JP6255792B2 - Rotation transmission device and wind power generator equipped with the same - Google Patents

Description

  The present invention relates to a rotation transmission device and a wind turbine generator including the rotation transmission device.

  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. In addition, a one-way clutch is provided between the output shaft of the speed increaser and the input shaft of the power generator in order to suppress fluctuations in the inertia torque of the power generator caused by wind power fluctuations and reduce the load on the speed increaser. There is also known a technique for providing (see, for example, Patent Document 1).

JP2013-60825A

  However, even if a one-way clutch is provided between the speed increaser and the generator, the load applied to the speed increaser is still large, so that the speed increaser is one of the devices that are prone to malfunction. In addition, when a large load is applied to the speed increaser, a large load is similarly applied to the one-way clutch, so that a possibility of occurrence of a problem is increased. Therefore, it is desired to grasp the state of the load applied to the speed increaser and the one-way clutch and prevent the occurrence of problems.

  The present invention relates to a rotation transmission device that can grasp a load applied to a speed increaser and a one-way clutch, and can be used for prevention of failure occurrence or early detection of failure, and a wind turbine generator including the rotation transmission device. The purpose is to provide.

The present invention is provided between an output shaft of a speed-up gear that speeds up and outputs the rotation of a main shaft in a wind turbine generator, and an input shaft of a power generator that generates power using the rotation of the output shaft as an input. In a state where the rotational speed of the shaft exceeds the rotational speed of the input shaft, the output shaft and the input shaft are connected so as to be integrally rotatable, and the rotational speed of the output shaft is lower than the rotational speed of the input shaft, A rotation transmission device having a one-way clutch that cuts off the connection between the output shaft and the input shaft, and measuring a state of the one-way clutch that varies depending on a load applied to the one-way clutch. A measurement unit; and an acquisition unit that acquires a load applied to the one-way clutch based on a measurement result of the measurement unit, wherein the one-way clutch includes an inner ring and an outer ring, and the inner ring and the outer ring. Multiple placed between An engagement element, and the engagement element meshes with the inner ring and the outer ring to connect the output shaft and the input shaft so as to be integrally rotatable, and the engagement is cut off by releasing the engagement. The measurement unit is arranged to face the engagement element in the circumferential direction, and measures a circumferential gap between the measurement part and the engagement element .

  According to this configuration, the measurement unit measures the state of the one-way clutch, and the acquisition unit acquires the load applied to the one-way clutch based on the measurement result of the measurement unit. It is possible to grasp the state of the load to be performed. Therefore, when the acquisition unit acquires an excessive load, it is possible to take measures so as not to cause a problem with the one-way clutch or the gearbox.

Further, there is a correlation between the magnitude of the circumferential load (torque load) applied to the one-way clutch and the circumferential gap between the engagement element and the measuring unit . Therefore, it is possible to acquire the load applied to the one-way clutch by measuring the gap .

The one-way clutch may have a cam surface for forming a wedge-shaped space between the inner ring and the outer ring on the inner peripheral surface of the outer ring or the outer peripheral surface of the inner ring.
In this case, the engaging element moves in the circumferential direction in the process of meshing with the cam surface. The amount of movement increases as the circumferential load applied to the one-way clutch increases. Therefore, if the circumferential gap between the engagement element and the measuring unit is measured, it is possible to acquire the circumferential load applied to the one-way clutch.

The one-way clutch may have a sprag as the engagement element.
In this case, the sprag moves in the circumferential direction in the process of meshing with the cam surface. The amount of movement increases as the circumferential load applied to the one-way clutch increases. Therefore, it is possible to acquire the circumferential load applied to the one-way clutch by measuring the circumferential gap between the sprag and the measurement unit .

A wind turbine generator according to the present invention includes a speed increaser that accelerates rotation of a main shaft by wind power and outputs the output from an output shaft, a generator that generates power by inputting rotation of the output shaft from an input shaft, and the rotation transmission described above. And an adjustment unit that adjusts the electric load of the generator according to the load acquired by the acquisition unit of the rotation transmission device.
According to this configuration, for example, when the load applied to the one-way clutch is large, the load applied to the one-way clutch is reduced by reducing the electric load in the generator, Problems that occur in the gearbox can be prevented.

The wind power generator preferably includes a transmission unit that transmits information on the state of the one-way clutch or information on a load applied to the one-way clutch to the outside of the wind power generator.
According to this configuration, for example, in the case of having an operation monitoring device that monitors the wind turbine generator from the outside, by transmitting the state of the one-way clutch and the load applied to the one-way clutch to the operation monitoring device, It is possible to remotely grasp the status of the load on the one-way clutch and gearbox, the status of electric load adjustment, and the like.

  According to the present invention, it is possible to grasp the load applied to the speed increaser and the one-way clutch, which can be used for prevention of trouble, early detection, and the like.

It is a schematic side view which shows the wind power generator concerning a reference example . It is sectional drawing which shows the connection part of the output shaft of a gearbox and the input shaft of a generator in a wind power generator. It is sectional drawing which shows the one way clutch in a wind power generator. It is sectional drawing which expands and shows a part of one-way clutch in a wind power generator. 1 is a cross-sectional view showing a one-way clutch according to a first embodiment of the present invention. It is sectional drawing which expands and shows a part of same direction clutch. It is sectional drawing which expands and shows a part of one-way clutch which concerns on the 2nd Embodiment of this invention.

Hereinafter, reference examples and embodiments of the present invention will be described in detail with reference to the accompanying drawings.
[ Reference example ]
FIG. 1 is a schematic side view showing a wind turbine generator according to a reference example . 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 control unit 9 for controlling the operation of the generator 4 is provided, and 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 includes a drive shaft (input shaft) 41 that rotates by inputting the 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.

The wind power generator 1 includes an input rotator 5 provided to be rotatable integrally with an output shaft 35 of the speed increaser 3, an output rotator 6 provided to be integrally rotatable with a drive shaft 41 of the generator 4, and an input The rotation transmission device 11 further includes a one-way clutch 7 disposed between the rotating body 5 and the output rotating body 6 and a pair of rolling bearings 8 disposed on both axial sides of the one-way clutch 7. . The one-way clutch 7 transmits the rotation of the output shaft 35 to the drive shaft 41 via the input rotator 5 and the output rotator 6. In the wind power generator 1 of the reference example , 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. .

FIG. 2 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. 2, the input rotator 5 is disposed concentrically with the output shaft 35, and a cylindrical portion 51 and a flange portion formed at the other axial end portion (left end portion in FIG. 2) of the cylindrical portion 51. 52.
The flange portion 52 is formed to extend radially outward from the outer peripheral surface of the cylindrical portion 51, and is detachably fixed to the output end portion 35 c of the output shaft 35. Specifically, the flange portion 52 is fastened and fixed to the flange portion 35c1 by bolts and nuts (not shown) in a state where the flange portion 52 is in contact with the flange portion 35c1 formed at the output end portion 35c of the output shaft 35. The inner peripheral surface of the cylindrical portion 51 is a cylindrical surface.

The output rotator 6 is arranged concentrically on the radially inner side of the input rotator 5 and is directed from one axial end portion (right end portion in FIG. 2) to the other axial end portion (left end portion in FIG. 2). The flange portion 61, the large diameter portion 62, and the small diameter portion 63 are provided in this order.
The flange portion 61 is formed to extend radially outward from the outer peripheral surface of the large-diameter portion 62 and is detachably fixed to the drive shaft 41. Specifically, the flange portion 61 is fastened and fixed to the flange portion 41a by bolts and nuts (not shown) in contact with the flange portion 41a formed on the drive shaft 41. A gap S1 is formed between the end surface of the small diameter portion 63 and the end surface of the flange portion 35c1 of the output shaft 35.

  A gap between the inner peripheral surface of one axial end portion (right end portion in FIG. 2) of the cylindrical portion 51 of the input rotator 5 and the outer peripheral surface of the large-diameter portion 62 of the output rotator 6 is larger than that of the cylindrical portion 51. An annular seal member 10 for sealing the annular space between the diameter portion 62 is provided. A gap S2 is formed between the end surface of the cylindrical portion 51 of the input rotator 5 on the one end side and the end surface of the flange portion 61 of the output rotator 6 facing the end surface. The output rotator 6 is movable in the axial direction with respect to the input rotator 5 while the output rotator 6 is separated from the drive shaft 41 by the gap S2 and the gap S1.

  FIG. 3 is a cross-sectional view showing the one-way clutch 7. 2 and 3, the one-way clutch 7 includes an outer ring 71 and an inner ring 72, and a plurality of rollers (engagers) 73 disposed between the inner peripheral surface 71 a of the outer ring 71 and the outer peripheral surface 72 a of the inner ring 72. And a plurality of elastic members (springs) 75 that elastically urge each roller 73 in one direction.

The outer ring 71 is configured by a part of the cylindrical portion 51 of the input rotator 5, specifically, a region in the central portion in the axial direction. An outer ring cam surface 71 a 1 is formed on the inner peripheral surface 71 a of the outer ring 71. The inner ring 72 is configured by a part of the small-diameter portion 63 in the output rotating body 6, specifically, a region B in the central portion in the axial direction. The rollers 73 have a cylindrical shape, and eight rollers 73 are arranged in the circumferential direction in this reference example . The elastic member 75 is composed of a compression coil spring and is accommodated in an accommodation recess 76 formed on the inner peripheral surface 71 a of the outer ring 71.

  In FIG. 3, the same number (eight) of substantially flat outer ring cam surfaces 71 a 1 as the rollers 73 are formed on the inner peripheral surface 71 a of the outer ring 71. Each outer ring cam surface 71 a 1 is inclined at a predetermined angle X (for example, 7 to 10 °) radially outward with respect to the tangential L direction of the inner peripheral surface of the outer ring 71. A plurality of (eight) wedge-shaped spaces S are formed in the circumferential direction between the outer ring cam surface 71 a 1 and the outer peripheral surface 72 a of the inner ring 72. The maximum inner diameter dimension d1 of the outer ring cam surface 71a1 (the inner diameter dimension at the point farthest radially outward from the tangent L) is the inner peripheral surface 5a of the input rotating body 5 (the outer ring 81 of the rolling bearing 8 described later). The inner diameter dimension d2 of the surface to be press-fitted) is set.

  Each roller 73 is individually arranged in each wedge-shaped space S, and the elastic member 75 urges the roller 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 contacts the outer ring cam surface 71a1 and the inner ring outer peripheral surface 72a, 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 72 and 71, which is a lubricant that is less susceptible to temperature changes using an ester as a base oil and a urea-based one as a thickener. It is in.

The housing recess 76 formed on the inner peripheral surface 71a of the outer ring 71 is formed continuously from one circumferential end of the outer ring cam surface 71a1. The housing recess 76 has a contact surface 76a on which the other end of the elastic member 75 contacts and an elastic member in contact with the contact surface 76a in a state where one end of the elastic member 75 contacts the roller 73. 75 has a restricting surface 76b for restricting the movement of 75 outward in the radial direction by centrifugal force. And the elastic member 75 is hold | maintained in the state which contact | abutted between the both end parts between the contact surfaces 76a and 73. Therefore, the one-way clutch 7 of this reference example does not include a retainer (for example, see the first embodiment) for holding the circumferential interval of the plurality of rollers 73 and attaching the elastic member 75.

  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 outer ring 71 is Attempt to rotate relative to 72 in one direction (counterclockwise direction in FIG. 3). 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, and the outer peripheral surface (contact surface) 73a of the roller 73 becomes the outer ring cam surface 71a1 and the inner ring outer peripheral surface 72a. The one-way clutch 7 comes into pressure contact with the rollers 73 between the inner and outer rings 72 and 71. Thereby, the inner and outer rings 72 and 71 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 rotating body 5 is rotated at a constant speed after the speed increasing rotation, and the rotation speed of the input rotating body 5 is the same as the rotation speed of the output rotating body 6, the rollers 73 are connected to the inner and outer rings 72, 71. 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 72 and 71 in the one direction, and the input rotator 5 and the output rotator 6 continue to rotate integrally.

  On the other hand, when the rotating speed of the input rotating body 5 is lower than the rotating speed of the output rotating body 6 due to the input rotating body 5 rotating at a reduced speed, the outer 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 72, 71 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.

  In FIG. 2, the pair of rolling bearings 8 are respectively disposed between the cylindrical portion 51 of the input rotator 5 and the small diameter portion 63 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 bearing 8 is composed of a cylindrical roller bearing including an outer ring 81 and an inner ring 82 and a plurality of cylindrical rollers 83 arranged so as to be able to roll between the outer ring 81 and the inner ring 82.

  The outer ring 81 has an outer ring raceway surface 81a formed on the inner periphery, and an outer ring flange 81b formed to protrude radially inward on both axial sides of the outer ring raceway surface 81a. The outer peripheral surface of the outer ring 81 is fitted to the inner peripheral surface 5 a of the input rotator 5. Both end surfaces of the cylindrical roller 83 are in sliding contact with the inner side surface of each outer ring flange portion 81b.

  A region A and a region C at both ends in the axial direction of the small diameter portion 63 in the output rotating body 6 are the inner rings 82 of the rolling bearing 8, and the outer peripheral surfaces of these regions A and C are the inner ring raceway surfaces 82 a of the inner ring 82. It is configured. Between the inner ring raceway surface 82a and the outer ring raceway surface 81a, a cylindrical roller 83 is disposed so as to be able to roll.

The wind power generator 1 of the reference example is arranged in one direction between the input rotator 5 that rotates integrally with the output shaft 35 of the speed increaser 3 and the output rotator 6 that rotates integrally 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 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 the accompanying rotation delay of the cylindrical roller of the roller bearing 38. Therefore, when the rotational speed of the main shaft 2 increases rapidly due to a change in wind force from this state and a high load is applied to the cylindrical roller of the roller bearing 38, the cylindrical roller of the roller bearing 38 becomes difficult to slip on the contact surface with the inner ring. Therefore, the occurrence of smearing in the roller bearing 38 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, a rolling bearing 8 is disposed between the input rotator 5 and the output rotator 6 so as to be relatively rotatable with respect to each other. Therefore, the roller 73 and the inner and outer rings 72 and 71 in the one-way clutch 7 are arranged. When the gap between the roller 73 and the inner and outer rings 72 and 71 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.

FIG. 4 is an enlarged cross-sectional view showing a part of the one-way clutch 7 in the wind power generator 1.
As shown in FIGS. 3 and 4, the one-way clutch 7 constituting the rotation transmission device 11 is provided with a strain sensor (measuring unit) 13 for detecting strain generated in the outer ring 71. The strain sensors 13 are provided at equal intervals at four locations on the outer peripheral surface of the outer ring 71. The strain sensor 13 is provided on the outer peripheral surface of the outer ring 71 on the outer side in the radial direction of the outer ring cam surface 71 a 1, and in a region where a force acts directly by meshing with the roller 73.

  More specifically, the roller 73 (see FIG. 4) in a state where the outer ring cam surface 71a1 and the inner ring outer peripheral surface 72a are not engaged, for example, the outer ring 71 and the inner ring 72 are stopped and no power is transmitted. The contact point between the cam surface 71a1 and the cam surface 71a1 is α, and a torque load is applied to the one-way clutch 7 so that the roller 73 is fully engaged with the outer ring cam surface 71a1 and the inner ring outer peripheral surface 72a. When the contact point between the roller 73 (shown by a two-dot chain line in FIG. 4) and the cam surface 71a1 is β, a virtual line extending from each contact point α, β in the normal direction of the cam surface 71a1 is the outer circumference of the outer ring 71. The strain sensor 13 is provided so as to include a region between the points α ′ and β ′ intersecting the plane. Further, as shown in FIG. 2, the strain sensor 13 is provided in alignment with the axial center D of the roller 73.

When the roller 73 meshes with the outer ring cam surface 71a1, the outer ring 71 is distorted on the outer side in the radial direction, and the distortion sensor 13 measures this distortion.
The measured value of each strain sensor 13 is transmitted to the control unit 9 by a wireless transmitter (not shown). As shown in FIG. 1, the control unit 9 includes an acquisition unit 15 that acquires a torque load of the one-way clutch 7, and an electric that adjusts an electric load (power generation amount) in the generator 4 based on the torque load. The load adjustment unit 16 and a storage unit 17 that stores a table that associates the relationship between the distortion generated in the outer ring 71 and the torque load applied to the outer ring 71 are provided.

The acquisition unit 15 reads the strain measured by each strain sensor 13, obtains an average value or a median value thereof, and refers to a table stored in the storage unit 17, whereby a torque load corresponding to the strain value is obtained. Ask for.
The electric load adjustment unit 16 adjusts the electric load in the generator 4 according to the torque load acquired by the acquisition unit 15. For example, when the torque load acquired by the acquisition unit 15 is large, the electric load adjustment unit 16 adjusts the electric load so as to reduce the output (power generation amount) of the generator 4. As a result, the torque load applied to the one-way clutch 7 can be reduced, and the burden on the one-way clutch 7 can be reduced to prevent problems such as damage. Further, since the torque load applied to the speed increaser 3 can be similarly reduced, it is possible to prevent the speed increaser 3 from being troubled. In addition, conventionally well-known various methods can be employ | adopted for the adjustment method of the electrical load of the generator 4 (for example, refer Unexamined-Japanese-Patent No. 2008-278725 etc.).

  The control unit 9 also includes a transmission unit 18 that transmits a measurement value of the distortion generated in the outer ring 71 and information on the acquired torque load to the operation monitoring device (operation monitoring facility) 20. The operation monitoring device 20 constantly monitors the operation status of the wind power generator 1, the occurrence of malfunction, and the like by using information on the strain measurement value and torque load transmitted from the control unit 9. Further, the operation monitoring device 20 can collectively monitor the operation statuses of the plurality of wind turbine generators 1.

First Embodiment
FIG. 5 is a cross-sectional view showing the one-way clutch 7 according to the first embodiment of the present invention, and FIG. 6 is an enlarged cross-sectional view showing a part of the same-direction clutch 7.
In the one-way clutch 7 of the present embodiment, a substantially flat cam surface 72a1 is formed on the outer peripheral surface 72a of the inner ring 72, the inner peripheral surface 71a of the outer ring 71 is formed in a cylindrical surface, and a wedge shape is formed between both surfaces 72a1 and 71a. A space S is formed. In each wedge-shaped space S, rollers 73 as engaging elements are arranged. Between the inner ring 72 and the outer ring 71, an annular retainer 74 that holds the rollers 73 at predetermined intervals along the circumferential direction is provided.

  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 pocket 74c is provided with an elastic member 75 that elastically biases the roller 73 in one direction.

In the present embodiment, the inner ring 72 is provided on the input rotator 5 side, and the outer ring 71 is provided on the output rotator 6 side.
In the one-way clutch 7 of the present embodiment, when the rotational speed of the input rotator 5 exceeds the rotational speed of the output rotator 6 due to the input rotator 5 rotating at an increased speed, the inner ring 72 becomes the outer ring 71. In contrast, the roller 73 is slightly moved in the direction in which the wedge-shaped space S is narrowed by the urging force of the elastic member 75 due to the relative rotation in one direction (counterclockwise direction in FIG. 5). The contact surface 73 a comes into pressure contact with the cam surface 72 a 1 of the inner ring 72 and the inner peripheral surface 71 a of the outer ring 71, and the one-way clutch 7 is in a state where the roller 73 is engaged between the inner and outer rings 72, 71. Thereby, the inner and outer rings 72 and 71 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 rotating body 5 is rotated at a constant speed after the speed increasing rotation, and the rotation speed of the input rotating body 5 is the same as the rotation speed of the output rotating body 6, the rollers 73 are connected to the inner and outer rings 72, 71. 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 72 and 71 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 72 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 72, 71 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.

  As shown in FIG. 6, the gap sensor 21 is provided on the column portion 74 b of the cage 74. The gap sensor 21 is attached to the side surface of the pillar portion 74b that faces the roller 73. The gap sensor 21 detects a gap (gap) g between the rollers 73. In the present embodiment, as shown in FIG. 5, four gap sensors 21 are provided at equal intervals in the circumferential direction. That is, among the eight rollers 73, the gap sensor 21 is provided corresponding to four rollers 73 arranged every other one.

  When the rotational speed of the input rotator 5 exceeds the rotational speed of the output rotator 6, the roller 73 moves in a direction in which the wedge-shaped space S is narrowed, and the gap g between the roller 73 and the gap sensor 21 is reduced. Conversely, when the rotational speed of the input rotator 5 is lower than the rotational speed of the output rotator 6, the roller 73 moves in the direction in which the wedge-shaped space S becomes wider, and the gap g between the roller 73 and the gap sensor 21. Becomes larger.

Therefore, by measuring the gap g between the roller 73 and the gap sensor 21, the degree of engagement of the roller 73 with the inner and outer rings 72, 71, that is, the torque load applied to the one-way clutch 7 can be grasped. Specifically, the storage unit 17 of the control unit 9 stores a table in which the relationship between the measurement value of the gap sensor 21 and the torque load is associated, and the acquisition unit 15 reads the measurement value of the gap sensor 21. At the same time, the torque load is determined by referring to the table.
Therefore, also exhibits the same effect as in Reference Example in the present embodiment.

Second Embodiment
FIG. 7 is an enlarged sectional view showing a part of the one-way clutch 7 according to the second embodiment of the present invention.
The one-way clutch 7 of this embodiment is the same as that of the second embodiment in that the gap sensor 21 is provided in the retainer 74, except that a sprag is used as the engagement element 73. . Further, the inner ring 72 of the one-way clutch 7 is constituted by the shaft portion 53 of the input rotating body 5, and the outer peripheral surface 72 a of the inner ring 72 is constituted by the outer peripheral surface 53 a of the shaft portion 53. Therefore, the outer peripheral surface 72a of the inner ring 72 is not formed with a cam surface as in the second embodiment, but is formed in a cylindrical surface.

  The sprag 73 includes a first contact surface 73b that contacts the outer peripheral surface 72a of the inner ring 72 and a second contact surface 73c that contacts the inner peripheral surface 71a of the outer ring 71. The contact surfaces 73c are each formed in a convex shape and a substantially arc shape. Further, the distance between the first contact surface 73b and the second contact surface 73c contacting the outer peripheral surface 72a of the inner ring 72 and the inner peripheral surface 71a of the outer ring 71 varies depending on the inclination of the sprag 73, and the inner ring 72 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 inner ring 72 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 increases, the sprag 73 meshes with the outer peripheral surface 72a of the inner ring 72 and the inner peripheral surface 71a of the outer ring 71, and conversely, the first contact. When the distance between the surface 73b and the second contact surface 73c is reduced, the engagement between the sprag 73 and the outer peripheral surface 72a of the inner ring 72 and the inner peripheral surface 71a of the outer ring 71 is released. Therefore, when the inner ring 72 attempts to rotate relative to the outer ring 71 in the direction of the arrow a, the inner ring 72 and the outer ring 71 are connected so as to rotate together, and the inner ring 72 rotates relative to the outer ring 71 in the direction of arrow b. When this is done, the connection between the inner ring 72 and the outer ring 71 is cut off.

Further, the gap sensor 21 provided in the pillar portion 74 b of the cage 74 measures the gap g between the retainer 74 and the sprag 73. By measuring the gap g between the sprag 73 and the gap sensor 21, the degree of engagement of the sprag 73 with the inner and outer rings 72, 71, that is, the torque load applied to the one-way clutch 7 can be grasped. Specifically, the storage unit 17 of the control unit 9 stores a table in which the relationship between the measurement value of the gap sensor 21 and the torque load is stored, and the acquisition unit 15 stores the measurement value of the gap sensor 21. The torque load is determined by reading and referring to the table.
Therefore, also exhibits the same effect as in Reference Example in the present embodiment.

  Moreover, in this embodiment, since it is not necessary to form a cam surface in the inner ring 72 (shaft portion 53) of the one-way clutch 7, the manufacturing cost can be reduced. Further, since the shaft portion 53 can be used as the inner ring 72, 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 rotation transmission device 11 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 rotation transmission device 11 can be suitably disposed.

  The present invention is not limited to the above-described embodiment, and can be implemented with appropriate modifications. For example, as the measurement unit that measures the state of the one-way clutch 7, for example, a temperature sensor that measures the temperature of the one-way clutch 7 or a vibration sensor that measures vibration of the one-way clutch 7 can be used. When a load on the one-way clutch 7, for example, a torque load increases, the thermal energy generated in the one-way clutch 7 increases, so that the load applied to the one-way clutch 7 is grasped by measuring the temperature of the one-way clutch 7. It becomes possible. Similarly, when the load on the one-way clutch 7 increases, the vibration also increases. Therefore, it is possible to grasp the load applied to the one-way clutch 7 by measuring the vibration generated in the one-way clutch 7.

In the second embodiment, the sensor constituting the measurement unit is the gap sensor 21, but may be the strain sensor 13 that measures the distortion of the inner ring 72. In this case, the strain sensor 13 may be provided at a position corresponding to the radially inner side of the cam surface 72a1.
In the first embodiment, the sensor constituting the measurement unit is the strain sensor 13, but may be the gap sensor 21 as described in the second and third embodiments.

  In each of the above embodiments, the information measured by the measuring units 13 and 21 is configured to be wirelessly transmitted. However, the information is recorded by a recording device such as a data logger, and the information is periodically extracted from the recording device. Also good.

1: wind power generator, 2: main shaft, 3: gearbox, 4: generator, 7: one-way clutch, 11: rotation transmission device, 13: strain sensor (measurement unit), 15: acquisition unit, 16: electricity Load adjustment unit, 18: transmission unit, 20: operation monitoring device, 21: gap sensor (measurement unit), 35: output shaft, 41: drive shaft (input shaft), 71: outer ring, 71a: inner peripheral surface, 71a1: Cam surface, 72: inner ring, 72a: outer peripheral surface, 72a1: cam surface, 73: engagement element (roller, sprag), S: wedge-shaped space

Claims (5)

The rotation speed of the output shaft is provided between the output shaft of the speed increaser that increases the rotation speed of the main shaft in the wind turbine generator and the input shaft of the power generator that generates power using the rotation of the output shaft as an input. The output shaft and the input shaft are connected so as to be integrally rotatable in a state in which the rotational speed of the output shaft is lower than the rotational speed of the input shaft. A rotation transmission device having a one-way clutch that disconnects from the input shaft;
A measuring unit for measuring a state of the one-way clutch, which varies depending on a load applied to the one-way clutch;
An acquisition unit that acquires a load applied to the one-way clutch based on a measurement result of the measurement unit;
The one-way clutch includes an inner ring and an outer ring, and a plurality of engagement elements disposed between the inner ring and the outer ring, and the engagement elements mesh with the inner ring and the outer ring, thereby the output shaft and the outer ring. The input shaft and the input shaft are connected so as to be integrally rotatable, and the connection is interrupted by releasing the engagement.
The rotation transmitting device is characterized in that the measuring unit is arranged to face the engaging element in the circumferential direction and measures a circumferential gap between the measuring part and the engaging element . The one-way clutch, the inner or outer peripheral surface of the inner ring of the outer ring has a cam surface for forming the wedge-shaped space between the inner ring and the outer ring, according to claim 1 Rotation transmission device. The rotation transmission device according to claim 1 , wherein the one-way clutch has a sprag as the engagement element. A gearbox output from the output shaft by accelerating the rotation of the main shaft by wind, a generator for generating electric power input from the input shaft rotation of the output shaft, according to any one of claims 1 to 3 A wind power generator comprising: the rotation transmission device of claim 1; and an adjustment unit that adjusts the electrical load of the generator according to the load acquired by the acquisition unit of the rotation transmission device. The wind turbine generator according to claim 4 , further comprising: a transmitter that transmits information on a state of the one-way clutch or information on a load applied to the one-way clutch to the outside of the wind turbine generator.

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