JP2013257045A - Method for designing vertical-axis wind turbine bearing and vertical-axis wind turbine bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a method for designing a vertical-axis wind turbine bearing, capable of improving power generation efficiency by smoothly rotating a shaft.SOLUTION: A method for designing a bearing rotatably supporting a vertical shaft of a vertical-axis wind turbine selects a bearing located in a region I surrounded by curves, by evaluating a curve indicative of a relation between rolling-groove curvatures and ball ratios for satisfying a load rating required for the bearing, a curve indicative of a relation between rolling-groove curvatures and ball ratios for satisfying a static rating required for the bearing, and a curve indicative of a relation between rolling-groove curvatures and ball ratios for satisfying a start torque required for the bearing.

Description

  The present invention relates to a design method for a vertical axis wind turbine bearing and a vertical axis wind turbine bearing.

  For example, a wind power generator using a flow of wind (working fluid) has been developed as a vertical axis fluid power generator that generates power using a fluid flow. Such a vertical axis type wind turbine generator is arranged with a shaft body, a plurality of blades (windmills) connected to the shaft body, and a bearing, arranged at intervals around the central axis of the shaft body. A support body that rotatably supports the shaft body around a central axis, and a generator that generates electric power by converting mechanical energy obtained by rotating the shaft body in the circumferential direction into electric energy.

  For example, in the wind turbine generator described in Patent Document 1, a rotating mechanism (shaft) integrated with a vertical blade (blade) extends in a vertical direction (a direction perpendicular to a horizontal plane) with respect to the ground. In addition, a pair of bearings (ball bearings) are provided and supported by an intermediate fixed shaft (support) in a state where the bearings are rotatable.

JP 2006-207374 A

  However, the conventional vertical wind power generator has the following problems. That is, the shaft body is set to a diameter necessary for securing the strength, and a ball bearing distributed in the market such as 70XX system is selected in accordance with the diameter. However, the ball bearing selected in this way has an excessive load rating (overspec). Further, since the load capacity (dynamic load rating or static load rating) of the ball bearing is large, the torque resistance is also increased. For this reason, there is a problem that the rotation of the shaft body (especially in the low wind speed region) is hindered to reduce the power generation efficiency, resulting in an inefficient windmill.

  The present invention has been made in view of such circumstances, and a design method for a vertical shaft type wind turbine bearing capable of increasing the power generation efficiency by reducing the torque resistance and smoothly rotating the shaft body. An object is to provide a shaft type wind turbine bearing.

  The present invention relates to a design method of a bearing that rotatably supports a vertical axis of a vertical axis type wind turbine, a curve showing a relationship between a rolling groove curvature and a ball ratio to satisfy a dynamic load rating required for the bearing; A curve showing the relationship between the rolling groove curvature and the ball ratio for satisfying the static load rating required for the bearing, and the relationship between the rolling groove curvature and the ball ratio for satisfying the starting torque required for the bearing. Curves are obtained, and a bearing in a region surrounded by these curves is selected.

  A vertical axis wind turbine bearing according to the present invention is characterized by being designed by the above-described method for designing a vertical axis wind turbine bearing.

  According to the present invention, it is possible to realize a vertical shaft type wind turbine bearing that has a small torque resistance and can smoothly rotate a shaft body to increase power generation efficiency.

1 is an external view showing a vertical axis wind power generator according to a first embodiment of the present invention. 1 is a side sectional view showing a vertical axis wind power generator according to a first embodiment of the present invention. It is a figure which shows the bearing which concerns on 1st embodiment of this invention. This is a graph of the relationship curve between rolling groove curvature and ball ratio to satisfy the required performance of the bearing. It is a sectional side view which shows the vertical axis type wind power generator and bearing which concern on 2nd embodiment of this invention.

Embodiments of the present invention will be described below with reference to the drawings.
(First embodiment)
FIG. 1 is an external view showing a vertical axis wind power generator 10 according to the first embodiment. FIG. 2 is a side sectional view showing the vertical axis wind power generator 10.
As shown in FIGS. 1 and 2, a vertical axis wind power generator (vertical axis fluid power generator) 10 is obtained by a rotating mechanism 10A that rotates in response to wind (working fluid) W, and the rotating mechanism 10A. A power generation mechanism 10B that converts mechanical energy into electrical energy.
The rotating mechanism 10A includes a wind turbine 1 that receives the wind W, a rotating shaft (shaft body) 2 connected to the wind turbine 1, and a casing that supports the rotating shaft 2 so as to be rotatable around the central axis C via a bearing 3 (support Body) 4.
The power generation mechanism 10B includes a generator 5 that generates electric power by converting mechanical energy obtained by rotating the rotating shaft 2 in the circumferential direction (around the central axis C) into electric energy.
The rotation mechanism 10A and the power generation mechanism 10B are disposed on an upper portion of a tower (post) 6 that is erected on the ground F and extends in the vertical direction.

The windmill 1 is a so-called gyromill type windmill. The windmill 1 has a rectangular plate shape or a belt plate shape and includes a plurality of blades 1A extending in the vertical direction with the ground F. The plurality of blades 1 </ b> A are arranged around the central axis C of the rotating shaft 2 at equal intervals in the circumferential direction. The plurality of blades 1A are connected to the rotary shaft 2 via a plurality of arms 1B that support them.
The blade 1A is formed in a shape that generates lift when receiving the wind W. The wind turbine 1 rotates around the central axis C of the rotating shaft 2 by this lift.
The windmill 1 has no dependency on the wind direction. That is, the wind turbine 1 is set to a shape that can rotate around the central axis C of the rotation shaft 2 with respect to the wind W from any direction.

  As shown in FIG. 2, the rotating shaft 2 to which the windmill 1 (blade 1 </ b> A) is connected is arranged to extend in the vertical direction so that the central axis C is perpendicular to the ground F. The rotary shaft 2 is rotatably supported with respect to the casing 4 via the bearing 3.

  One end of an arm 1B having a rectangular plate shape or a strip plate shape is connected to the outer peripheral surface of the rotary shaft 2, and a plurality of protrusions project radially outward. These arms 1 </ b> B are arranged at equal intervals in the circumferential direction of the rotating shaft 2. The blade 1A is connected to the other end of the arm 1B. A pair of arms 1B are provided in parallel to be spaced apart in the direction of the central axis C with respect to one blade 1A.

The rotating shaft 2 is rotatably supported with respect to the casing 4 by providing bearings 3 in the vicinity of the center portion and in the vicinity of the lower end portion thereof. The bearing 3 includes radial bearings 13 that are separated from each other in the direction of the central axis C of the rotary shaft 2 and double-row angular bearings 14A and 14B.
The radial bearing 13 is disposed at the end of the rotating shaft 2 on the generator 5 side in the direction of the central axis C. Specifically, the inner ring 15 of the radial bearing 13 is fixed to the lower end side of the rotary shaft 2.
Double-row angular bearings 14A and 14B are arranged on the windmill 1 side of the rotation shaft 2 in the direction of the central axis C. Specifically, the inner rings 17 and 17 of the double-row angular bearings 14 </ b> A and 14 </ b> B are fixed to the central portion of the rotary shaft 2.

The casing 4 is formed in a multistage cylindrical shape in which the upper portion 4A on the wind turbine 1 side (one side) is reduced in diameter than the lower portion 4B on the tower 6 side (the other side) opposite to the wind turbine 1. In the casing 4, the lower end portion of the lower portion 4 </ b> B is connected to the upper end portion of the tower 6.
Outer rings 18 and 18 of angular bearings 14A and 14B are fixed to the inner peripheral surface of the upper portion 4A of the casing 4 on the upper end side. An outer ring 16 of the radial bearing 13 is fixed to the inner peripheral surface of the upper portion 4A of the casing 4 on the lower end side.
The radial bearing 13 and the angular bearings 14A and 14B of the bearing 3 have a plurality of balls 7 having the same diameter. It has a plurality of balls 7 of the same diameter.

Note that the vertical positions of the radial bearing 13 and the angular bearings 14A and 14B may be set opposite to the above. That is, the radial bearing 13 may be disposed on the wind turbine 1 side of the rotating shaft 2, and the angular bearings 14 </ b> A and 14 </ b> B may be disposed on the generator 5 side of the rotating shaft 2.
Further, the angular bearings 14A and 14B may be face-to-face alignment or parallel alignment other than back-to-back alignment.

Inside the lower portion 4B of the casing 4, a generator 5, a control unit (not shown), and the like are accommodated.
The generator 5 generates electric power by converting the rotational force (mechanical energy) obtained by the rotation of the rotary shaft 2 into electric energy.
The generator 5 includes a magnet rotor 8 that is connected to the lower end of the rotating shaft 2 and rotates together with the rotating shaft 2, and a coil stator 9 that is disposed so as to surround the outer peripheral side of the magnet rotor 8.

With such a configuration, when the windmill 1 receives the wind W and rotates the rotary shaft 2 around the central axis C, the magnet rotor 8 connected to the rotary shaft 2 also rotates around the central axis C. That is, the magnet rotor 8 rotates on the same axis (center axis C) as the windmill 1 and the rotating shaft 2.
Then, when the magnet rotor 8 rotates about the central axis C with respect to the coil stator 9, electromagnetic induction is generated between the magnet rotor 8 and the coil stator 9, and electric power is generated.

Next, the required performance of the bearing 3 that supports the rotating shaft 2 will be described in detail.
FIG. 3 is a view showing the bearing 3 according to the first embodiment.
It is desired that the rotary shaft 2 of the vertical axis type wind power generator 10 rotates efficiently and lightly. For this reason, the bearing 3 used for the rotating shaft 2 is required to be supported so that the rotating shaft 2 rotates even when the wind turbine 1 receives wind W having a weak wind speed.
For this reason, the bearing 3 (radial bearing 13 and angular bearings 14A and 14B) needs to have as little starting torque and rotational torque as possible.
On the other hand, since the bearing 3 that supports the rotating shaft 2 receives an external force (wind W received by the wind turbine 1) having a large fluctuation over a long period of time, it has a sufficient static load capacity (basic static load rating) and dynamics. It is necessary to have performance that satisfies the dynamic load capacity (basic dynamic load rating).
Therefore, the bearing 3 needs to have a small rated torque while having a sufficient rated load.

  Among the specifications (performance) of the bearing 3, it is known that the shape parameters that determine the rotational torque and the rated load (basic static load rating / basic dynamic load rating) include the following four items.

(1) Ball diameter Dw
(2) Rolling groove curvature α (α = R / Dw, R = rolling groove radius)
(3) Ball center diameter Dpw
(4) Number of balls z

  Generally, when the numerical values of (1), (3), and (4) are increased, the rotational torque and the rated load are also increased. On the other hand, it is known that when the numerical value of (2) is increased, the rotational torque and the rated load are reduced. For this reason, the balance of these four parameters is important.

On the other hand, the diameter d1 of the rotating shaft 2 is almost inevitably determined (more than the necessary minimum diameter) from conditions (usage conditions) such as maximum wind force received by the windmill 1. And since the internal diameter d of the bearing 3 is the same as the diameter d1 of the rotating shaft 2, it is determined inevitably.
When the inner diameter d of the bearing 3 is determined, (3) the ball center diameter Dpw is derived by (1) determining the ball diameter Dw.
Further, (4) the number of balls z is derived by determining (1) the ball diameter Dw and (3) the ball center diameter Dpw. This is because the maximum number of balls B that can be placed on the track is physically determined. If the number of balls z is reduced, the load per ball B increases and the reliability decreases, which is not realistic.

Then, when designing (adopting) the optimum bearing 3 for the rotating shaft 2 of the wind turbine 1, it can be understood that (1) the ball diameter Dw and (2) the rolling groove curvature α are two important parameters. .
Therefore, in order for the bearing 3 to have a sufficient load capacity and low rotational torque, the bearing 3 needs to satisfy the following conditions.
(I) The ball diameter Dw is reduced.
(Ii) Increase the rolling groove curvature α.

And in order to design (adopt) the bearing 3 which satisfy | fills the conditions mentioned above, the following procedures are performed.
First, the performance required for the bearing 3 that supports the rotating shaft 2 is obtained from the specifications (use conditions) of the wind turbine 1. Specifically, the rated load (basic dynamic load rating / basic static load rating) and starting torque required for the bearing 3 are obtained.
Next, for each of the obtained required performance (basic dynamic load rating, basic static load rating and starting torque), (1) relationship between ball diameter Dw and (2) rolling groove curvature α to satisfy the required performance ( (Relation curve).

FIG. 4 is a graph showing a relationship curve between the ball ratio β and the rolling groove curvature α for the bearing 3 to satisfy the required performance. FIG. 4 shows a case where the wind receiving area of the windmill 1 is 9 m ² . The wind condition is IEC 61400-2 class IV.
In IEC 61400-2, a windmill having a wind receiving area of 2 m ^{2 to} less than 200 m ² is referred to as a small windmill.

  In FIG. 4, the vertical axis represents the ball ratio β, and the horizontal axis represents the rolling groove curvature α. The vertical axis indicates (1) not the ball diameter Dw itself but the ratio of the ball diameter Dw to the diameter d1 of the rotating shaft 2 (ball ratio β). Since the diameter d1 of the rotating shaft 2 is not necessarily designed to the minimum necessary size, the ball ratio β is used.

  Ball ratio β = Dw / d (Dw = ball diameter, d = rotating shaft diameter)

  As described above, the bearing 3 needs to satisfy the rated load and the starting torque. The bearing 3 must satisfy at least one of the basic dynamic load rating and the basic static load rating, and further satisfy the starting torque. More preferably, the bearing 3 is desired to satisfy all of the basic dynamic load rating, the basic static load rating, and the starting torque.

In the case of FIG. 4, if (1) the ball diameter Dw and (2) the rolling groove curvature α of the bearing 3 are plotted in the regions I, II and III, the vertical axis wind power generator It can be understood that it is suitable as a bearing used for ten rotating shafts 2.
Furthermore, it is optimal that (1) the ball diameter Dw and (2) the rolling groove curvature α of the bearing 3 are plotted in the region I. Approximately (1) The ball diameter Dw is 20% or less. Preferably, it is 10% to 15%. (2) The rolling groove curvature α is 54% to 100%. Preferably, it is 55% to 65%.
For example, the bearing 3 having a rolling groove curvature α = 60% and a ball ratio β = 12% may be designed (adopted).

When the ball diameter Dw exceeds 20%, it is difficult to satisfy both the rated load and the starting torque. Further, if the ball diameter Dw is too large with respect to the diameter of the rotating shaft 2, the number of balls 7 that can be disposed on the bearing 3 is reduced, and the load per ball 7 becomes excessive, which is realistic. is not. Furthermore, generally, a ball having a diameter that is too small or a large ball (especially, 1 inch or more in diameter) has low marketability and increases costs.
For this reason, the ball diameter Dw is preferably 20% or less.

When the ball diameter Dw is less than 10%, it is difficult to satisfy both the rated load and the starting torque.
For this reason, the ball diameter Dw is preferably 10% or more.

When the rolling groove curvature α is less than 54%, it is difficult to satisfy both the rated load and the starting torque, as in the case where the ball diameter Dw is 10% or less.
For this reason, the rolling groove curvature α is preferably 54% or more.

When the rolling groove curvature α exceeds 100%, it is difficult to satisfy both the rated load and the starting torque, as in the case where the ball diameter Dw exceeds 20%.
For this reason, the rolling groove curvature α is preferably 100% or less.

As described above, in the vertical axis wind power generator 10 according to the first embodiment, the bearing 3 has a sufficient rated load because (i) the ball diameter Dw is small and (ii) the rolling groove curvature α is large. Rotational torque is small.
Therefore, even when the windmill 1 receives the wind W having a weak wind speed, the rotary shaft 2 is pivotally supported so as to rotate. Moreover, the external force (wind W which the windmill 1 receives) with a big fluctuation | variation can be received over a long period of time. Therefore, the vertical axis wind power generator 10 can generate power with high efficiency.

(Second embodiment)
FIG. 5 is a side sectional view showing the vertical axis wind power generator 20 and the bearing 23 according to the second embodiment.
Below, a different point from the vertical axis wind power generator 10 and the bearing 3 which concerns on 1st embodiment is demonstrated, and description is abbreviate | omitted etc. about the member etc. which are the same as the vertical axis wind power generator 10 and the bearing 3.

The rotary shaft 22 of the vertical axis wind power generator 20 is supported by a bearing 23. The bearing 23 includes the above-described radial bearing 13 and angular bearings 24A and 24B.
In the rotating shaft 22 to which the windmill 1 is connected, a rolling groove 33 in which a plurality of balls 7 roll is formed in a portion where the double-row angular bearings 24A and 24B are provided. That is, the angular bearings 24A and 24B have only the outer ring 28 and do not have an inner ring. For this reason, a rolling groove 33 on which the ball 7 rolls is formed on the outer peripheral surface of the rotating shaft 22.
The rolling groove 33 has an annular shape extending in the circumferential direction on the outer peripheral surface of the rotating shaft 22 and is formed in a concave curve shape that is recessed toward the central axis C side.

Note that the vertical positions of the radial bearing 13 and the angular bearings 24A and 24B may be set opposite to the above. That is, the radial bearing 13 may be disposed on the wind turbine 1 side of the rotating shaft 2, and the angular bearings 24 </ b> A and 24 </ b> B may be disposed on the generator 5 side of the rotating shaft 2.
Further, the angular bearings 24A and 24B may be face-to-face alignment or parallel alignment other than back-to-back alignment.

The required performance of the bearing 23 that supports the rotary shaft 22 is the same as that of the bearing 3.
Therefore, in order to design (adopt) the bearing 23 that satisfies the above-described conditions, the same procedure as that for designing (adopting) the bearing 3 may be performed.
However, since the radial bearing 13 and the angular bearings 24A and 24B have different values of the radius d, the ball diameter Dw, the rolling groove radius R, the ball center diameter Dpw, and the number of balls z, it is necessary to design (adopt) them separately. is there. For example, the radius d of the angular bearings 24A and 24B is not the diameter d1 of the rotating shaft 22, but the diameter d2 of the portion where the rolling groove 33 is formed.

  Also in the vertical axis wind power generator 20 according to the second embodiment, since the bearing 23 has (i) a small ball diameter Dw and (ii) a large rolling groove curvature α, it has a sufficient rated load while having a rotational torque. Is small. Therefore, even when the windmill 1 receives the wind W having a weak wind speed, the rotary shaft 22 is pivotally supported so as to rotate. Moreover, the external force (wind W which the windmill 1 receives) with a big fluctuation | variation can be received over a long period of time. Therefore, the vertical axis wind power generator 20 can generate power with high efficiency.

  Various shapes, combinations, and the like of the constituent members shown in the above-described embodiments are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.

  The radial bearing may not be provided with an inner ring and a rolling groove may be formed on the rotating shaft 22.

  The radial bearing and the angular bearing may have only an inner ring, and may have a rolling groove on the inner peripheral surface of the casing 4 (upper portion 4A) without an outer ring.

The rotary shafts 2 and 22 are not limited to an integral structure, and may be a case where a plurality of shaft members are connected.
The pair of arms 1B may not be parallel to each other in the central axis C direction.
The ball diameters of the radial bearing 13 of the bearings 3 and 23 and the angular bearings 14A, 14B, 24A, and 24B may be the same or different.

  DESCRIPTION OF SYMBOLS 1 ... Windmill, 2 ... Rotating shaft (shaft body), 3 ... Bearing (vertical shaft type windmill bearing), 4 ... Casing (support body), 5 ... Generator, 7 ... Ball, 10 ... Vertical axis wind power generator 13 ... Radial bearings, 14A, 14B ... Angular bearings, 20 ... Vertical axis wind power generators, 22 ... Rotating shaft (shaft), 23 ... Bearings (bearings for vertical axis wind turbines), 24A, 24B ... Angular bearings, 33 ... rolling groove, C ... central axis

Claims (5)

In a method of designing a bearing that rotatably supports a vertical axis of a vertical axis type wind turbine,
A curve showing the relationship between the rolling groove curvature and the ball ratio to satisfy the dynamic load rating required for the bearing;
A curve showing the relationship between the rolling groove curvature and the ball ratio to satisfy the static load rating required for the bearing;
A curve showing the relationship between the rolling groove curvature and the ball ratio to satisfy the starting torque required for the bearing, and
A design method for a bearing for a vertical axis wind turbine, wherein a bearing in a region surrounded by these curves is selected.   2. The vertical according to claim 1, wherein a ratio of the diameter of the ball to the vertical axis is 10% or more and 15% or less, and a curvature of the rolling groove is 55% or more and 65 or less. Design method for shaft type wind turbine bearings.   3. The method for designing a vertical axis wind turbine bearing according to claim 1, wherein the bearing includes a pair of angular bearings and a radial bearing that is disposed apart from the pair of angular bearings. .   The design method of the bearing for a vertical axis type wind turbine according to any one of claims 1 to 3, wherein a rolling groove of the ball is formed on an outer peripheral surface of the vertical axis.   A vertical axis wind turbine bearing, which is designed by the method for designing a vertical axis wind turbine bearing according to any one of claims 1 to 4.

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