JP6144287B2 - Wind power generator - Google Patents

Description

The present invention is, for example, as in the main shaft bearing of a wind power generation apparatus, a wind power generation device that provides a single support capable bearing the shaft of the rotating body cantilevered that moment acts.

Conventionally, the size of a bearing such as a main shaft bearing structure of a wind turbine generator is determined based on either a maximum load or a fatigue load that is received during operation during the design life.
In the case of a general wind power generator, the fatigue load is about half of the maximum load. However, for example, there is a demand for a design in which a maximum load is set so as to withstand a storm that may be about once every 50 years even though the windmill life is 20 years. Therefore, the physique of the bearing structure of the wind power generator is determined based on a very large maximum load, which is considered to never act during the design life.

FIG. 20 shows a main shaft bearing structure of a wind turbine generator employing a double row tapered roller bearing. The double-row tapered roller bearing is an example of a bearing support structure that can independently support a shaft portion of a rotating body in a cantilever shape in which a moment acts.
In FIG. 20, on the front end side of the nacelle 3 installed at the upper end of the support 2, the rotor head (hub) 4 rotates by receiving wind power from the wind turbine rotor 5. The rotor head 4 includes a plurality of windmill rotor blades 5.

The rotor head 4 is a rotating body that rotates about the axis of the main shaft 7, and the main shaft front end 7 a of the power generation mechanism connected to the rear end of the rotor head 4 is rotatably supported by the double-row tapered roller bearing 10. Yes. Therefore, the double-row tapered roller bearing 10 whose outer ring side is fixedly supported by the nacelle 3 is a cantilever beam in which a rotating body shaft portion such as the rotor head 4 rotating on the front end side of the main shaft 7 acts on a single bearing. It is supported alone in the shape.
In addition, about the other end used as the rear-end part side of the main axis | shaft 7, there exists a power generation system which drives a generator via the speed increaser and hydraulic mechanism which are not shown in figure, or a power generation system which drives a generator directly.

  As a main shaft bearing structure of a wind power generator, for example, as shown in FIGS. 21 and 22, a bearing that supports the main shaft 7 by a pair of front and rear rolling bearings Bf and Br arranged at a predetermined interval in the axial direction. There is also a support structure. 21 and 22, reference numeral 3 a in FIG. 21 is a base plate (nacelle base plate) of the nacelle 3, Si is a speed increasing device, Ge is a generator, Rm is a reinforcing member, and Hc is a load load position at the center of the hub. It is.

  The following Patent Document 1 discloses a technology that can withstand an exposed load without becoming an excessive dimension in a wind power generation drive unit. In this prior art, the planetary carrier is provided with an additional support such as a support roller, and this support provides sufficient support for the rotor shaft.

  Reference 2 below relates to a wind turbine slewing ring bearing structure that supports a variable pitch blade so as to be capable of pivoting. The surface pressure difference distribution is flattened by flattening the load difference distribution, and the double row and the surface pressure are equalized. A technique for simultaneously realizing the above is disclosed.

JP 2009-162380 A Japanese Patent No. 4533642

By the way, recent wind power generators tend to be larger, and even when rolling bearings such as the above-mentioned double row tapered roller bearings are used for main shaft bearings, the maximum load is adopted instead of the fatigue load to determine the size of the bearing. ing.
FIG. 23 is an image diagram of the load size (vertical axis) and time scale (horizontal axis). In the load fluctuation accompanying the wind condition shown by the solid line, the peak load that occurs at the time of abnormalities such as storms is used for the static safety factor evaluation. This is the maximum load Lm to be used. On the other hand, the equivalent load (fatigue load) La used for life evaluation is an average value (indicated by a broken line) based on load fluctuations during normal power generation.

As is clear from FIG. 23, when the maximum load Lm and the equivalent load La are compared, the maximum load Lm becomes a large value of about twice, so the physique determination of the main shaft bearing based on the maximum load Lm is This will increase the size of the main shaft bearing.
In addition, the size of the main shaft bearing (rolling bearing such as a double-row tapered roller bearing) is inevitably increased due to the increase in the size of the wind power generator.

However, in order to increase the size of main shaft bearings such as double-row tapered roller bearings, not only higher machining accuracy is required compared to general-purpose bearings, but also the heat treatment furnace required for tempering is increased in size. Will do.
For this reason, when a rolling bearing such as a double-row tapered roller bearing or the like is employed as a bearing support structure for a main shaft of an enlarged wind turbine generator, a problem has been pointed out that the unit price of weight is higher than that of a general-purpose bearing.

  Further, in most cases, a double-row tapered roller bearing having a single bearing structure in which an axial load and a radial load are received by one bearing requires a ring material such as a sleeve in order to require incidental rigidity in either the inner or outer ring. Therefore, compared with a two-bearing structure in which dedicated bearings are provided in the axial direction and the radial direction, respectively, the nacelle as a whole can be reduced in weight and cost, but the weight unit cost is high when evaluated only around the main shaft bearing. was there.

From such a background, a bearing support structure that can cope with a maximum load in the unlikely event and that can adopt a fatigue load that is generally smaller than the maximum load is required for physique determination that corresponds to normal operation (power generation). .
Further, in a bearing support structure that supports the main shaft by a pair of front and rear rolling bearings, it is desired to reduce the radial load and the axial load borne by the rolling bearing and to suppress the increase in size of the bearing body.

The present invention has been made in view of the above circumstances, and the object of the present invention is to cope with a rare emergency maximum load, and to apply a fatigue load to determine the size of the bearing during normal operation. and to provide a wind turbine generator having a shaft receiving support structure that can be employed.
Further, the present invention reduces the radial load and axial load roller bearing to be borne also aims to provide a wind turbine generator having a shaft receiving support structure that can suppress an increase in the size of the bearing body size.

In order to solve the above problems, the present invention employs the following means.
A wind turbine generator according to a first aspect of the present invention includes a bearing support structure that includes a plurality of wind turbine rotor blades and rotatably supports a shaft portion of a rotor head that rotates about a horizontal axis. The bearing support structure includes a rolling bearing capable of independently supporting the rotor head shaft portion in the form of a cantilever beam on which a moment acts, and an auxiliary bearing that supports the shaft rear end side of the rolling bearing. And the rolling bearing alone supports the shaft portion during normal operation in which a load of a predetermined value or less acts, and the auxiliary bearing provides the shaft only in emergency operation in which a large load exceeding the predetermined value acts. The auxiliary bearing is responsible for the difference between the maximum load acting during the emergency operation and the fatigue load having a value smaller than the maximum load, and the shaft portion during the normal operation. Supporting alone The rolling bearing is characterized in that it is physique determined by the fatigue loading.

According to the wind power generator of the first aspect as described above, the auxiliary bearing takes charge of the difference between the maximum load during emergency operation and the fatigue load, thereby determining the size of the rolling bearing used independently during normal operation from the maximum load. A small fatigue load can be applied. The rolling bearing in this case is not particularly limited, such as a rolling bearing or a sliding bearing, but a double row tapered roller bearing is most preferable.
Note that the maximum load during emergency operation described above is extremely low as the frequency of occurrence during the wind turbine lifetime, and is mainly intended for loads with a short duration of action.

In the wind turbine generator according to the first aspect, a gap is formed between the bearing surface of the auxiliary bearing and the outer peripheral surface of the shaft portion while maintaining a predetermined inter-surface distance during the normal operation. Is preferred. Thereby, it is possible to suppress a resistance force such as a frictional force that is generated during normal operation and acts on the shaft portion.

In the wind power generator according to the first aspect, the bearing surface of the auxiliary bearing may be provided over the entire circumference in the circumferential direction, or may be provided in a discontinuous state in which the circumferential direction is divided into a plurality.
In the wind power generator according to the first aspect, it is desirable to employ a sliding bearing as the auxiliary bearing. That is, as an auxiliary bearing that is not used except during an emergency operation, a sliding bearing that does not require maintenance such as prevention of poor lubrication is suitable.

A wind turbine generator according to a second aspect of the present invention includes a plurality of rolling wheels provided with a plurality of wind turbine rotor blades, and the shaft portion of a rotor head that rotates about a horizontal axis is arranged at predetermined intervals in the axial direction. A wind turbine generator having a bearing support structure that is rotatably supported by a bearing, wherein the rolling bearing bears a radial load or an axial load during normal operation, and the radial during the normal operation. When the load increases more than the axial load , in addition to the rolling bearing, the radial load or the axial load is borne, and the radial acting on the rolling bearing under an equivalent load condition and a maximum load condition and it is characterized in that it comprises an auxiliary bearing to reduce the load or the axial load.

According to the wind power generator of such a 2nd aspect, the enlargement of the bearing body by the load burden reduction of a rolling bearing can be suppressed.

In the wind turbine generator according to the reference example of the second aspect, the auxiliary bearing includes a rotation-side magnetic body installed on the outer peripheral surface of the shaft portion and a fixed-side magnetic body fixedly installed on the outer peripheral member of the shaft portion. It is composed of a magnetic bearing divided body divided into a plurality of circumferential directions, and a gap distance between the rotating side magnetic body and the fixed side magnetic body is detected by a gap sensor, and the detected value of the gap sensor Accordingly, the magnetic bearing is preferably configured to change the magnetic force and the load direction of the magnetic force for each of the magnetic divided bodies.

According to such a wind turbine generator , the magnetic bearing installed on the front end side as a plurality of rolling bearings as an auxiliary bearing repels the shaft portion in the lower region of the bearing and attracts the shaft portion in the upper region of the bearing. As a result, the radial load borne by the sliding bearing on the tip side where the hub exists can be reduced with respect to the downward load acting on the hub center.

In the wind turbine generator according to the reference example of the second aspect, the auxiliary bearing is not in contact with the outer peripheral surface of the shaft portion in a state where the shaft portion receives a load load during normal operation, and the shaft portion is abnormal. It is preferable that the bearing is a sliding bearing in which a distance between the shaft portion outer peripheral surface and the shaft portion outer peripheral surface is set so as to be in contact with the shaft portion outer peripheral surface in a state of receiving a load.

According to such a wind turbine generator , the sliding bearing of the auxiliary bearing comes into contact with the outer peripheral surface of the shaft portion when the radial load increases from the load load during normal operation and approaches an abnormal load load. Radial load can be reduced.

In the wind turbine generator according to the reference example of the second aspect, the auxiliary bearing protrudes from the outer peripheral surface of the shaft portion and rotates integrally, and has a magnetic body surface orthogonal to the axis on both surfaces in the axial direction. The rotary side magnetic body and the fixed side magnetic body are fixedly installed on the outer peripheral member of the shaft portion and have a pair of fixed side magnetic bodies having opposite magnetic surfaces on both sides in the axial direction of the rotary side magnetic body. It is preferable that the magnetic bearing be configured to detect the inter-surface distance generated between the magnetic sensor and the gap sensor with a gap sensor and to change the magnetic force and the load direction of the magnetic force according to the detection value of the gap sensor.

According to such a wind turbine generator , the magnetic bearing of the auxiliary bearing attracts the axial front (backward from the front end side in the axial direction) to the axial front and receives the axial load from the wind turbine rotor blade at the hub center. By repelling on the side, the radial load imposed on the rolling bearing can be reduced.

In the wind turbine generator according to the reference example of the second aspect, the auxiliary bearing protrudes from the outer peripheral surface of the shaft portion to form a circumferential stopper surface orthogonal to the axis and rotates integrally with the shaft portion. The flange portion is non-contacted with the stopper surface in a state of receiving a load load during normal operation so that the flange portion is fixedly installed on the outer peripheral side member of the shaft portion to form an opposing surface of the stopper surface. And it is a slide bearing installed in the axial direction position which contacts the said stopper surface in the state which received the abnormal load load to the said axial part.

According to such a wind turbine generator , the auxiliary bearing slide bearing comes into contact with the stopper surface when the axial load increases from the load load during normal operation and approaches an abnormal load load. Can be reduced.

In the wind turbine generator according to the second aspect, the auxiliary bearing is disposed so as to surround the outer peripheral surface of the shaft portion, and a sliding bearing divided body having a plurality of circumferential directions divided therein, and a radius of the sliding bearing divided body A drive mechanism that moves in a direction, and in a state in which the shaft portion receives a load during normal operation, the sliding bearing divided body and the outer peripheral surface of the shaft portion are not in contact with each other, and the shaft portion in the state that received an abnormal load load, the drive mechanism Ru configured auxiliary support mechanism der into contact with the slide bearing the divided body is moved in the axial center direction the shaft portion outer circumferential surface.

According to such a wind turbine generator , the auxiliary support mechanism of the auxiliary bearing is not in contact with the outer peripheral surface of the shaft portion in a state of receiving a load load during normal operation, and is in a state of receiving an abnormal load load or a load load. When approaching the abnormal load load, the drive mechanism operates to move the sliding bearing divided body in the axial center direction so as to come into contact with the outer peripheral surface of the shaft portion, so that the load imposed on the rolling bearing can be reduced. It should be noted that the load borne by the rolling bearing can be limited so as not to exceed the load load during normal operation, depending on the setting for operating the drive mechanism.

  A wind turbine generator according to the present invention includes a main shaft bearing that supports rotation of a rotor head that includes a plurality of wind turbine rotor blades, a pitch bearing that variably supports a pitch angle of the wind turbine rotor blades, and a yaw angle of a nacelle. At least one of the variably supported yaw bearings is the bearing support structure described above.

According to such a wind turbine generator of the present invention, the main shaft bearing that supports the rotation of the rotor head including a plurality of wind turbine rotor blades, the pitch bearing that variably supports the pitch angle of the wind turbine rotor blades, and the nacelle Since the above bearing support structure is adopted for at least one of the yaw bearings that variably support the yaw angle, the maximum load and the fatigue load during emergency operation in the bearing support structure for the main shaft, pitch bearing, and / or yaw bearing If the auxiliary bearing takes charge of the difference, it becomes possible to apply a fatigue load smaller than the maximum load to determine the size of the rolling bearing used independently during normal operation, and it becomes possible to reduce the size and weight of the bearing and the wind turbine generator. .
In addition to the rolling bearing, if the bearing support structure is equipped with an auxiliary bearing that reduces the radial load or the axial load under the equivalent load condition, the increase in the size of the bearing due to the reduced load bearing of the rolling bearing is suppressed. Can do.
A wind turbine generator according to a third aspect of the present invention includes a plurality of rolling elements provided with a plurality of wind turbine rotor blades, and a shaft portion of a rotor head that rotates about a horizontal axis is arranged at predetermined intervals in the axial direction. A wind turbine generator having a bearing support structure rotatably supported by a bearing, wherein the bearing support structure reduces a radial load or an axial load under an equivalent load condition and a maximum load condition in addition to the rolling bearing. The auxiliary bearing is disposed so as to surround the outer peripheral surface of the shaft portion of the shaft portion, and is divided into a plurality of sliding bearing divisions in the circumferential direction, and the sliding bearing division body in the radial direction. A sliding drive mechanism, and in a state in which the shaft portion receives a load during normal operation, the sliding bearing divided body and the outer peripheral surface of the shaft portion are not in contact with each other, and an abnormal load is applied to the shaft portion. Under load The state is characterized in that said drive mechanism is configured auxiliary support mechanism into contact with the shaft portion outer circumferential surface by moving the sliding bearing split body in the axial center direction.

According to the present invention described above, a fatigue load having a value smaller than the maximum load can be adopted for determining the size of the main bearing that is supported independently during normal operation, and the main bearing and the auxiliary bearing cooperate in the event of the maximum load. Therefore, the weight of the bearing support structure can be reduced by reducing the size of the main bearing while ensuring the support strength, durability, reliability and the like for the maximum load.
In addition, the wind turbine generator employing the bearing support structure of the present invention for the main shaft bearing, pitch bearing and / or yaw bearing can be reduced in size and reduced in unit weight while ensuring the support strength and reliability of the bearing support structure. As a result, the entire apparatus can be reduced in size and cost.

It is a figure which shows one Embodiment (1st aspect) which concerns on the bearing support structure of this invention, and is a side view of the structural example applied to the main shaft bearing of a wind power generator. It is sectional drawing of the auxiliary bearing shown in FIG. It is sectional drawing which shows the modification of the auxiliary bearing shown in FIG. About the bearing support structure shown in FIG. 1, a state during normal operation (left side of the paper) supported by the main bearing alone and a state during emergency operation (right side of the paper) supported by the main bearing and the auxiliary bearing in cooperation are shown. It is explanatory drawing shown. It is explanatory drawing which made the bearing support structure shown in FIG. 1 the simple support model, and the state at the time of normal operation (left side of a paper surface) which a main bearing supports independently, and the emergency which a main bearing and an auxiliary bearing support in cooperation The state during operation (right side of the drawing) is shown. FIG. 5 is a diagram showing the load distribution (compression) corresponding to the explanatory diagram of FIG. 4 with the rotation direction angle when the main bearing is viewed from the axial direction as the horizontal axis, and the state during normal operation that the main bearing alone supports ( The left side of the drawing) and the state during emergency operation (right side of the drawing) supported by the main bearing and the auxiliary bearing in cooperation are shown. It is explanatory drawing which shows the relationship between the allowable external force (horizontal axis) regarding a main bearing and an auxiliary bearing, and load capability (vertical axis) about the bearing support structure (1st aspect) of this embodiment. It is principal part sectional drawing which shows the schematic structural example which applied the bearing support structure (1st aspect) of this embodiment to the pitch bearing of a wind power generator. It is principal part sectional drawing which shows the schematic structural example which applied the bearing support structure (1st aspect) of this embodiment to the yaw bearing of a wind power generator. FIG. 10 is a cross-sectional view of a main part illustrating a schematic configuration example when a sliding bearing is employed in the yaw bearing of FIG. 9. It is a side view which shows the outline | summary of a wind power generator. The figure which shows one Embodiment (2nd aspect) which concerns on the bearing support structure of this invention, and is a side view of the structural example which used the magnetic bearing for the auxiliary bearing (corresponding to radial load) applied to the main shaft bearing of a wind power generator. It is. FIG. 13 is an operation explanatory diagram of the bearing support structure shown in FIG. 12 as an auxiliary bearing (corresponding to a radial load) with respect to a load load and an abnormal load load during normal operation. It is a side view which shows the 1st reference example using a sliding bearing (corresponding to a radial load) about the bearing support structure of the 2nd aspect shown in FIG. FIG. 13 is a side view showing a second reference example using a magnetic bearing as an auxiliary bearing (corresponding to an axial load) in the bearing support structure of the second mode shown in FIG. 12. FIG. 16 is an operation explanatory diagram of the bearing support structure shown in FIG. 15 as an auxiliary bearing (corresponding to an axial load) with respect to a load load and an abnormal load load during normal operation. FIG. 13 is a side view showing a third reference example using a sliding bearing as an auxiliary bearing (corresponding to an axial load) in the bearing support structure of the second mode shown in FIG. 12. The bearing support structure of the second embodiment shown in FIG. 12 is a side view showing an embodiment using the auxiliary support mechanism having a sliding bearing as an auxiliary bearing. It is operation | movement explanatory drawing of the auxiliary | assistant support mechanism shown in FIG. 18, and is a longitudinal cross-sectional view which shows the state from which the positional relationship of a rolling bearing and a shaft part changed at the time of the maximum load of the lower stage from the normal operation of the upper stage. It is operation | movement explanatory drawing of the auxiliary | assistant support mechanism shown in FIG. 18, and is a longitudinal cross-sectional view which shows the state in which the auxiliary | assistant support mechanism changed at the time of the maximum load of the lower stage from the normal operation of the upper stage. It is a partial cross section side view which shows the bearing part for main shafts of a wind power generator as a prior art example of a bearing support structure. It is a schematic block diagram which shows the main bearing structure of the wind power generator which supports a main axis | shaft with a pair of rolling bearing arrange | positioned to an axial direction as a prior art example of a bearing support structure. It is principal part sectional drawing of the main bearing structure shown in FIG. It is an image figure of a load size (vertical axis) and a time scale (horizontal axis), and shows an image of load change according to wind conditions during normal power generation (operation) or abnormal conditions such as storms.

Hereinafter, as an embodiment of a bearing support structure according to the present invention, an application example to a wind turbine generator will be described with reference to the drawings.
A wind turbine generator 1 shown in FIG. 11 rotates around a substantially horizontal rotation axis, a column (also referred to as “tower”) 2 standing on the foundation B, a nacelle 3 installed at the upper end of the column 2. And a rotor head (hub) 4 that is supported on the nacelle 3 and is supported. In addition, when the wind power generator 1 is an offshore windmill, either a floating body type or a method of providing a foundation B on the seabed may be used.

  A plurality of (for example, three) wind turbine rotor blades 5 are attached to the rotor head 4 in a radial pattern around the rotation axis. As a result, the force of wind striking the wind turbine rotor blade 5 from the direction of the rotation axis of the rotor head 4 is converted into power for rotating the rotor head 4 around the rotation axis.

<First embodiment (first aspect)>
In the wind power generator 1 described above, as shown in FIG. 1, for example, a rotor is used as a bearing support structure that cantilever-supports a shaft portion of a rotating body that rotates about an axis (rotation axis Rs in FIG. 1). A spindle bearing BU for rotatably supporting the head 4 and the spindle 7 connected to the rear end portion of the rotor head 4 is provided. The windmill rotor blade 5 described above is attached to the rotor head 4 and protrudes radially through the cover of the rotor head 4.
In the illustrated configuration example, the rear end side of the main shaft 7 is connected to the speed increaser 8 to drive the generator (not shown) by increasing the rotation of the rotor head 4. The method is not limited.

The main shaft bearing BU includes a double-row tapered roller bearing 10 which is a main bearing capable of supporting the tip end side of the shaft portion of the rotor head 4, which is a rotating body, in a cantilevered manner, and a shaft portion of the double-row tapered roller bearing 10. And an auxiliary bearing slide bearing 20 that supports the rear end side (speed increaser 8 side).
The double-row tapered roller bearing 10 serving as a main bearing is fixedly supported by the nacelle 3 having a spring constant k1, and has a spring constant k2 connected to the rear end of the rotor head 4 during normal operation in which a load of a predetermined value or less acts. The main shaft front end portion 7a of the set main shaft 7 is supported alone. The spring constant k1 of the nacelle 3 and the spring constant k2 of the main shaft 7 are set so that the spring constant k1 of the nacelle 3 becomes an overwhelmingly large value (k1 >> k2).

The double row tapered roller bearing 10 has a configuration in which a large number of rollers 13 arranged at equal pitches in the circumferential direction are arranged in two rows in the axial direction between the inner ring 11 and the outer ring 12. In this case, the columnar rollers 13 arranged in two rows are inclined substantially 45 degrees with respect to the center line C1 so that the end on the center line C1 side orthogonal to the rotation axis Rs is on the inner ring 11 side. Has been placed.
As a result, the single double-row tapered roller bearing 10 receives the load of the rotating body and rotatably supports the main shaft 7, and two rows of rollers 13 that are inclined with respect to the center line C 1 act on the main shaft 7. It is also possible to respond to moments.

  The auxiliary bearing slide bearing 20 supports the main shaft 7 in cooperation with the double-row tapered roller bearing 10 only during an emergency operation in which a large load exceeding a predetermined value is applied. The sliding bearing 20 includes a bearing surface 21 having a circular cross section formed using a material such as polyether ether ketone (PEEK) resin. For example, as shown in FIG. 2, the bearing surface 21 has a positional relationship that is substantially concentric with the main shaft 7 during normal operation with a smaller load than during emergency operation.

Further, in a state during normal operation, a gap 22 is formed between the outer peripheral surface of the main shaft 7 and the inner peripheral surface of the slide bearing 20 while maintaining a predetermined inter-surface distance S1 (preferably about 0.5 mm). The main shaft 7 is not in contact with the slide bearing 20.
As a result, during normal operation, resistance force such as friction force is not generated in the non-contact sliding bearing 20, so that resistance force such as friction force acting on the entire main shaft 7 can be suppressed.

The sliding bearing 20 described above is fixedly supported by a stay 24 with respect to a high-rigidity base plate 3a constituting the nacelle 3, and is particularly supported to have high rigidity with respect to an input in a vertical direction. . The stiffness of the stay 24 with respect to bending, that is, the spring constant k3 which means the stiffness in the vertical direction is the largest value compared to the spring constant k1 of the nacelle 3 supporting the double row tapered roller bearing 10 and the spring constant k2 of the main shaft 7 ( k3> k1 >> k2). This is because if the rigidity of the stay 24 is insufficient, it will be deformed and moved together with the double-row tapered roller bearing 10 under the load during emergency operation, and the purpose of installing the sliding bearing 20 cannot be achieved.
Such a sliding bearing 20 is suitable as an auxiliary bearing that is not used except during emergency operation because maintenance such as prevention of poor lubrication is unnecessary.

By the way, although the sliding bearing 20 mentioned above has provided the bearing surface 21 over the perimeter of the circumferential direction, as shown in FIG. 3, for example, you may provide the bearing surface 21A of the discontinuous state which divided the circumferential direction into four. . In this discontinuous state, the bearing surface 21A and the gaps 23 without the bearing surface 21A are alternately arranged in the circumferential direction, and the number of divisions of the bearing surface 21A is not particularly limited.
Further, instead of the discontinuous bearing surface 21A, for example, a plurality of rolling elements such as rollers may be arranged at equal pitches in the circumferential direction, and the main shaft 7 may be supported in contact during emergency operation.

Hereinafter, the operation of the main shaft bearing BU will be described with reference to FIGS.
As shown in FIG. 4, the main bearing BU described above has a distance from the center of gravity of the rotating body such as the rotor head 4 to the center line C1 of the double row tapered roller bearing 10 as L1, and from the center line C1 of the double row tapered roller bearing 10. If the distance to the center line C2 of the plain bearing 20 is L2, the distance L1 is set to be larger than the distance L2 (L1> L2). If the diameter of the double row tapered roller bearing 10 is D1 and the diameter of the sliding bearing 20 is D2, the diameter D1 is set to be larger than the diameter D2 (D1> D2). The sliding bearing 20 has an axial width L3.

FIG. 5 is an explanatory diagram in which the above-described bearing support structure is a simple support model of material mechanics.
During normal operation on the left side of the sheet, the length L1 is a cantilever beam B1 on which the external force F1 acts, and a moment M acts on the base portion that supports the cantilever beam B1. In this case, the external force F1 is equal to or less than the moment M (0 ≦ F1 ≦ M). In this state, in the normal operation of FIG. 4, a gap 22 having a surface distance S1 is formed between the bearing surface 21 of the sliding bearing 20 and the main shaft 7, and the main shaft 7 is supported by the double row tapered roller bearing 10. Is.

During such normal operation, the load distribution of the compressive load acting on the main shaft bearing BU is 180 degrees in the rotation direction angle between the hub side roller train and the speed increasing device side roller train, as shown on the left side of FIG. Degrees are off. Further, since there is no assist support by the sliding bearing 20, the load distribution of the sliding bearing 20 is always 0 as shown by the dotted line in the figure.
That is, the load distribution of the hub side roller row indicated by the solid line decreases from the maximum 0 degree to 90 degrees, and after the state of the load 0 continues from 90 degrees to 270 degrees, it increases from 270 degrees to the maximum 360 degrees. To rise. Further, the load distribution of the speed increaser side roller train indicated by a broken line gradually increases from 90 degrees and reaches a maximum at 180 degrees after the state of zero load continues from 0 degrees to 90 degrees. Thereafter, the load decreases from 180 degrees to 270 degrees with a load of 0, and the state of the load of 0 continues from 270 degrees to 360 degrees.

On the other hand, during an emergency operation on the right side of the page, the cantilever B2 has a length L1 + L2 in which an external force F2 (M ≦ F2 ≦ M ′) greater than the external force F1 acts on the tip, and is an elastic cantilever support and a two-point simple support It has a function. In this case, when the cantilever B2 receives a load (external force F2) of a predetermined value or more, the cantilever B2 is simply supported at two points P1 and P2 from the one point support at P1 by elastic deformation. Become.
In this state, as in the emergency operation shown in FIG. 4, the main shaft 7 having the lowest rigidity (elastic coefficient k2) is elastically deformed by receiving an excessive external force F2.

  As a result, the gap 22 of the inter-surface distance S1 maintained between the bearing surface 21 of the sliding bearing 20 and the main shaft 7 becomes zero when the main shaft 7 comes into contact with one (for example, the lower surface side) bearing surface 21, At the same time, the other (for example, the upper surface side) is almost doubled (S2≈S1 × 2) to the inter-surface distance S2. That is, the main shaft 7 is supported not only by the double row tapered roller bearing 10 but also by the sliding bearing 20.

During such an emergency operation, the load distribution of the compressive load acting on the main shaft bearing BU is as shown on the right side of FIG.
That is, the load distribution on the hub side (rotor head side) roller row indicated by the solid line decreases from the maximum 0 degree to 0 degree 90 degrees, and the load 0 from 90 degrees to 270 degrees, as in the normal operation described above. After the condition continues, it rises from 270 degrees to a maximum of 360 degrees.

  However, although the load distribution of the speed increasing machine side roller train indicated by the broken line slightly decreases in the range of 90 to 270 degrees, it significantly increases in the range of 0 to 90 degrees and 270 to 360 degrees. Then, in the range from 90 degrees to 270 degrees where the load distribution of the speed increaser side roller train decreases, the assist support by the slide bearing 20 increases to an allowable value as indicated by the dotted line in the figure.

Therefore, in the main shaft bearing BU having the above-described bearing support structure, the relationship between the allowable external force (horizontal axis) and the load capacity (vertical axis) regarding the double-row tapered roller bearing 10 of the main bearing and the sliding bearing 20 of the auxiliary bearing is, for example, The explanatory diagram shown in FIG.
That is, in the region where the allowable external force is 0 to M, the double row tapered roller bearing 10 alone bears the range of the load capability from 0 to a, and in the region where the allowable external force exceeds M, the load capability is a to The range up to c is borne by the double row tapered roller bearing 10 and the sliding bearing 20.

In other words, in the region where the allowable external force is M to M ′, the allowable value is exceeded by adding the sliding bearing 20 that can bear the load capacity up to ef (translating upward and connecting to a). As for the load capacity of the double row tapered roller bearing 10, the load capacity of the main shaft bearing BU as a whole can be secured from 0 to c without increasing the load capacity as in a to b.
The double-row tapered roller bearing 10 and the sliding bearing 20 shown in the figure have been described as linearly increasing the load capacity linearly, but for example, non-linearly increasing the load capacity such as g to f and 0 to h shown in FIG. However, there is no particular limitation as long as it can support the double row tapered roller bearing 10 with an allowable value or more.

As described above, the main shaft bearing BU of the present embodiment is configured to receive the assist support by the sliding bearing 20 of the auxiliary bearing with respect to the maximum load acting at the time of emergency operation. For the double-row tapered roller bearing 10 as the main bearing, a fatigue load having a value smaller than the maximum load can be adopted for determining the physique. Accordingly, the double row tapered roller bearing 10 can be downsized, and even if the wind power generator 1 is enlarged, the double row tapered roller bearing 10 that can be relatively downsized can be used as a general-purpose product. Becomes easier.
That is, in the unlikely event that a storm or the like that occurs once every 50 years is assumed, the double-row tapered roller bearing 10 and the sliding bearing 20 are configured to support each other in a cooperative manner. As the support strength, durability, reliability, and the like are ensured, and the size of the double-row tapered roller bearing 10 is reduced in size, the main shaft bearing BU can reduce the weight of the entire bearing support structure.

Next, an embodiment in which the bearing support structure of the present invention is applied to a pitch bearing will be described with reference to FIG.
The pitch bearing 40 shown in FIG. 8 is a bearing support structure that variably supports the pitch angle of the wind turbine rotor 5, and includes a rolling bearing 41 as a main bearing and an assist support support portion 42 as an auxiliary bearing. .

The rolling bearing 41 is fixedly supported by the rotor head 4, and a spherical bearing 41c is sandwiched between the inner ring 41a and the outer ring 41b.
A pair of assist support support portions 42 are provided on both sides in a direction (vertical direction on the paper surface) orthogonal to the rotational direction (left and right direction on the paper surface) of the wind turbine rotor 5. Specifically, the pair of assist support support portions 42 are provided between the upper end surface of the outer ring 41 b, the lower end surface of the outer ring 41 b, and the rotor head 4. A sliding member 42a such as a PEEK material is attached to the opposing surfaces of the pair of assist support support portions 42 so as to form a predetermined gap between the upper and lower end surfaces of the inner ring 41a. For this reason, the assist support support part 42 described above functions as a non-contact sliding bearing during normal operation.

The pitch bearing 40 configured in this manner functions as a sliding bearing when the rolling bearing 41 supports the rotation of the wind turbine rotor blade 5 associated with pitch angle control during normal operation and the maximum load is applied during emergency operation. The assist support support portion 42 having the function is supported in cooperation with the rolling bearing 41.
Therefore, the rolling bearing 41 of the main bearing can employ a fatigue load having a value smaller than the maximum load for determining the physique, and thus can be reduced in size.

Next, an embodiment in which the bearing support structure of the present invention is applied to a yaw bearing will be described with reference to FIGS.
The yaw bearing 50 shown in FIG. 9 has a bearing support structure that variably supports the yaw angle of the nacelle 3, and includes a rolling bearing 51 serving as a main bearing and an assist support support 52 serving as an auxiliary bearing.

In this case, the brake disc 61 of the yaw brake device 60 is used for the assist support support portion 52 and the like.
The rolling bearing 51 is fixedly supported by a brake disc 61 fixedly installed at the upper end portion of the support column 2, and a spherical bearing 51c is sandwiched between an inner ring 51a and an outer ring 51b.

A pair of assist support support portions 52 are provided on both sides in a direction (vertical direction of the paper surface) orthogonal to the rotation direction of the nacelle 3 (horizontal direction of the paper surface). Specifically, the pair of assist support support portions 52 includes an upper end surface of the outer ring 51 b and a brake disc 61 provided between the lower end surface of the outer ring 51 b and the upper end surface of the column 2.
Further, an auxiliary member 53 is provided between the inner ring 51a and the base plate 3a of the nacelle 3 so as to protrude like a bowl up to the upper end surface of the outer ring 51a.

Further, a predetermined gap is formed between the upper surface of the auxiliary member 53 and the lower surface of the inner ring 51a on the opposing surfaces of the pair of assist support support portions 52, such as a PEEK material. A sliding member 52a is attached. For this reason, the above-described assist support support portion 52 functions as a non-contact sliding bearing during normal operation.
Therefore, when the maximum load is applied during emergency operation, the assist support support portion 52 having the function of a sliding bearing can be supported in cooperation with the rolling bearing 51. For this reason, since the rolling bearing 51 of the main bearing can employ a fatigue load having a value smaller than the maximum load for determining the physique, the size can be reduced.

  Moreover, the yaw bearing 70 shown in FIG. 10 has shown the case where the sliding bearing 71 is employ | adopted as the main bearing. The yaw bearing 70 is disposed on the upper and lower sides of the fixed side collar 71a and rotatably supports the nacelle 3. The yaw bearing 70 is disposed on the inner peripheral surface of the rotation side collar 71a and is horizontally disposed on the nacelle 3. And a sliding member 72b for restricting the direction movement.

In this case, the assist support is performed by a pair of upper and lower sliding members 74 installed in the vicinity of the sliding member 72a. The sliding member 74 is installed on the rotating nacelle 3 side, and forms a predetermined gap with the fixed side flange 71a.
Even in such a yaw bearing 70, when the maximum load is applied during an emergency operation, the assist support support portion 74 of the auxiliary bearing having the function of a sliding bearing can be supported in cooperation with the sliding bearing 71 of the main bearing. . For this reason, the sliding bearing 70 of the main bearing can employ a fatigue load having a value smaller than the maximum load for determining its physique, and thus can be reduced in size.

  The wind turbine generator 1 of the present embodiment, as its bearing support structure, variably supports the main shaft bearing BU for supporting the rotation of the rotor head 4 including a plurality of wind turbine rotor blades 5 and the pitch angle of the wind turbine rotor blades 5. If at least one of the pitch bearing 40 and the yaw bearings 50 and 70 that variably support the yaw angle of the nacelle 3 is employed, the auxiliary bearing will be responsible for the difference between the maximum load and the fatigue load during emergency operation. Will be able to. As a result, a fatigue load smaller than the maximum load can be applied to determine the size of the main bearing that is used alone during normal operation, and the bearing and the wind power generator 1 that are the main bearing can be reduced in size and weight.

  When the wind power generator 1 is increased in size, the above-described bearing support structure according to the present embodiment is effective for reducing the weight and reducing the length of the nacelle 3 from the two-bearing structure as a bearing for supporting the main shaft 7. By adopting the row taper roller bearing 10 and taking advantage of its merit, it is possible to reduce the restriction due to the limit of the bearing manufacturing capability of the bearing supplier by downsizing the main bearing. Therefore, it is possible to release the restrictions associated with the increase in the size of the bearing support structure and to increase the size of the wind power generator 1 by scaling up.

<Second Embodiment (Second Aspect)>
Next, a second embodiment of the bearing support structure according to the present invention will be described with reference to the drawings.
The embodiment described below is applied to a bearing support structure in which a main shaft 7 is supported by a pair of front and rear rolling bearings Bf and Br arranged at predetermined intervals in the axial direction. In addition to the rolling bearings Bf and Br, In addition, an auxiliary bearing for reducing radial load or axial load under the equivalent load condition and the maximum load condition is provided. The rolling bearing that supports the main shaft 7 is normally supported by a pair of front and rear rolling bearings Bf and Br, but is not particularly limited, and may be two or more.

The bearing support structure of the second aspect shown in FIG. 12 is a pair of front and rear rolling bearings Bf in which main shafts (shaft portions) 7 of a rotating body that rotates about a rotation axis Rs are arranged at predetermined intervals in the axial direction. The magnetic bearing MB is provided so as to be rotatable by Br and provided at a position closer to the shaft tip side than the rolling bearing Bf on the front side. This magnetic bearing MB is an auxiliary bearing installed for the purpose of reducing the radial load in order to suppress an increase in the size of the bearing body. The shaft tip side in this case is the direction in which the wind turbine rotor 5 and the rotor head (hub) 4 are attached to the main shaft 7.
In addition, the code | symbol 3a in a figure is a base plate of the nacelle 3, and Rm is a reinforcement member.

  The magnetic bearing MB is composed of a rotation-side magnetic body Mr installed on the outer peripheral surface of the main shaft 7 and a fixed-side magnetic body Mf fixedly installed on the outer peripheral member of the main shaft 7, and the magnetic bearing divided into a plurality of circumferential directions. It is an aggregate of divided bodies Mp. That is, the magnetic bearing MB has a configuration in which a plurality of magnetic bearing divided bodies Mp are arranged substantially equally in the circumferential direction so as to surround the outer periphery of the main shaft 7.

  Incidentally, in the illustrated magnetic bearing MB, one of the rotation-side magnetic body Mr and the fixed-side magnetic body Mf, preferably the fixed-side magnetic body Mf, is an electromagnet. Direction) can be controlled. The rotation-side magnetic body Mr is a magnet embedded in the outer surface of the main shaft 7.

  A gap sensor GS for detecting a radial inter-surface distance (gap G shown in FIG. 13) generated between the rotation-side magnetic body Mr and the fixed-side magnetic body Mf is installed in the vicinity of the magnetic bearing MB described above. Yes. The gap sensor GS is used to control the magnetic force and polarity of the fixed-side magnetic body Mf, which is an electromagnet, for example, by inputting the detected gap G to a control unit (not shown). That is, the magnetic bearing MB is configured to change the magnetic force and the load direction of the magnetic force for each magnetic divided body Mp according to the detection value of the gap sensor GS.

  In addition to the rolling bearings Bf and Br, the bearing support structure including the magnetic bearing MB of the second aspect includes an auxiliary bearing that reduces a radial load under an equivalent load condition used for life evaluation. Therefore, by reducing the load load of the rolling bearings Bf and Br, particularly in the rolling bearing Bf on the front side close to the load loading position Hc at the center of the hub (center of the rotor head), it repels the main shaft 7 in the region below the bearing, and By pulling the main shaft 7 in the region on the upper side of the bearing, it is possible to reduce the radial load acting downward and suppress the increase in size of the bearing body.

Below, the operation | movement as an auxiliary bearing is demonstrated concretely based on FIG. 13 about magnetic bearing MB mentioned above.
In the main shaft 7, the equivalent load (radial load) for life evaluation is downward due to the downward load acting on the load load position Hc at the center of the hub. Therefore, the load relationship during normal operation varies in the positional relationship between the main shaft 7 and the fixed-side magnetic body Mf of the magnetic bearing MB that are substantially concentric at the neutral position. That is, the main shaft 7 receives a radial load and moves downward, and the gap G expands in the upper region of the main shaft 7 in comparison with the neutral position.

Such a change in the gap G can be recognized from the detection value of the gap sensor GS, and at the same time, the load load direction can be grasped.
Therefore, the electromagnet of the magnetic bearing MB is controlled so that the attractive force is generated in the direction opposite to the load direction. That is, in the illustrated configuration example, if the electromagnet of the fixed-side magnetic body Mf is controlled so that an attractive force is generated in the direction of the white arrow, the main shaft 7 approaches the original rotation axis Rs and the gap G is reduced. Therefore, the bearing load acting on the rolling bearing Bf can be reduced. The electromagnet of the fixed-side magnetic body Mf may adjust the magnetic force as appropriate according to the gap G in order to bring the main shaft 7 as close as possible to the direction of the rotation axis Rs.

  On the other hand, when an abnormal load such as an emergency is applied and a gap G larger than that at the neutral time is generated in another region (lower region in the illustrated example), the gap G is detected by the gap sensor GS. The electromagnet of the magnetic bearing MB is controlled so that the attractive force (see the white arrow) is generated in the direction of reducing. As a result, the main shaft 7 approaches the direction of the original rotation axis Rs, so that the gap G is reduced and the bearing load acting on the rolling bearing Bf is also reduced.

As described above, the bearing support structure in which the magnetic bearing MB is provided as the auxiliary bearing on the tip side from the rolling bearing Bf is controlled so that the magnetic force of the magnetic bearing MB and the load direction of the magnetic force are as close as possible to the detection value of the gap G. By doing so, the radial load borne by the sliding bearing Bf on the tip side where the rotor head 4 exists can be reduced.
Note that the electromagnet of the magnetic bearing MB may simultaneously apply the attractive force and the repulsive force. In such a case, the reverse direction of 180 degrees from the direction of the attractive side is the direction of the repulsive force. .

Next, a first reference example will be described based on FIG. 14 with respect to the bearing support structure of the second aspect described above.
The auxiliary bearing employed in this reference example reduces the radial load under equivalent load conditions and maximum load conditions. The auxiliary bearing is not in contact with the outer peripheral surface of the shaft portion when the main shaft 7 receives a load load during normal operation, and is in contact with the outer peripheral surface of the shaft portion when the main shaft 7 receives an abnormal load load. Further, the sliding bearing SB is set with a distance between the outer peripheral surface of the shaft portion. In this case, the oil used for the sliding bearing SB can also be used in combination with equipment installed in the vicinity, such as a main bearing.
Note that the position of the sliding bearing SB is arranged between the rolling bearings Bf and Br, but is not particularly limited, such as being arranged on the tip side of the rolling bearing Bf.

  According to such a bearing support structure, the sliding bearing SB of the auxiliary bearing reduces the inter-surface distance in any of the circumferential directions when the radial load increases from the load load during normal operation and approaches an abnormal load load. In contact with the outer peripheral surface of the shaft. For this reason, since the sliding bearing SB functions as a bearing and bears a part of the radial load, the radial load burdened on the rolling bearing Bf can be reduced.

Next, a second reference example will be described based on FIGS. 15 and 16 for the above-described bearing support structure of the second aspect.
The auxiliary bearing used in this reference example reduces the axial load under the equivalent load condition and the maximum load condition.

The magnetic bearing MB of the auxiliary bearing adopted here protrudes from the outer peripheral surface of the main shaft 7 and rotates integrally therewith, and also has a rotation-side magnetic body Mr having magnetic surfaces orthogonal to the axis Rs on both axial sides, and the outer periphery of the main shaft 7. It is configured by a pair of fixed-side magnetic bodies Mf that are fixedly installed on a member (for example, the base plate 3a) and that have magnetic surfaces facing both sides in the axial direction of the rotation-side magnetic body Mr. In this reference example, the fixed-side magnetic body Mf is an electromagnet, and the polarity, magnetic force, and the like can be appropriately controlled.

In this magnetic bearing MB, the inter-surface distance (gap Gf, Gr shown in FIG. 15) generated between the rotation-side magnetic body Mr and the fixed-side magnetic body Mf is detected by the gap sensor GS, and the magnetic force is determined according to the detected value. And it is comprised so that the load direction of magnetic force may be changed.
Here, the gaps Gf and Gr detected by the gap sensor GS are axial distances that change due to variations in the axial load acting on the main shaft 7.

According to the bearing support structure of the second reference example provided with such a magnetic bearing MB, in addition to the rolling bearings Bf and Br, the axial load under the equivalent load condition can be reduced, and therefore the rolling bearing Bf. , Br can reduce the increase in the size of the bearing body due to the reduced load burden of Br.

  More specifically, when an axial load is applied to the main shaft 7, the gaps Gf and Gr are set to substantially coincide (Gf≈Gr) at the neutral position. However, when a load during normal operation (axial load) is applied, the gap Gf on the shaft front end side increases and the gap Gr on the shaft rear end side decreases. Therefore, the fixed-side magnetic body Mf of the magnetic bearing MB generates a magnetic force in a direction that corrects the unbalance of the gaps Gf and Gr.

  That is, the shaft-side fixed-side magnetic body Mf may attract the rotation-side magnetic body Mr to correct the imbalance between the gaps Gf and Gr, or only the repulsive force by the shaft-side end-side fixed-side magnetic body Mf. Alternatively, the imbalance may be corrected by using both suction force and repulsive force. Such unbalance correction of the gaps Gf and Gr is borne by the rolling bearings Bf and Br against the axial load (the load directed from the front end side in the axial direction to the rear) received from the wind turbine rotor 5 at the center of the hub 6. The radial load can be reduced and the size of the bearing body can be prevented from increasing.

Next, a third reference example will be described based on FIG. 17 with respect to the bearing support structure of the second aspect described above.
The auxiliary bearing employed in this reference example reduces the axial load under the equivalent load condition and the maximum load condition. The auxiliary bearing reduces the axial load by bringing the sliding bearing SB into contact with the stopper surface Sa of the flange portion Sf that rotates integrally with the main shaft 7.

  More specifically, the slide bearing SB projects from the outer peripheral surface of the main shaft 7 to form a circumferential stopper surface Sa perpendicular to the axis Rs, and the flange 7 S rotates integrally with the main shaft 7 so that the main shaft 7 rotates. It is installed so as to be fixed to an outer peripheral side member (for example, the base plate 3a) and to form a facing surface of the stopper surface Sa. The sliding bearing SB is in non-contact with the stopper surface Sa in a state of receiving a load load during normal operation, and is in an axial position in contact with the stopper surface Sa in a state of receiving an abnormal load load on the main shaft 7. Is installed.

According to such a bearing support structure, the sliding bearing SB of the auxiliary bearing functions as a bearing in contact with the stopper surface Sa when the axial load increases from the load load during normal operation and approaches an abnormal load load. The axial load borne by the rolling bearings Bf and Br can be reduced.
In the illustrated configuration example, two sets of front and rear sliding bearings SB and flange portions Sf are provided in the axial direction, but there is no particular limitation, and one set or three or more sets may be used.

Finally, one embodiment of the above-described bearing support structure according to the second aspect will be described with reference to FIGS. 18 to 19B.
The auxiliary bearing employed in this embodiment is an auxiliary support mechanism AS that reduces the load under the maximum load condition. Hereinafter, the auxiliary support mechanism AS will be described in detail.

  The auxiliary support mechanism AS is disposed so as to surround the outer peripheral surface of the main shaft 7 and is divided into a plurality of sliding bearings Sp in the circumferential direction, and a hydraulic cylinder of a drive mechanism that moves the sliding bearing splits Sp in the radial direction. HS. In this case, a dry type that does not require lubricating oil is suitable as the sliding bearing split Sp.

  The auxiliary support mechanism AS is in a state in which the sliding bearing divided body Sp and the outer peripheral surface of the main shaft 7 are not in contact with each other when the main shaft 7 receives a load during normal operation (see the upper part of FIG. 19A). A gap δ1 (see the upper part of FIG. 19A) is formed between the inner ring Ri and the bearing W in the region above the main shaft in the rolling bearing Bf. In this state, in the region below the main shaft in the rolling bearing Bf, the bearing W is in contact with the inner ring Ri and the outer ring Ro, and there is no gap.

Further, in a state where the main shaft 7 is subjected to an abnormal load (see the lower part of FIG. 19B), the hydraulic cylinder HS moves the sliding bearing divided body Sp toward the axial center, and the sliding bearing divided body Sp is moved to the shaft outer peripheral surface. It is comprised so that it may contact.
In the illustrated configuration example, three sets of auxiliary support mechanisms AS are installed at a 120-degree pitch in the circumferential direction, but the present invention is not particularly limited.

According to such a bearing support structure, the auxiliary support mechanism AS of the auxiliary bearing is not in contact with the outer peripheral surface of the shaft portion when the main shaft 7 receives a load load during normal operation, and the sliding bearing split Sp is a sliding bearing. It does not demonstrate its function.
However, when the main shaft 7 is subjected to an abnormal load load, or the load load is close to the abnormal load load, the hydraulic cylinder HS is operated to move the slide bearing divided body Sp toward the center of the shaft, and the slide bearing. The divided body Sp is brought into contact with the outer peripheral surface of the shaft portion and pressed.

As a result, since the bearing split body Sp functions as a sliding bearing that rotatably supports the main shaft 7, it is possible to reduce the radial load and the axial load that are borne by the rolling bearings Bf and Br. As described above, when the bearing divided body Sp functions as a sliding bearing, the clearances δ2 and δ3 are generated between the bearing W and the inner ring Ri in the rolling bearing Bf (see the lower stage in FIG. 19A). Therefore, the load burden is reduced.
The above-described gap δ1 is the sum of the gap δ2 and the gap δ3 (δ1 = δ2 + δ3).

  Further, by setting the conditions for operating the hydraulic cylinder HS described above, the load borne by the rolling bearings Bf and Br can be limited so as not to exceed the load load during normal operation.

As described above, according to the second aspect , the reference example, and the one embodiment described above, in addition to the rolling bearings Bf and Br, the auxiliary load for reducing the radial load or the axial load under the equivalent load condition and the maximum load condition. Since the bearing support structure is provided with a bearing, it is possible to suppress an increase in the size of the bearing body due to the reduced load burden on the rolling bearings Bf and Br.
Note that the present invention is not limited to the above-described embodiment, and the generator drive system is not limited to a speed increasing system provided with a speed increaser, and can be appropriately changed within a range not departing from the gist thereof. .

1 Wind power generator 2 Strut (tower)
3 Nacelle 3a Base plate 4 Rotor head (hub)
5 Wind turbine rotor blade 7 Main shaft 10 Double row tapered roller bearing (main bearing)
20 Sliding bearing (auxiliary bearing)
21, 21A Bearing surface 22 Gap 23 Gap portion 24 Stay 40 Pitch bearing 50, 70 Yaw bearing 60 Yaw brake device Bf, Br Rolling bearing MB Magnetic bearing Mr Rotating side magnetic body Mf Fixed side magnetic body Mp Magnetic bearing divided body GS Gap sensor SB Slide bearing Sf Flange portion Sa Stopper surface AS Auxiliary support mechanism Sp Slide bearing divided body HS Hydraulic cylinder

Claims (6)

A wind turbine generator having a bearing support structure that includes a plurality of wind turbine rotor blades and rotatably supports a shaft portion of a rotor head that rotates about a horizontal axis,
The bearing support structure is
A rolling bearing that can be independently supported in the form of a cantilever in which a moment acts on the front end side of the shaft portion of the rotor head, and an auxiliary bearing that supports the rear end side of the shaft portion of the rolling bearing,
The rolling bearing individually supports the shaft during normal operation when a load of a predetermined value or less acts,
The auxiliary bearing supports the shaft portion in cooperation with the rolling bearing only during an emergency operation in which a large load exceeding the predetermined value acts.
The auxiliary bearing is responsible for the difference between the maximum load acting during the emergency operation and a fatigue load having a value smaller than the maximum load,
The wind turbine generator according to claim 1, wherein the rolling bearing that independently supports the shaft portion during the normal operation is determined by the fatigue load.   The gap portion is formed between the bearing surface of the auxiliary bearing and the outer peripheral surface of the shaft portion while maintaining a predetermined inter-surface distance during the normal operation. Wind power generator.   The wind turbine generator according to claim 2, wherein the bearing surface of the auxiliary bearing is provided in a discontinuous state over the entire circumference in the circumferential direction or divided into a plurality of circumferential directions.   The wind turbine generator according to any one of claims 1 to 3, wherein the auxiliary bearing is a sliding bearing. Wind power having a bearing support structure that includes a plurality of wind turbine rotor blades and rotatably supports a shaft portion of a rotor head that rotates about a horizontal axis by a plurality of rolling bearings arranged at predetermined intervals in the axial direction. A power generator,
The bearing support structure is
The rolling bearing bears a radial load or an axial load during normal operation,
When the load increases more than the radial load or the axial load during the normal operation, in addition to the rolling bearing, the radial load or the axial load is borne, and the equivalent load condition and the maximum load condition are satisfied. An auxiliary bearing for reducing the radial load or the axial load acting on a rolling bearing ;
The auxiliary bearing includes a sliding bearing divided body that is arranged so as to surround the outer peripheral surface of the shaft portion of the shaft portion and is divided into a plurality of circumferential directions, and a drive mechanism that moves the sliding bearing divided body in the radial direction. Prepared,
In a state in which the shaft portion receives a load load during normal operation, the sliding bearing divided body and the shaft portion outer peripheral surface are not in contact with each other, and in a state in which the shaft portion receives an abnormal load load, The wind power generator, wherein the drive mechanism is an auxiliary support mechanism configured to move the sliding bearing divided body in the axial center direction so as to contact the outer peripheral surface of the shaft portion . Wind power having a bearing support structure that includes a plurality of wind turbine rotor blades and rotatably supports a shaft portion of a rotor head that rotates about a horizontal axis by a plurality of rolling bearings arranged at predetermined intervals in the axial direction. A power generator,
The bearing support structure is
In addition to the rolling bearing, an auxiliary bearing that reduces radial load or axial load under equivalent load conditions and maximum load conditions is provided,
The auxiliary bearing includes a sliding bearing divided body that is arranged so as to surround the outer peripheral surface of the shaft portion of the shaft portion and is divided into a plurality of circumferential directions, and a drive mechanism that moves the sliding bearing divided body in the radial direction. Prepared,
In a state in which the shaft portion receives a load load during normal operation, the sliding bearing divided body and the shaft portion outer peripheral surface are not in contact with each other, and in a state in which the shaft portion receives an abnormal load load, The wind power generator, wherein the drive mechanism is an auxiliary support mechanism configured to move the sliding bearing divided body in the axial center direction so as to contact the outer peripheral surface of the shaft portion.

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