further receives the rotation increased by the planetary gear mechanism 203. Is provided with a high-speed gear mechanism 204 that speeds up the rotation, and an output shaft 205 that outputs the rotational torque of the high-speed gear mechanism 204.

In the planetary gear mechanism 203, when the input shaft 203a connected to the main shaft 200 so as to rotate integrally is rotated, the planet carrier 203b is rotated, so that the sun gear 203d is rotated at an increased speed via the planetary gear 203c. It is transmitted to the low-speed shaft 204a of the high-speed gear mechanism 204.
When the low-speed shaft 204a rotates, the high-speed gear mechanism 204 rotates the intermediate shaft 204d through the low-speed gear 204b and the first intermediate gear 204c, and further outputs the output shaft through the second intermediate gear 204e and the high-speed gear 204f. 205 is rotated at a high speed.
As bearings that rotatably support the low-speed shaft 204a, the intermediate shaft 204d, and the output shaft 205 of the speed increaser 202, roller bearings 206 to 211 are frequently used (see, for example, Patent Document 1).

JP 2007-232186 A

In conventional wind turbine generators, in roller bearings that support high-speed rotating output shafts, smearing (a phenomenon in which surface seizure occurs) occurs on the rolling surfaces of the rollers and the raceways of the rotating wheels, and the life of the roller bearings is reduced. There was a problem of lowering.
This invention is made in view of such a situation, and provides the electric power generating apparatus which can suppress effectively that smearing generate | occur | produces in the roller bearing which supports the output shaft of a gearbox. With the goal.

  The inventor of the present application has made extensive studies on the mechanism of smearing. As a result, when the rotation speed of the main shaft rapidly decreases due to a decrease in wind power, the inertia of the heavy generator rotor causes the rotation speed of the generator drive shaft to exceed the rotation speed of the output shaft, so-called torque loss. (Load loss) occurs, and the radial load acting on the roller bearing that supports the output shaft is reduced by this torque loss, so that the roller and the roller that holds the roller retain it rather than the rolling friction resistance between the roller and the rotating wheel. It has been found that the roller rotation is delayed when the sliding frictional resistance with the container exceeds. From this state, when the rotational speed of the main shaft suddenly increases due to an increase in wind power, the increased inertial torque is applied and the radial load acting on the roller bearing that supports the output shaft increases. The inventors have obtained the knowledge that smearing occurs when the roller slides on the contact surface with the rotating wheel under high load and the contact surface is heated, and the present invention has been completed based on such knowledge.

That is, the present invention includes a main shaft that is rotated by an external force, a rotation transmission mechanism that receives and accelerates rotation of the main shaft, and a roller bearing that rotatably supports an output shaft that outputs rotational torque of the rotation transmission mechanism. And a generator that has a drive shaft that rotates with the rotation of the output shaft as an input, and that generates electric power with the rotation of a rotor that rotates integrally with the drive shaft. An input rotator provided to be rotatable integrally with the output shaft; and an output rotator provided to be integrally rotatable with the drive shaft and arranged concentrically on the radially inner side or radially outer side of the input rotator. And between the input rotator and the output rotator, the input rotator and the output rotator can be rotated together in a state where the rotation speed of the input rotator exceeds the rotation speed of the output rotator. Connected to the input A one-way clutch that cuts off the connection between the input rotator and the output rotator in a state in which the rotation speed of the body is lower than the rotation speed of the output rotator. A plurality of rollers individually disposed in a circumferential surface, a plurality of wedge-shaped spaces formed between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring, and the plurality of rollers at predetermined intervals along the circumferential direction. An annular cage that holds the inner ring outer peripheral surface and the outer ring inner peripheral surface, the input rotating body and the output rotating body are connected to each other so as to be integrally rotatable, and the meshing is released. And further comprising a rolling bearing disposed between the input rotator and the output rotator and supporting the input rotator and the output rotator so that they can rotate relative to each other. bearings, double A cylindrical roller bearing, and an inner ring collar portion with which the end surface of the cylindrical roller is in sliding contact, and the both end surfaces of the cage of the one-way clutch are in contact with the inner ring collar portion of the cylindrical roller bearing. A pair of adjacent ones are disposed adjacent to both axial sides of the one-way clutch so as to contact each other, and an inner peripheral surface of the outer ring of the one-way clutch is a cylindrical surface, and the cylindrical roller bearing is the cylindrical roller And the output rotating body is disposed on the radially outer side of the input rotating body, and the outer ring inner peripheral surface of the one-way clutch and the cylinder are arranged on the inner peripheral surface of the output rotating body. An outer ring raceway surface of the roller bearing is formed, and the output rotating body is detachably fixed to the drive shaft and is arranged to be movable in the axial direction with respect to the input rotating body. Features.

  According to the power generator configured as described above, when the rotational speed of the input rotating body exceeds the rotational speed of the output rotating body, the input rotating body and the output rotating body can be rotated integrally by the one-way clutch. When the rotational speed of the input rotator is lower than the rotational speed of the output rotator, the connection between the input rotator and the output rotator can be disconnected. That is, even if the rotational speed of the output shaft rapidly decreases through the main shaft due to a decrease in external force, it is possible to prevent the rotation due to the inertia of the rotor of the generator from being transmitted to the output shaft through the drive shaft. . Thereby, the reduction of the radial load which acts on the roller bearing which supports the output shaft, and the rotation delay of the roller accompanying this can be suppressed. Therefore, when the rotational speed of the main shaft suddenly increases due to a change in external force from this state and a high load is applied to the rollers, the rollers are less likely to slip on the contact surface with the rotating wheels, so smearing occurs in the roller bearings. Can be effectively suppressed.

In addition , when the meshing between the roller of the one-way clutch and the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring is released, a gap is generated between them, so that the input rotator and the output rotator have a diameter relative to each other. Relative movement in the direction can be prevented by the rolling bearing. Therefore, it is possible to prevent the input rotating body and the output rotating body from rattling in the radial direction during operation of the power generation device.

Moreover , it can control that the said holder | retainer moves to an axial direction both sides by contacting the axial direction both end surfaces of the holder | retainer of a one-way clutch with the axial direction edge part of a pair of rolling bearing, respectively.

Moreover , since the inner ring collar part of a rolling bearing can be used also as a member which controls the axial movement of a cage | basket, the structure of a rolling bearing can be simplified.

Moreover , since the output rotating body can be used as an outer ring having an outer ring inner peripheral surface of a one-way clutch and an outer ring having an outer ring raceway surface of each cylindrical roller bearing, the structure of the entire apparatus can be simplified. .

Further , if the output rotator is detached from the drive shaft and moved in the axial direction with respect to the input rotator, the output rotator can be detached from the input rotator. Thereby, since the outer ring | wheel of a one-way clutch and the outer ring | wheel of a cylindrical roller bearing can be removed simultaneously, the maintenance operation | work of a one-way clutch and a cylindrical roller bearing can be performed easily. At this time, since it is not necessary to move the generator, the maintenance work can be performed more easily.

  According to the power generator of the present invention, it is possible to effectively prevent smearing from occurring in the roller bearing that supports the output shaft of the speed increaser.

It is a schematic side view which shows the wind power generator which concerns on one Embodiment of this invention. It is sectional drawing which shows the roller bearing of the gearbox in the said wind power generator. It is sectional drawing which shows the connection part of the output shaft of a gearbox and the drive shaft of a generator in the said wind power generator. It is sectional drawing which shows the one way clutch in the said wind power generator. It is sectional drawing which shows the conventional gear box.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is a schematic side view showing a wind turbine generator according to an embodiment of the present invention. This wind power generator (power generator) 1 includes a main shaft 2 that rotates in response to wind power (external force), a speed increaser 3 connected to the main shaft 2, and a generator 4 connected to the speed increaser 3. The generator 4 is driven in a state where the rotation of the main shaft 2 is increased by the speed increaser 3.

For example, a blade (not shown) is connected to the tip of the main shaft 2 so as to be integrally rotatable. The blade rotates together with the main shaft 2 when receiving wind force.
The generator 4 has a drive shaft 41 that rotates by inputting rotation increased by the speed increaser 3, a rotor 42 built in the generator 4, a stator (not shown), and the like. The rotor 42 is coupled to the drive shaft 41 so as to be integrally rotatable, and generates electric power as the drive shaft 41 rotates and the rotor 42 is driven.

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. 2 is a cross-sectional view showing the roller bearing 38 that supports the one end 35 b of the output shaft 35. In FIG. 2, 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 periphery thereof and a pair of outer ring rods formed on both axial sides 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 FIG. 1, the wind turbine generator 1 includes an input rotator 5 provided to be rotatable integrally with an output shaft 35 of the speed increaser 3 and an output rotator provided to be integrally rotatable with a drive shaft 41 of the generator 4. 6, a one-way clutch 7 disposed between the input rotator 5 and the output rotator 6, and a pair of rolling bearings 8 disposed on both axial sides of the one-way clutch 7. The one-way clutch 7 and the rolling bearing 8 transmit the rotation of the output shaft 35 to the drive shaft 41 via the input rotator 5 and the output rotator 6 .

FIG. 3 is a cross-sectional view showing a connecting portion between the output shaft 35 of the speed increaser 3 and the drive shaft 41 of the generator 4. In FIG. 3, the input rotator 5 is disposed concentrically with the output shaft 35, and extends from one axial end portion (left end portion in FIG. 3) to the other axial end portion (right end portion in FIG. 3). The flange portion 51, the large diameter portion 52, and the small diameter portion 53 are provided in this order.
The flange portion 51 is formed to extend radially outward from the outer peripheral surface of the large diameter portion 52 and is detachably fixed to the output end portion 35 c of the output shaft 35. Specifically, the flange portion 51 is fastened and fixed to the flange portion 35c1 by bolts and nuts (not shown) in contact with the flange portion 35c1 formed at the output end portion 35c. Between the end face and the end face of the flange portion 41a of the drive shaft 41 of the small diameter portion 53, a gap S1 is formed.

The output rotator 6 is arranged concentrically outside the input rotator 5 in the radial direction, and has a cylindrical portion 61 and a flange formed at the other axial end of the cylindrical portion 61 (the right end portion in FIG. 3). Part 62.
The flange portion 62 is formed to extend radially outward from the outer peripheral surface of the cylindrical portion 61, and is detachably fixed to one end portion of the drive shaft 41. Specifically, the flange portion 62 is fastened and fixed to the flange portion 41a by bolts and nuts (not shown) in contact with the flange portion 41a formed at the one end portion of the drive shaft 41.

An inner peripheral surface of the cylindrical portion 61 is a cylindrical surface, and an inner peripheral surface of one end portion in the axial direction of the cylindrical portion 61 (left end portion in FIG. 3) and an outer peripheral surface of the large-diameter portion 52 of the input rotating body 5. In the gap, an annular seal member 10 for sealing an annular space between the cylindrical portion 61 and the small diameter portion 53 of the input rotating body 5 is provided. A gap S <b> 2 is formed between the end surface of the cylindrical portion 61 on the one end side and the end surface of the flange portion 51 of the input rotating body 5 facing the end surface. Thus, in a state that disconnects the output rotor 6 from the drive shaft 41, the output rotary member 6 is movable in both axial sides with respect to the input rotor 5.

FIG. 4 is a cross-sectional view showing the one-way clutch 7. 3 and 4, the one-way clutch 7 includes an inner ring 71 and an outer ring 72, and a plurality of rollers 73 disposed between the outer peripheral surface 71a of the inner ring 71 and the inner peripheral surface 72a of the outer ring 72. Yes.
The inner ring 71 is externally fitted and fixed to the central portion in the axial direction of the small-diameter portion 53 of the input rotator 5, and rotates integrally with the small-diameter portion 53. A region B in the axial center portion of the cylindrical portion 61 in the output rotator 6 is an outer ring 72 of the one-way clutch 7. Therefore, the inner peripheral surface 72 a is formed on the inner peripheral surface of the region B of the cylindrical portion 61. The rollers 73 have a cylindrical shape, and eight rollers 73 are arranged in the circumferential direction in this embodiment.

The one-way clutch 7 further includes an annular cage 74 that holds the rollers 73 at predetermined intervals along the circumferential direction, and a plurality of elastic members 75 that elastically urge the rollers 73 in one direction. I have.
The cage 74 includes a pair of annular portions 74a facing each other in the axial direction, and a plurality of cage portions 74a extending in the axial direction between the annular portions 74a and arranged at equal intervals in the circumferential direction to connect the annular portions 74a. And a column portion 74b. A plurality of pockets 74c are formed between both annular portions 74a and adjacent column portions 74b, and each roller 73 is individually accommodated in each pocket 74c.
The elastic member 75 includes a compression coil spring, and is individually accommodated in each pocket 74c of the retainer 74 and attached to the column portion 74b.

  In FIG. 4, the same number (eight) of flat cam surfaces 71 a 1 as the rollers 73 are formed on the outer peripheral surface 71 a of the inner ring 71, and the inner peripheral surface 72 a of the outer ring 72 is a cylindrical surface. Between the cam surface 71a1 of the inner ring 71 and the cylindrical surface of the outer ring 72, a plurality (eight) of wedge-shaped spaces S are formed in the circumferential direction. The rollers 73 are individually arranged in each wedge-shaped space S, and the elastic member 75 urges the rollers 73 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 comes into contact with the cam surface 71a1 of the inner ring 71 and the cylindrical surface of the outer ring 72, and the contact surface 73a is formed straight in the width direction (axial direction). The one-way clutch 7 is an environment in which grease is provided between the inner and outer rings 71 and 72, which is a lubricant that is hardly affected by temperature changes using an ester as a base oil and a urea-based one as a thickener. It is in.

  In the one-way clutch 7 configured as described above, when the input rotator 5 rotates at an increased speed and the rotation speed of the input rotator 5 exceeds the rotation speed of the output rotator 6, the inner ring 71 is 72 to rotate relative to one direction (counterclockwise direction in FIG. 4). In this case, the roller 73 slightly moves in the direction in which the wedge-shaped space S is narrowed by the urging force of the elastic member 75, so that the contact surface 73 a of the roller 73 is the outer peripheral surface 71 a of the inner ring 71 and the inner peripheral surface 72 a of the outer ring 72. The one-way clutch 7 is in a state where the rollers 73 are engaged 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, 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. Try to rotate relative to the rotation direction. 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 engagement between the rollers 3 is released, so that the connection between the input rotator 5 and the output rotator 6 is cut off.

  In FIG. 3, the pair of rolling bearings 8 are respectively disposed between the small diameter portion 53 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. Further, each rolling bearing 8 is disposed adjacent to both axial sides of the one-way clutch 7 so as to be able to abut on both axial end surfaces of the retainer 74 of the one-way clutch 7 at the axial end thereof. ing.

The rolling bearing 8 includes a cylindrical roller bearing provided with an inner ring 81 and an outer ring 82 and a plurality of cylindrical rollers 83 that are arranged between the inner ring 81 and the outer ring 82 so as to be able to roll.
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. The outer surface 81b1 of the inner ring collar 81b adjacent to the one-way clutch 7 is a contact surface with which the outer surface of the annular portion 74a that is the axial end surface of the retainer 74 of the one-way clutch 7 contacts. .

  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.

  According to the wind power generator 1 configured as described above, the input rotating body 5 that rotates integrally with the output shaft 35 of the speed increaser 3 and the output rotating body 6 that rotates integrally with the drive shaft 41 of the generator 4. When the rotational speed of the input rotator 5 is lower than the rotational speed of the output rotator 6 by the one-way clutch 7 disposed therebetween, 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.

In addition, the pair of rolling bearings 8 are disposed adjacent to both axial sides of the one-way clutch 7 so that both axial end surfaces of the retainer 74 of the one-way clutch 7 can come into contact with the axial ends thereof. The axial movement of the cage 74 can be restricted by bringing both axial end surfaces of the cage 74 into contact with the axial ends of the rolling bearings 8.
Further, in order to bring both end surfaces in the axial direction of the retainer 74 of the one-way clutch 7 (outer surfaces of the annular portion 74a) into contact with the inner ring flange 81b of the rolling bearing 8, the inner ring flange 81b of the rolling bearing 8 is The retainer 74 can also be used as a member that restricts the axial movement of the retainer 74. Thereby, the structure of the rolling bearing 8 can be simplified.

Moreover, since 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 output rotator 6, the output rotator 6 is connected to the outer ring 72 of the one-way clutch 7, Also, it can be used as 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.

The present invention is not limited to the above-described embodiment, and can be implemented with appropriate modifications. For example, in this embodiment, the input rotating body is provided as a separate member with respect to the output shaft , but may be formed integrally with the output shaft .

Also, the power generating apparatus of the present embodiment has been illustrated for the case of using wind as an external force can be applied to a power generator that generates power using other external force, such as hydraulic or thermal power.

  1: wind power generator (power generator), 2: main shaft, 3: gearbox, 4: generator, 5: input rotor, 6: output rotor, 7: one-way clutch, 8: rolling bearing (cylindrical roller) Bearing), 30: gear mechanism (rotation transmission mechanism), 35: output shaft, 38: roller bearing, 41: drive shaft, 42: rotor, 71a: outer peripheral surface (outer ring outer peripheral surface), 72a: inner peripheral surface (inner outer ring) Peripheral surface), 73: roller, 74: cage, 81b: inner ring collar part, 82a: outer ring raceway surface, 83: cylindrical roller, S: wedge-shaped space

Claims (1)

A spindle that rotates by external force;
A speed increaser having a rotation transmission mechanism for inputting and increasing the rotation of the main shaft; and a roller bearing for rotatably supporting an output shaft for outputting a rotational torque of the rotation transmission mechanism;
A generator having a drive shaft that rotates using the rotation of the output shaft as an input, and a generator that generates electric power as the rotor rotates integrally with the drive shaft,
An input rotator provided on the output shaft so as to be integrally rotatable;
An output rotator that is provided so as to be integrally rotatable with the drive shaft, and is arranged concentrically on the radially inner side or radially outer side of the input rotator;
It is arranged between the input rotator and the output rotator, and the input rotator and the output rotator are connected together so that the input rotator and the output rotator can rotate together in a state where the rotation speed of the input rotator exceeds the rotation speed of the output rotator. A one-way clutch that disconnects the connection between the input rotator and the output rotator in a state where the rotation speed of the input rotator is lower than the rotation speed of the output rotator,
The one-way clutch includes an inner ring outer peripheral surface and an outer ring inner peripheral surface, a plurality of rollers individually disposed in a plurality of wedge-shaped spaces formed between the inner ring outer peripheral surface and the outer ring inner peripheral surface, and the plurality of rollers An annular cage that holds the rollers at predetermined intervals along the circumferential direction, and the rollers are engaged with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, thereby connecting the input rotating body and the output rotating body. It is connected so that it can rotate integrally, and the connection is cut off by releasing its meshing,
A rolling bearing that is disposed between the input rotator and the output rotator and supports the input rotator and the output rotator so as to be relatively rotatable with respect to each other;
The rolling bearing is a cylindrical roller bearing having a plurality of cylindrical rollers and an inner ring collar portion with which an end surface of the cylindrical roller is in sliding contact, and an inner ring flange portion of the cylindrical roller bearing is provided with a retainer for the one-way clutch. A pair of adjacent ones are disposed adjacent to both axial sides of the one-way clutch so that both axial end surfaces abut .
The outer circumferential surface of the outer ring of the one-way clutch is a cylindrical surface,
The cylindrical roller bearing has an outer ring raceway surface on which the cylindrical roller rolls,
The output rotator is disposed on the radially outer side of the input rotator, and an outer ring inner peripheral surface of the one-way clutch and an outer ring raceway surface of the cylindrical roller bearing are formed on an inner peripheral surface of the output rotator. ,
The output rotating body is detachably fixed to the drive shaft and is arranged to be movable in the axial direction with respect to the input rotating body .

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