JP2003161357A - Speed-increasing gear for wind power generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a speed-increasing gear for a generator capable of achieving a large reduction ratio, and also generating electric power of good quality by rotating the generator at a rated speed regardless of the strength of wind. <P>SOLUTION: The variable speed-changing ratio type speed-increasing gear for a wind power generator has an outer ring 15 mounted to an input shaft (low speed shaft) 12 via a power transmission means, a sun roller 21 provided at an output shaft (high speed shaft) 19, and double cones 22 located between the outer ring 15 and the sun roller 21. In the speed-increasing gear, a female screw 23d is formed on an extended portion 23c of a flange 23b of a carrier 23 rotatably supporting the double cone 22, and also a male screw 26a is formed on an outside peripheral surface of a rotary shaft 26 of a driving motor 25, and the male screw 26a is engaged with the female screw 23d. The carrier 23 is capable of moving in the axial direction of the input and output shafts by the rotational motion of the driving motor 25. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed increaser for a wind power generator, and more particularly to a speed increaser for a wind power generator that accelerates the rotation of a rotor that receives wind to rotate the generator at a rated speed. Regarding speed machines.

[0002]

2. Description of the Related Art A wind power generator is a device that converts wind energy into a rotational force and transmits the rotational force to the power generator to generate electric power. The generator has the structure shown in FIG. The wind power generator 100 of FIG. 6 is provided with a yoke drive device 103 on the upper part of a pillar 102 that is planted on the ground 101.
1 or more (usually 3) on this yoke drive device 103
Rotor 105 having blades 104 of
A speed increaser 107 for increasing the rotational speed (rotation speed) of the main shaft 106 of No. 5 and a generator 108 for generating power at the rated speed increased by the speed increaser 107 are provided. 10
Reference numeral 9 is a nacelle for storing components such as the speed increasing gear 107 and the generator 108.

In this propeller-type wind power generator 100, a blade 104 attached to a rotor 105 receives wind to generate a lift force on the blade 104, and the lift force causes a rotation force on a main shaft 106. The rotation speed of the main shaft 106 changes to about 10 to 100 rotations per minute depending on the strength of the wind received by the wind turbine, but the rotation speed at which the generator 108 can efficiently generate power is determined by the generator. for that reason,
By providing the speed increasing device 107 between the main shaft 106 and the generator 108, the number of revolutions input to the generator 108 is increased to efficiently generate electricity. Conventionally,
As the gearbox 107, a gear type gearbox such as a multi-axis gear type gearbox or a planetary gear type gearbox is generally used.

Problems with Gear Type Gearbox When a gear type gearbox such as a multi-shaft gear type gearbox or a planetary gear type gearbox is used as a gearbox for a generator as in the prior art, There are the following issues. 1. Generation of noise and vibration due to tooth engagement 2. Deterioration of power quality due to generation of higher harmonic component output components due to tooth meshing

Noise in gear type gearbox of wind power generator
The generation of vibration is mainly due to the meshing of gears. Therefore, although measures such as improving the shape and dimensional accuracy of the teeth are taken, noise and vibration cannot be completely eliminated. Therefore, as another measure, the nacelle 109 or the support 1
02 has been treated with vibration damping materials and soundproofing materials. With these measures, vibration damping and vibration damping are possible to some extent, but fundamental measures to prevent vibration and noise are generated. Not only that, but the cost increases. Further, the generation of harmonic components due to the meshing of teeth requires expensive converters and inverters having a filtering function for removing the harmonics, resulting in high cost of the wind power generator system.

Therefore, a traction drive type speed increaser is used. A traction drive is a type of friction transmission device, in which power is transmitted through an oil film formed between rolling elements having smooth surfaces pressed against each other. Rolling elements include rings / cones, balls / discs, rollers / rollers, toroidal discs /
There are various combinations such as rollers. Such a traction drive has the following features.

(1) Vibration and noise levels are low as compared with a power transmission device using gears. (2) Continuously Variable Transmissi
on, CVT) can be constructed.

A speed increaser using a traction drive is
It is classified into a fixed gear ratio type speed increaser having a constant gear ratio and a continuously variable gear ratio type speed increaser having a continuous gear ratio.

Problems of Fixed Gear Ratio Type Gearbox As shown in FIG. 7 (a), the gearbox type gearbox is mainly used for a variable speed type gearbox or a windturbine gearbox which controls the number of revolutions of the generator at a constant wind speed or more. A fixed gear ratio type speed increaser 107A having a fixed ratio is mounted. As the fixed gear ratio type speed increaser 107A, a planetary roller as shown in FIG. The gearbox 110 is used. In this planetary roller type speed increaser 110, an outer ring 112 is arranged around a sun roller 111 with their axes aligned, and a plurality of cylindrical shapes are formed in a space portion formed between the sun roller 111 and the outer ring 112. Carrier 115 having a plurality of planetary roller support shafts 114 for arranging the planetary rollers 113 and rotatably arranging the planetary rollers 113 at equal intervals in the circumferential direction, and integrally formed with the carrier 115. The input shaft (low speed rotation shaft) 116 is provided.

In this fixed gear ratio type gearbox 110,
For example, by restraining the rotation of the outer ring 112, power is transmitted between the input shaft (low-speed rotation shaft) 116 and the carrier 115, and power is transmitted between the carrier 115 and the sun roller 111. That is, when the input shaft (low speed rotation shaft) 116 is rotationally driven, the planet roller 113 having the planet roller support shaft 114 of the carrier 115 integrated with the input shaft (low speed rotation shaft) 116 is inserted into the sun roller 111 and the outer ring 112. Between the sun roller 111 and the sun roller 111, and the rotation and revolution of the planetary roller 113 causes the sun roller 111 to rotate at a speed increased by a speed ratio inversely proportional to the outer diameter ratio thereof.
It can be used as a speed increaser that rotates at high speed according to the number of revolutions (revolution number).

However, in the wind power generator equipped with the planetary roller type speed increaser 110 as the fixed speed ratio type speed increaser 107A, there is a problem that the power generation efficiency is deteriorated when the wind is weak. That is, when the wind is weak, the generator rotation speed is less than the rated rotation speed, so that the power generation efficiency is reduced and the rated voltage cannot be obtained.

On the other hand, a continuously variable transmission can be realized by continuously changing the radius of rotation (the distance from the rotation axis to the contact portion with another power transmission member) of the power transmission member constituting the traction drive. Various types of traction drive type continuously variable transmissions have been developed according to the method of changing the radius of gyration, and a cone type continuously variable transmission is one of the typical ones. Therefore, instead of the fixed gear ratio type speed increaser 107A of FIG. 7A, a wind power generator using a variable gear ratio type speed increaser 107B as shown in FIG. 8 is also considered.

FIG. 9 is a vertical cross-sectional view of a cone type continuously variable transmission 120 as an example of a variable gear ratio type speed increaser. In this cone type continuously variable transmission 120, an input shaft (low speed rotation shaft) 122 is rotatably supported by a bearing 123 on one end side of a casing 121. The input shaft (low speed rotation shaft) 122 has a cam ring 124 and an outer ring 1.
25 is inserted. The cam ring 124 is connected to the input shaft (low-speed rotation shaft) 1 by a power transmission means such as a spline.
Power is transmitted to and from 22.

On the other hand, the outer ring 125 has a rolling surface on its inner peripheral portion and is rotatably provided to the input shaft (low speed rotating shaft) 122 via a bearing 126. A cam surface is formed on the opposing surface of the cam ring 124 and the outer ring 125, and when the cam surfaces are meshed with each other, power is transmitted between the cam ring 124 and the outer ring 125 and a transmission torque is transmitted. Is applied to the outer ring 125.

The cone type continuously variable transmission 12 shown in FIG.
Between the cam surfaces of the zero cam ring 124 and the outer ring 125, in order to reduce friction and stabilize the behavior of the axial pressing force, a rolling element (steel ball or the like) is interposed and a pressure cam 127 is provided. It is configured.

Further, in the cone type continuously variable transmission 120 of FIG. 9, a disc spring 128 is provided between the cam ring 124 and the outer ring 125. The resultant force of the axial pressing force of the pressure cam 127 and the axial pressing force of the disc spring 128 acts on the outer ring 125, and as a result,
It becomes possible to generate a normal force required for power transmission at the traction drive contact portion.

At the other end of the casing 121,
An output shaft (high-speed rotation shaft) 129 is arranged coaxially with the input shaft (low-speed rotation shaft) 122 via a bearing 130. At the inner end of this output shaft (high-speed rotation shaft) 129, a sun roller 131 having a rolling surface formed on the outer peripheral portion is integrally formed.

This sun roller 131 and outer ring 1
Between 25, a plurality of double cones 132 having an abacus shape are rotatably arranged at equal intervals in the circumferential direction. Each double cone 132 has two rolling surfaces, that is, conical surfaces 132a and 132b.
At 32a, it comes into pressure contact with the outer ring 125,
The conical surface 132b comes into pressure contact with the sun roller 131.

The cone type continuously variable transmission 12 will be described with reference to FIG.
The mechanism of the zero shift operation will be described. Double cone 132
The carrier 133 that holds the circles at equal intervals in the circumferential direction is restricted from rotating around the input / output axis. That is, the double cone 132 is restricted from revolving around the input / output shaft, and can only rotate about the axis of the rotation support shaft 134. In this case, the gear ratio e (high speed rotating shaft rotation speed / low speed rotating shaft rotation speed) is given by the following equation.

[0020]

[Formula 1]

The double cone 132 is the outer ring 1
The conical generatrix 132c that contacts 25 and the conical generatrix 132d that contacts the sun roller 131 are formed to be parallel to each other. Therefore, as shown in FIG.
2 can move along the conical generatrixes 132c and 132d. When the double cone 132 moves, the radii b and c in the above equation 1 change, so that the gear ratio e becomes continuously variable.

In the cone type continuously variable transmission 120 shown in FIG. 9, the rotary support shaft 134 of the double cone 132 has the carrier 133.
The double cone 132 is rotatable with respect to the rotary support shaft 134 via a bearing. Further, the carrier 133 is driven by the rack 135 and the pinion gear 136 so that it can be moved in the input / output axis direction.

The carrier 133 has a flange 133.
Although not shown in the drawing, these flange portions 133a and 133b are made of a bowl-shaped integral body.

Further, in FIGS. 9 and 10, the double cone 132 on the upper side of the drawing is located on the rightmost side in the axial movable range, and the axial movable range of the carrier 133 is easily understood. The lower double cone 132 in the drawing is shown as located on the leftmost side in the axially movable range.

That is, the double cone 13 on the upper side of the drawing
In 2, the contact portion of the conical generatrix 132c on the outer ring 125 side with the outer ring 125 is located near the maximum radius of the conical surface 132a, and the contact portion of the conical generatrix 132d on the sun roller 131 side with the sun roller 131 is:
It is located near the minimum radius of the conical surface 132b. Also,
In the double cone 132 on the lower side of the drawing, the contact portion of the conical generatrix 132c on the outer ring 125 side with the outer ring 125 is located near the minimum radius of the conical surface 132a, and the sun roller 131 of the conical generatrix 132d on the sun roller 131 side. The contact portion with is located near the maximum radius of the conical surface 132b.

Advantages of using a traction drive for a speed increaser for a wind power generator In recent years, mechanical devices tend to be required to be even quieter. When the cone type continuously variable transmission 120 as shown in FIG. 9 is used as the variable gear ratio type speed increaser 107B shown in FIG. 8, the noise and vibration levels are lower than those of the gear type speed increaser, so that the nacelle The cost can be reduced because it is possible to simplify the soundproofing and antivibration measures on the columns and columns, and because harmonic components due to tooth meshing do not occur in the output power of the generator, inexpensive converters and inverters can be used. can do. In addition, wind causes the rotor 105
Even if the rotation speed of the (spindle 106) changes, the generator 1 can be controlled by controlling the gear ratio of the cone type continuously variable transmission 120.
The rotational speed of 08 can be controlled within a certain range. As a result, there is an advantage that the power generation efficiency at low wind speed can be improved.

[0027]

As described above, the traction drive is a kind of friction transmission, and power is transmitted through the oil film formed between the two surfaces having smooth surfaces. However, even a synthetic naphthenic traction oil manufactured to obtain a high traction coefficient has a traction coefficient of 0.1 at most. In the cone type continuously variable transmission 120, it is generally unavoidable that spin occurs at its contact portion, and this spin further lowers the traction coefficient.

For these reasons, in the traction drive, it is generally necessary to apply a large normal force between the power transmission members for power transmission. If a sufficient normal force does not act on the contact portion, excessive slippage (gross slip) occurs, and seizure occurs unless the load is reduced.

In the cone type continuously variable transmission 120 shown in FIG. 9, a pinion gear 136 driven by a drive motor is used.
Driving the rack 135 integrated with the carrier 133 causes the double cones 132, which are arranged at equal intervals in the circumferential direction by the carrier 133, to form the cone generatrix 132.
c, 132d, and as a result,
It is possible to obtain a predetermined speed increasing ratio. When a large normal force acts on the contact portion of the cone type continuously variable transmission 120, a large force is required to move the carrier 133 in the input / output axis direction. Therefore, in the method using the rack 135 and the pinion gear 136, the following problems are likely to occur.

(1) In order to apply a sufficiently large axial force to the carrier 133 for gear shifting, a drive motor having a large drive force is used, or the drive motor and the rack 135 are used.
It is necessary to provide a speed reduction mechanism between the pinion gear 136 and the pinion gear 136.

(2) By reducing the size of the pinion gear 136, a larger gear ratio can be obtained. On the other hand, by reducing the size of the tooth module, the mechanical strength of the tooth is reduced and the tooth is broken. May occur.

Accordingly, a main object of the present invention is to provide a speed up gear for a wind power generator which solves the above two problems in the cone type continuously variable speed up gear.

[0033]

In order to solve the above-mentioned problems, a speed-up gear for a generator according to a first aspect of the present invention is provided.
At least the input shaft and the output shaft are arranged coaxially,
An outer ring having an inner peripheral surface as a rolling surface and a sun roller having an outer peripheral surface as a rolling surface are provided coaxially with the input / output shaft, and rotation is transmitted by a rotation transmitting means between the input shaft and the outer ring. The rotation is transmitted between the sun roller and the output shaft by the rotation transmitting means, and three or more double cones that are in contact with the outer ring and the sun roller are rotatably held by the carrier at equal intervals in the circumferential direction. In a speed increaser for a wind power generator having a cone-type continuously variable transmission that makes it possible to continuously change speed by moving a carrier, the rotation of which is restricted about the axis of the carrier, in the axial direction of the carrier. It is characterized by being provided with a feed screw mechanism for performing.

The relationship between the torque T required to rotate the feed screw and the generated axial force F is as follows.

[0035]

[Formula 2]

Although there is a difference depending on the above parameters, it is generally possible to generate a large axial force by a screw mechanism. With the feed screw mechanism provided integrally with or separately from the carrier of the cone type continuously variable transmission, the drive motor can be downsized or the reduction mechanism can be omitted, and the device can be downsized or the cost can be reduced.

According to the speed increasing gear for a generator having the above-mentioned structure, since it is a traction drive, the generation of noise and vibration as in a gear type speed increasing gear is small, and the generated electric power does not contain harmonic components. Not only is it possible to generate a large amount of generated power, but it is also possible to reduce or reduce the soundproofing and antivibration measures such as nacelles and columns. In addition, since it is a continuously variable speed increaser, it is possible to increase the speed increase ratio at low wind speeds, so there is no decrease in generated power at low wind speeds, which is the case with fixed speed ratio type speed increasers. Is obtained. Furthermore, instead of the conventional rack and pinion gear type mechanism, a feed screw mechanism that moves the carrier in the axial direction by a drive motor is provided, so compared to the case of the rack and pinion gear type moving mechanism, the carrier axial direction The driving force for movement is small, a small drive motor can be used, and the driving force can be easily changed.

According to a second aspect of the present invention, there is provided the generator speed increasing machine, wherein the female screw of the feed screw mechanism is provided on the carrier, and a rotary shaft having a male screw is screwed into the female screw. Is provided with a drive motor for driving the.

According to the speed-up gearbox for a generator having the above-mentioned structure, the drive motor rotates the rotating shaft having the external thread, and thereby the carrier having the internal thread screwed to the rotating shaft having the external screw formed. Can be moved in the direction of the input / output axis, so the structure is simple and compact compared to the case where a conventional rack and pinion gear type moving mechanism is provided.
Therefore, the cost can be reduced and the breakdown can be reduced.

According to a third aspect of the present invention, there is provided a speed increasing gear for a generator, wherein a male screw or a female screw coaxial with the input / output shaft is provided on the carrier, or a separate member having a female screw or a male screw. Is integrated with the carrier, has a threaded portion that meshes with the female screw or the male screw, and is provided with a drive motor for driving a rotating member whose axial movement is restricted.

According to the speed-up gearbox for a generator having the above structure, when the male screw or the female screw coaxial with the input / output shaft is provided on the carrier, the carrier is coaxial with the input / output shaft by the drive motor. Since the carrier is moved to, no unbalanced load is applied to the carrier, and therefore, life reduction or breakage due to uneven wear does not occur. Further, when the reduction mechanism is provided between the rotation member whose axial movement is restricted and the drive motor, the rotation force of the motor can be amplified and transmitted to the carrier, and the size of the drive motor can be reduced.

According to a fourth aspect of the present invention, in the speed increasing gear for a wind power generator, the rotating member is rotatably attached to the casing via a bearing, and the carrier is rotated to the casing via a needle. Is regulated, and
It is characterized in that it is attached so as to be movable in the axial direction.

According to the speed increasing gear for the wind power generator described above, since the stress load toward the input / output shaft center of the rotating member is received by both the bearing and the needle, the rotating member is inclined with respect to the input / output shaft center. Since the rotating member is rotatably attached to the casing via the bearing, the rotating member can smoothly rotate with respect to the casing, and the carrier is restricted from rotating by the casing via the needle, and Since the needle and the casing are in line contact with each other because they are attached so as to be movable in the input / output axis direction, the carrier can be smoothly moved in the input / output axis direction.

According to a fifth aspect of the present invention, a speed increasing gear for a wind turbine generator is characterized in that a planetary roller type transmission is arranged on the input side of the cone type continuously variable transmission.

According to the speed increasing gear for the wind power generator described above, a large speed increasing ratio can be obtained as compared with the case where the cone type continuously variable transmission is used alone. In other words, a predetermined speed increasing ratio is obtained. Since the speed increasing ratio of the cone type continuously variable transmission can be reduced, the cone type continuously variable transmission can be made compact and inexpensive.

[0046]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a speed increasing gear for a wind power generator according to the present invention will be described below with reference to the drawings.

FIG. 1 is a vertical sectional view of a speed increasing gear 10 for a wind power generator according to a first embodiment of the present invention. In the figure, 11
Is a casing, and an input shaft (low-speed rotating shaft) 12 is rotatably supported at one end thereof via a bearing 13. A cam ring 1 is attached to the input shaft (low speed rotating shaft) 12.
4 and the outer ring 15 are inserted. Power is transmitted to the cam ring 14 between the cam ring 14 and the input shaft (low speed rotation shaft) 12 by a power transmission means such as a spline.

On the other hand, the outer ring 15 has a rolling surface on its inner peripheral portion, and is rotatably provided to the input shaft (low speed rotating shaft) 12 via a bearing 16. The cam ring 1
A cam surface is formed on the opposing surface between the outer ring 15 and the outer ring 15, and the cam surfaces mesh with each other to transmit the power between the cam ring 14 and the outer ring 15 and to respond to the transmission torque. The axial pressing force acts on the outer ring 15.

The cone type continuously variable gearbox 10 shown in FIG.
In order to reduce friction and stabilize the behavior of the axial pressure force between the cam surfaces of, rolling elements (steel balls etc.) are interposed,
The pressure cam 17 is configured.

Further, in the cone type continuously variable gearbox 10 of FIG. 1, a disc spring 18 is provided between the cam ring 14 and the outer ring 15. The resultant force of the axial pressing force of the pressure cam 17 and the axial pressing force of the disc spring 18 acts on the outer ring 15, and as a result, a normal force required for power transmission is generated at the traction drive contact portion. It will be possible.

At the other end of the casing 11, an output shaft (high-speed rotation shaft) 19 is rotatably arranged via a bearing 20 coaxially with the input shaft (low-speed rotation shaft) 12. At the inner end of the output shaft (high-speed rotation shaft) 19, a sun roller 21 having a rolling surface formed on the outer peripheral portion is integrally formed.

Between the sun roller 21 and the outer ring 15, a plurality of double cones 22 having an abacus shape are rotatably arranged at equal intervals in the circumferential direction. Each double cone 22 has two rolling surfaces, namely, conical surfaces 22a and 22b.
At a, it comes into pressure contact with the outer ring 15, and at the other conical surface 22b it comes into pressure contact with the sun roller 21.

The mechanism of the shifting operation of the cone type continuously variable gearbox 10 is as follows. The conventional cone type continuously variable transmission 12 shown in FIG.
The same as 0. That is, the carrier 23 that holds the double cones 22 at equal intervals in the circumferential direction is restricted from rotating around the input / output axis. The double cone 22 is restricted from revolving around the input / output shaft, and can rotate only around the axis of the rotating shaft 24. Gear ratio e in this case
(High speed rotating shaft rotating speed / low speed rotating shaft rotating speed) is given by the following equation.

[0054]

[Formula 3]

The double cone 22 has an outer ring 15
The conical generatrix 22c in contact with and the conical generatrix 22d in contact with the sun roller 21 are formed to be parallel to each other. For this reason, as shown in FIG.
It is possible to move along 2c and 22d. When the double cone 22 moves, the radius b in the above equation 2
Since gear ratios c and c change, the gear ratio e is continuously variable.

In the cone type continuously variable gearbox 10 of FIG. 1, the rotary support shaft 24 of the double cone 22 is press-fitted and integrated with the carrier 23, and the double cone 22 is connected to the rotary support shaft 24 via a bearing. It is freely rotatable. Further, by driving the carrier 23 by the drive motor 25, the carrier 23 can be moved in the input / output axis direction.

The carrier 23 has a flange portion 23a,
23b, and these flange portions 23
Although not shown in the drawing, a and 23b are made of a bowl-shaped integrated body.

In addition, in FIG. 1, the double cone 22 on the upper side of the drawing is located on the rightmost side in the axially movable range (gear ratio to facilitate understanding of the axially movable range of the carrier 23). Further, the double cone 22 on the lower side of the drawing is shown to be located on the leftmost side in the movable range in the axial direction (the maximum gear ratio).

That is, the double cone 22 on the upper side of the drawing
Then, the contact portion of the conical generatrix 22c on the outer ring 15 side with the outer ring 15 is located near the maximum radius of the conical surface 22a (radius dimension c maximum), and the conical generatrix 22d on the sun roller 21 side with the sun roller 21. The contact portion is located near the minimum radius of the conical surface 22b (minimum radius dimension b). Further, in the double cone 22 on the lower side of the drawing, the contact portion of the conical generatrix 22c on the outer ring 15 side with the outer ring 6 is located near the minimum radius of the conical surface 22a (radius dimension c is the minimum), and the sun roller 21 is
The contact portion of the side conical generatrix 22d with the sun roller 21 is located near the maximum radius of the conical surface 22b (radius dimension b
maximum).

The flange portion 23b of the carrier 23 is provided with an extension portion 23c.
A female screw 23d is formed on 3c. A drive motor 25 is attached to the other end (on the output shaft (high-speed rotation shaft) 19 side) of the casing 11, and a male screw 26a is provided on the outer peripheral surface of the rotation shaft or the rotation shaft 26 directly connected to the rotation shaft. Are formed. And the carrier 23
The male screw 26a of the rotary shaft 26 of the drive motor 25 is screwed into the female screw 23d of the extended portion 23c. Therefore, when the rotary shaft 26 is rotated by the drive motor 16, the male screw 26a formed on the rotary shaft 26 is formed.
Extension portion 23 formed with internal thread 23d that is screwed into
The carrier 23 having c is configured to be movable in the input / output axis direction.

Here, in the conventional cone type continuously variable transmission 120 shown in FIG. 9, the rack 135 and the pinion gear 136 are screwed to each other, so that the rotational force in the direction orthogonal to the input / output shaft of the pinion gear 136 is changed to the rack. Since the driving motor is required to have a large driving force because it is converted into movement in the input / output axis direction by the 135, in the embodiment of FIG. , The movement of the carrier 23 in the input / output axis direction is converted via the extended portion 23c of the carrier 23, the movement of the carrier 23 can be performed smoothly, and the driving motor 25 is not required to have a large driving force. It can be made smaller, lighter, and cheaper.

Further, since the drive motor 25 is arranged parallel to the input / output axis direction, as compared with the case where the conventional drive motor for driving the pinion gear 136 is arranged in the direction orthogonal to the input / output axis direction, Since the casing 11 does not have a protruding portion in the radial direction, the speed increasing gear 10 for the wind power generator can be downsized.

Next, a speed increasing gear 10A for wind power generator according to a second embodiment of the present invention will be described with reference to FIG.

In the cone type continuously variable gearbox 10 shown in FIG.
When the transmission torque from the input shaft (low speed rotation shaft) 12 is transmitted to the outer ring 15 via the cam ring 14,
Pressure cam 17 that generates an axial force according to the transmission torque
However, on the output shaft (high speed rotation shaft) 19 side, the sun roller 21 is integrally formed with the output shaft (high speed rotation shaft) 19.
Is provided, and the pressure cam is not provided on the output shaft (high-speed rotation shaft) 19 side.

The cone type continuously variable gearbox 10A of the second embodiment shown in FIG. 2 has a structure in which pressure cams 17a and 17b are provided on both sides of the input side and the output side. That is, in FIG. 2, the pressure cam 17 a is provided between the support cam 14 a to which torque is transmitted from the input shaft (low-speed rotation shaft) 12 and the outer ring 15. Also, output shaft (high-speed rotation shaft)
19 and the sun roller 21 are formed separately, and the output shaft (high-speed rotation shaft) 19 is provided with a cam ring 14b,
The pressure cam 17 is also provided between the cam ring 14b and the sun roller 21 where torque is transmitted between the output shaft (high-speed rotation shaft) 19 and the sun roller 21.
b is provided. The pressure cams 17a and 17b for both the input and output shafts have the advantage that the normal force acting on the traction drive unit can be increased and the torque transmission efficiency can be improved.

Next, a cone type continuously variable gearbox 30 according to a third embodiment of the present invention will be described with reference to FIG. Figure 3
, 31 is a casing, 32 is an input shaft (low speed rotation shaft), 33 is a bearing, 34 is a cam ring, 35 is an outer ring, 36 is a bearing, 37 is a pressure cam, 38 is a disc spring,
Reference numeral 39 is an output shaft (high-speed rotation shaft), 40 is a bearing, 41 is a sun roller, 42 is a double cone, 43 is a carrier, 44 is a rotation support shaft thereof, 45 is a drive motor, and the above-mentioned components are as shown in FIG. Since it corresponds to the casing 11 or the drive motor 25 of the speed increaser 10 for the wind power generator, detailed description thereof will be omitted.

A big difference from the speed increasing gear 10 for the wind power generator of FIG. 1 is a mechanism portion for moving the carrier 43 in the input / output axis direction by the drive motor 45. That is, in the speed increasing gears 10 and 10A for wind power generators shown in FIGS. 1 and 2, the male screw 26a is formed on the outer peripheral surface of the rotary shaft 26 of the drive motor 25, and the female screw 23d is formed on the extended portion 23c of the carrier 23. In contrast to the configuration in which the male screw 26a is screwed into the female screw 23d, in the third embodiment, the power transmission member 47, that is, the power transmission member 47, is provided between the rotary shaft 46 of the drive motor 45 and the carrier 43. , The first gear 48 to the fourth
The gear 51 is interposed.

That is, the drive motor 45 has its rotary shaft 4
6 is attached to a mounting angle 53 fixed to the casing 31 without penetrating the casing 31 like the speed increaser 10 for a wind power generator of FIG. 1, and the rotary shaft 46 has a peripheral surface portion. A first gear 48 having teeth 48a is fixed to it. A shaft 54 is fixed to the casing 31, and a second gear 49 having a tooth 49a screwed to the tooth 48a of the first gear 48 on the outer peripheral surface thereof is mounted on the shaft 54 via a bearing. A third gear 50, which is rotatably mounted and integrally formed with the second gear 49, has teeth 50a formed on its outer peripheral surface.

Further, the casing 31 has a rotating member, that is, a tooth 51a which is screwed with the tooth 50a of the third gear 50, is formed on the outer peripheral surface of the casing 31 through a bearing 52 having a ball-shaped rolling element. Four gears 51 are rotatably attached. The fourth gear 51 is provided with an extension portion 51b in the input / output axis direction, and an inner peripheral surface of the extension portion 51b is internally threaded with a male thread 43a formed on the outer peripheral surface of the carrier 43. Are formed.

In FIG. 3, the flange portions 43A and 43B of the carrier 43, which rotatably supports the rotary support shaft 44 of the double cone 42, are the same as those of the wind power generator speed-up gears 10 and 10A shown in FIGS. Differently, it is manufactured separately from the carrier 43, and is fixedly integrated with the carrier 43 by welding or other structure. The reason is that, as described above, the male screw 43a is formed on the outer peripheral surface of the carrier 43, and thus the manufacturing die becomes complicated when integrated. However,
The carrier 43 and the flange portions 43A and 43B may be integrally formed.

Further, the casing 31 and the carrier 43
In between, a sliding member 55 made of a material having high wear resistance such as super steel is attached to the casing 31 side,
Between the sliding member 55 and the carrier 43, the needle 5
A large number of 6 are interposed along the circumferential surface of the sliding member 55, with the length direction parallel to the input / output axis direction. The sliding member 55 and the needle 56 are in line contact with each other along the input / output axis direction so that the carrier 43 can be smoothly moved in the input / output axis direction.

According to the speed increasing gear 30 for the wind power generator of FIG.
The rotation of the drive motor 45 causes the rotation shaft 46 to rotate, and the rotation operation of the first gear 48 fixed to the rotation shaft 46 causes the second gear 49 to be screwed into the first gear 48.
Rotates about the axis of the shaft 54. Also, this second
The rotation operation of the gear 49 causes the third gear 50 integrated with the second gear 49 to rotate. By the rotation operation of the third gear 50, the fourth gear 51, which is a rotating member screwed with the third gear 50, rotates around the output shaft (high-speed rotation shaft) 39. By the rotation operation of the fourth gear 51, the carrier 43 formed with the male screw 43a screwed to the female screw 51c formed on the inner peripheral surface of the extension portion 51b moves in the input / output axis direction.

According to the speed increasing gear 30 for the wind power generator of FIG. 3, the speed increasing gears 10, 10A for the wind power generator of FIGS. 1 and 2 are used.
Compared with, there are the following advantages. That is, in the speed increasing gears 10 and 10A for wind power generators of FIGS. 1 and 2, the extension portion 23c is provided for one of the plurality of flange portions 23b of the carrier 13, and the extension portion 23c is provided.
To the female screw 23d provided on the rotary shaft 26 of the drive motor 25.
The male screw 26a formed on the outer peripheral surface of the carrier is screwed to move the carrier 23 in the input / output axis direction.
It is unavoidable that an unbalanced load is applied to. Due to this uneven load, the carrier 23 is unevenly worn or the carrier 2
The female screw 23d of No. 3 may break.

In order to prevent such an unbalanced load, for example, the extension portion 2 is formed on the entire flange portion 23b of the carrier 23.
3c may be provided and screwed with the male screw 26a of the rotary shaft 26 of the drive motor 25 corresponding to each extended portion 23c. It is not a good idea to increase the size of the speed increaser 10 for machines and also to increase the price.

On the other hand, in the wind power generator speed-up gear 30 of FIG. 3, the rotational force of one drive motor 45 is transmitted through the power transmission member 47, that is, the first gear 48 to the third gear 50. Female screw formed on the inner peripheral surface of the extension portion 51b of the fourth gear 51 by transmitting to the fourth gear 51, which is a rotating member, and rotating the fourth gear 51 around the output shaft (high-speed rotation shaft) 39. Since the carrier 43 having the male screw 43a to be screwed with 51c is moved in the input / output axis direction, the rotating member 47 can increase the driving force.

Further, as described above, since the carrier 43 is supported by the bearing 52 and the needle 56 by the structure in which the needle 56 is interposed between the carrier 43 and the sliding member 55, the carrier 43 is inserted. Since the inclination with respect to the output shaft direction is prevented, the above-mentioned unbalanced load is not applied to the carrier 43, and the stress applied to the needle 56 can be reduced, the carrier 43 can be smoothly moved in the input / output axis direction.

Next, a speed increasing device 60 for a wind turbine generator according to a fourth embodiment of the present invention will be described with reference to FIG.

In each of the embodiments shown in FIGS. 1, 2 and 3, the description has been given of the case where the cone type stepless speed increasing gear is used alone to construct the speed increasing gear for the wind power generator. It is necessary to increase the diameter of the double cone in order to obtain the speed increasing ratio required for the generator only with the machine, and the cone type continuously variable speed increasing machine becomes large and heavy, and becomes expensive. Therefore, it is a good idea to connect the fixed gear ratio type speed increasing gear to the input side of the cone type continuously variable speed increasing gear.

That is, in a general wind power generator, the rotor speed of 10 to 100 revolutions per minute is increased to about the rated speed of the generator by the speed increaser. A certain speed increase ratio is required. One of the effective means for obtaining such a high speed increasing ratio is, as shown in FIG. 4, a fixed gear ratio type increase between the rotating main shaft 4 of the rotor 2 having the blade 3 and the generator 5. It is conceivable to interpose a speed increaser 6 in which a speed reducer (planetary roller type speed increaser or gear type speed increaser) 7 and a variable speed ratio type speed increaser (cone type continuously variable speed increaser) 8 are combined.

In this case, it is also possible to connect the output shaft (high-speed rotating shaft) of the existing separately configured planetary roller type speed increaser to the input shaft (low-speed rotating shaft) of the cone type continuously variable speed increaser. However, doing so makes the gearbox large, heavy, and expensive. Therefore, it is possible to reduce the size, weight and cost of the speed increaser by housing the planetary roller type speed increaser and the cone type continuously variable speed increaser in a single casing to form a compound speed increaser. It's a good idea.

FIG. 5 shows an example of such a wind turbine generator having a compound type gearbox in which a planetary roller type gearbox 70 and a cone type continuously variable gearbox 80 are housed in a casing 61. The structure of the speed machine 60 is shown. Here, the planetary roller type speed increaser 70 is arranged on the input side of the cone type continuously variable transmission 80.

The casing 61 has a tubular member 611.
And the inside of the tubular member 611, the planetary roller type speed increaser 7
A partition member 612 for partitioning the 0 side and the cone type continuously variable speed increaser 80 side, an end member 613 for closing one open end of the tubular member 611, and another open end of the tubular member 611 for closing. And an end member 614 for

Further, the planetary roller type speed increaser 70 has a bearing 72 that rotatably supports an input shaft (low speed rotation shaft) 71 that is provided so as to penetrate the end member 613 on one side of the casing 60. , A sun roller 74 divided into two intermediate shafts 73 arranged coaxially with the input shaft (low-speed rotation shaft) 71.
a and 74b are attached via a support cam 75 and a pressure cam 76, and an outer ring 77 is arranged around the intermediate shaft 73 so that their axial centers coincide with each other. The outer ring 77 is attached to the partition member 612 of the casing 60. Fixed to
In the space formed between the sun rollers 74a, 74b and the outer ring 77, a plurality of cylindrical planetary rollers 78 are rotatably supported by a carrier 79 at equal intervals in the circumferential direction. It is configured integrally with the input shaft (low speed rotation shaft) 71. Incidentally, reference numeral 76a is a disc spring, and by the combined force of the pressing force in the input / output axis direction by the spring force and the pressing force in the input / output axis direction by the pressure cam 76,
This is to increase the normal force acting on the contact portion between the sun rollers 74a and 74b and the planet roller 78.

The cone type continuously variable speed increaser 80 has an intermediate shaft 8 connected to the intermediate shaft 73 via a coupling 81.
2, an outer ring 85 attached to the intermediate shaft 82 via a support cam 83 and a pressure cam 84, a conical surface 86a in pressure contact with a rolling surface of an inner peripheral portion of the outer ring 85, and an outer periphery of a sun roller described later. Double cone 86 having a conical surface 86b in pressure contact with the rolling surface of the section, an output shaft (high-speed rotating shaft) 87 rotatably attached to the other end member 614 via a bearing 88, and this output shaft A sun roller 89 mounted on a (high-speed rotation shaft) 87 and in pressure contact with the conical surface 86b of the double cone 86, and a carrier for press-fitting one end 90a and the other end 90b of the rotation support shaft 90 of the double cone 86. 91 flanges 91a, 91b and a female screw 91d formed on an extension 91c of the flange 91b of the carrier 91.
A drive motor 92 attached to the other end 614 of the casing 61, and a male screw 93a formed on the outer peripheral surface of the rotary shaft 93 of the drive motor 92. The male screw 93a is screwed into the female screw 91d. ing. Reference numeral 94 is a disc spring that applies a predetermined axial pressing force between the outer ring 85 and the double cone 86.

The compound type gearbox 60 having the above-mentioned structure is
In the planetary roller speed increaser 70, the rotation of the rotary shaft (low speed rotary shaft) 71 causes the carrier 79 to rotate, and the rotation of the carrier 79 causes the planetary roller 78 to rotate and revolve around the intermediate shaft 73. On the other hand, power is transmitted between the sun roller 74 b and the support cam 75 via the pressure cam 76. At the left end of the sun roller 74a in the drawing and the right end of the support cam 75 in the drawing, spacers (annular members) whose axial movement is restrained with respect to the intermediate shaft 73 by nuts or retaining rings are provided. Pressure cam 7
Axial pressing force according to the transmission torque by 6 acts not only on the sun roller 74b but also on the sun roller 74a.
Further, power is transmitted between the sun roller 74a and the intermediate shaft 73 by a power transmission means such as a key or a spline, or by integration such as press fitting.

Further, in the cone type continuously variable gearbox 80, the power is transmitted between the support cam 83 and the outer ring 85 via the pressure cam 84, and the pressure cam 84 is used.
Thus, an axial pressing force according to the transmission torque acts on the outer ring 85. Further, power is transmitted between the intermediate shaft 82 and the support cam 83 by a power transmission means such as a key or a spline, or an integration such as press fitting. Further, power is transmitted between the intermediate shaft 73 and the intermediate shaft 82 by power transmission means such as a spline.

The composite type speed increaser 60 is a combination of a planetary roller type speed increaser 70 and a cone type continuously variable transmission 80. With the continuously variable transmission 80,
Compared with the case of a single cone type continuously variable gearbox, a higher speedup ratio can be obtained, and further, the speedup ratio of the cone type continuously variable transmission 80 can be made smaller. Can be reduced, and thus the casing 61
It also has the advantage that the radial size can be reduced, and the weight and cost can be reduced.

Although the above embodiments have been described with respect to specific configurations, the present invention is not limited to these embodiments, and various modifications are possible.

For example, in FIG. 5, the planetary roller type speed increaser 7 is used.
Although the cone type continuously variable gearbox 80 shown in FIG. 1 is used as the cone type continuously variable gearbox 80 to be combined with 0, the pressure cams 17a, 17 are provided on both sides of the input and output shown in FIG.
A cone type continuously variable speed increasing gear 10A having a b may be used, or a cone type continuously variable speed increasing gear in which a power transmission member 47 is interposed between the rotary shaft 46 of the drive motor 45 and the carrier 43 shown in FIG. The machine 30 may be used.

Further, instead of the pressure cam, a mechanism using only a spring to apply a constant pressure may be used. Further, the present invention can be applied to the case where the cone-type continuously variable speed increaser is used as a speed increaser for a wind power generator regardless of the type of the pressurizing mechanism.

Further, although the carrier 43 and the flange portions 43A and 43B are separate bodies in FIG. 3, they may be integrally molded. Further, the carrier 43 is provided with a male screw 43a,
Although the extended portion 51b of the fourth gear 51 is provided with the internal thread 51c, the carrier 43 is provided with the internal thread 51c.
A male screw may be provided on the extension portion 51b of the.

Furthermore, FIG. 1, FIG. 2, FIG. 4 and FIG.
In the embodiment, the feed screw mechanism is a slide screw such as a triangular screw or a trapezoidal screw, but a ball screw may be used.

[0093]

As described above, according to the present invention, at least the input shaft and the output shaft are arranged coaxially, and the outer ring whose inner peripheral surface is a rolling surface and the sun roller whose outer peripheral surface is a rolling surface are provided. The input / output shaft is provided coaxially, and rotation is transmitted between the input shaft and the outer ring by the rotation transmission means, and rotation is transmitted between the sun roller and the output shaft by the rotation transmission means. Three or more double cones that are in contact with each other are rotatably held by the carrier at equal intervals in the circumferential direction, and the carrier whose rotation around the axis of the input / output shaft is restricted is moved in the axial direction to continuously change the speed. In a speed increasing gear for a wind power generator having a cone-type continuously variable transmission, a feed screw mechanism for axially moving the carrier is provided. Al, since as compared with the conventional gear type speed increaser, a power transmission by the traction drive,
The noise and vibration levels can be reduced, and as a result, good-quality generated power that does not include harmonic components due to vibration can be obtained. Further, as compared with the conventional fixed speed increasing ratio type planetary roller type speed increaser, the speed increasing ratio can be made higher at low speed, so that the generated power shortage at low speed does not occur. Further, compared to the conventional rack and pinion gear type carrier moving mechanism, the carrier can be smoothly moved in the input / output axis direction with a small driving torque.

Further, a rotary member is interposed between the rotary shaft of the drive motor and the carrier to form a female screw on the inner peripheral surface of the rotary member and a male screw on the outer peripheral surface of the carrier to form the rotary member. When the male screw of the carrier is screwed into the female screw of (4), an unbalanced load of the carrier can be prevented, and the carrier can be moved more smoothly in the input / output axis direction.

Furthermore, when the fixed gear ratio type speed increaser and the variable gear ratio type speed increaser are combined, a large speed increase ratio can be obtained even in a weak wind, and the generator can be rotated at the rated speed. You can Further, when the wind is strong, the number of revolutions can be reduced by the variable gear ratio type speed increaser, and the generator can be operated at the rated number of revolutions, so that it is possible to obtain high-quality generated power.

Furthermore, when the fixed gear ratio type speed increaser having a large torque transmission capacity is arranged on the input side with respect to the variable gear ratio type speed increaser, a large torque transmission capacity is obtained and at the same time, the variable gear ratio is increased. The transmission torque of the mold speed increaser can be reduced to improve durability.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a speed increasing gear for a wind power generator according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of a main part of a speed increaser for a wind power generator according to a second embodiment of the present invention.

FIG. 3 is a cross-sectional view of a speed increasing gear for a wind power generator according to a third embodiment of the present invention.

FIG. 4 is a schematic configuration diagram of a wind power generator using a speed increaser for a wind power generator according to a fourth embodiment of the present invention.

FIG. 5 is a cross-sectional view of a speed increaser for a wind power generator according to a fourth embodiment of the present invention.

FIG. 6 is a schematic configuration diagram of a general wind power generator.

FIG. 7A is a schematic configuration diagram of a wind power generator using a conventional fixed gear ratio type gearbox, and FIG. 7B is a planetary roller type gearbox which is an example of a fixed gear ratio type gearbox. It is an exploded perspective view.

FIG. 8 is a schematic configuration diagram of a wind power generator using a conventional variable gear ratio type speed increaser.

FIG. 9 is a cross-sectional view of a cone type continuously variable gearbox which is an example of a conventional variable gear ratio type gearbox.

FIG. 10 is a side sectional view of a main part for explaining a variable gear ratio operation of the cone type continuously variable gearbox.

[Explanation of symbols]

1 Wind power generator 2 Rotor 3 Blade 4 Main shaft 5 Generator 6,60 Combined type gearbox 7,70 Fixed gear ratio type gearbox (planetary roller type gearbox) 8,80 Variable gear ratio type gearbox ( Cone type continuously variable gearbox) 10, 10A, 30 Gearbox for wind power generator 12, 32, 71 Input shaft (low-speed rotating shaft) 13, 20, 33, 40, 52, 72, 88 Bearing 15, 35, 77, 85 Outer ring 17, 17a, 17b, 37, 76, 84 Pressure cam 18, 38, 76a Disc spring 19, 39, 87 Output shaft (high speed rotation shaft) 21, 41, 74, 89 Sun roller 22, 42, 86 double cone 22a, 22b, 42a, 42b, 86a, 86b conical surface 22c, 22d conical generatrix 23, 43, 79, 91 carrier 23a, 23b, 43A, 43B, 91a, 91b flange part 2 of carrier 3c, 91c Carrier extended portions 23d, 91d Female screws 25, 45, 92 Drive motors 26, 46, 93 Rotating shafts 26a, 43a, 93a Male screw 47 Power transmission members 48-50 First gear to third gear 51 Rotating member (first 4b) 51b Extension part 51c of the 4th gear in the input / output axis direction Female screw 54 Shaft 56 Needle 73, 82 Intermediate shaft 78 Planetary roller

Claims (5)

[Claims] 1. An input / output shaft is coaxially provided with at least an input shaft and an output shaft arranged coaxially, and an outer ring having an inner peripheral surface as a rolling surface and a sun roller having an outer peripheral surface as a rolling surface. The rotation is transmitted between the input shaft and the outer ring by the rotation transmission means, the rotation is transmitted between the sun roller and the output shaft by the rotation transmission means, and the three or more double cones that are in contact with the outer ring and the sun roller are carriers. Cone-type continuously variable transmission, which is rotatably held at equal intervals in the circumferential direction and is capable of continuously variable transmission by moving in the axial direction a carrier whose rotation around the axis of the input / output shaft is restricted. A speed increaser for a wind power generator, comprising a feed screw mechanism for axially moving the carrier. 2. A female screw of the feed screw mechanism is provided on the carrier, a rotary shaft having a male screw is screwed to the female screw, and a drive motor for driving the rotary shaft is provided. A speed increaser for a wind power generator according to. 3. A screw having a male screw or a female screw coaxial with the input / output shaft, which is provided on the carrier, or a separate member having the female screw or the male screw is integrated with the carrier and meshed with the female screw or the male screw. 2. The speed increasing gear for a wind power generator according to claim 1, further comprising a drive motor that drives a rotating member that has a portion and is restricted from moving in the axial direction. 4. The rotating member is rotatably attached to the casing via a bearing, and the carrier is restricted from rotating by the casing via a needle,
The speed increaser for a wind power generator according to claim 3, wherein the speed increaser is attached so as to be movable in the axial direction. 5. A planetary roller type transmission is arranged on the input side of the cone type continuously variable transmission.
5. The speed increasing gear for a wind power generator according to any one of 4 to 4.