CN201461270U - Drive shaft support structure of wind power generation gearbox - Google Patents

Abstract

The utility model discloses a supporting structure for a transmission shaft of a wind-power step-up box. The supporting structure comprises a front box body (1), a main shaft (5) and a planet shaft (6), wherein the main shaft (5) is supported on the front box body (1) by a double-row tapered roller bearing (3). In the utility model, the main shaft adopts one double-row tapered roller bearing, thereby reducing the quantity of the bearing, reducing the axis deflection of the main shaft caused by the unsteady load and the clearance of a rear bearing and being helpful for steady meshing. The double-row tapered roller bearing has big radial size and has pre-load, the distribution of the roller patch stress is better, and the impact resistance is stronger; the quantity of rollers can be large, and the stress of single roller is smaller, so as to ensure the long-time steady running. The utility model reduces the processing quantity of bearing holes and shaft necks, thereby avoiding the affection caused by the pre-load and decentration due to the processing error, being helpful for the load distribution of a gear, prolonging the running time and improving the running reliability.

Description

Drive shaft support structure of wind power generation gearbox

technical field

The utility model belongs to the technical field of a speed-up gearbox for high-power wind power generation, and in particular relates to a bearing arrangement method for a main shaft of a speed-up gearbox used in the wind power generation industry.

Background technique

At present, there are many ways to configure the bearings of domestic wind power speed-up gearboxes. For large transmission shafts such as main shafts and planetary carriers, the bearing configurations are often self-aligning, cylindrical, and conical. Due to the differentiation of the units, higher requirements are put forward for the bearing configuration of the large transmission shaft. Since the wind load and gravity of the hub impeller are borne by the bearing on the main shaft, the axial and radial load requirements of the front bearing are relatively high, while the load requirements of the rear bearing are relatively low, and its size is determined by the span of the bearing and the size of the model. If the size of the main shaft is to be shortened, the specification of the rear bearing must be increased. For some long spindle models, the spindle often has three or four bearing configurations, showing an over-positioning state. The disadvantages of traditional dual bearing arrangements are:

1. The axial dimension is large, the processing range is large, and there are more quality control points and failure points.

2. Unstable load and rear bearing clearance will cause the axis of the main shaft to sway, which is not conducive to smooth meshing, and on the other hand, the impact resistance is weak, making it difficult to ensure long-term stable operation.

3. The number of machining of bearing holes and journals is large, and the preload and non-concentricity caused by machining errors will affect the gear load distribution, shorten the running time, and the running reliability is poor.

Utility model content

The technical problem to be solved by the utility model is to provide a transmission shaft support structure of a wind power generation speed-up box that can operate continuously, effectively and stably.

The technical scheme of the utility model is as follows: a wind power generation gearbox drive shaft support structure, including the front box, the main shaft and the planetary shaft, the key lies in: the main shaft is supported on the box by a double-row tapered roller bearing .

With the above technical scheme, the main shaft only has double-row tapered roller bearings at the front end, and there is no support bearing at the rear end, which is supported by a single bearing and is in a cantilever state. The input load is transmitted to the main shaft, and the radial load, axial load and torque are transmitted to the front box through the bearing, and then to the tower; the torque is transmitted to the planetary shaft through the main shaft, and the planetary shaft is stressed by a set of planetary gears. Parallel force balance, this group of parallel force distribution is transmitted to the ring gear and the sun gear, the force of the ring gear is transmitted to the tower through the rear box, and the force of the sun gear is transmitted to the output shaft sleeve to the motor or the second-stage meshing transmission output . The utility model has a reasonable and compact structure, can run continuously, effectively and stably, and can better meet the operation requirements of medium and high-power wind turbines, especially when the axial dimension requirement is relatively short.

The double-row tapered roller bearing is composed of two inner rings, two rows of rollers and an outer ring, wherein the two inner rings are tightly fitted, each inner ring is interference fit with the main shaft, and the two inner rings pass through two The symmetrically arranged rollers are in rolling fit with the outer ring, and the outer ring is fixed with the front box by bolts. The above structure is simple and reliable, and easy to assemble; the double-row tapered roller bearing is configured with interference so that when it is subjected to a bending moment, the rollers on the left and right sides are diagonally stressed. The roller raceway has good rigidity, and the axis deflection under the rated load is extremely small, which has little effect on the meshing of planetary stage gears, and is conducive to smooth load output.

The raceway angle of the rollers in the double-row tapered roller bearing is 43° to 47°. The cone angle of about 45° enables the raceway to withstand the stress caused by the force couple of the balanced bending moment, and the number of rollers is greatly reduced. The stress borne by a single roller can resist bending energy and bear radial and axial loads at the same time.

The beneficial effects of the utility model are:

1. The main shaft is supported by a double-row tapered roller bearing, which reduces the number of bearings, reduces the yaw of the main shaft axis caused by unstable load and rear bearing clearance, and helps to mesh smoothly.

2. The double-row tapered roller bearing has a large radial dimension and preload, the raceway stress distribution is good, and the impact resistance is strong; the number of rollers is large, and the stress of a single roller is small, which can ensure long-term stable operation .

3. Reduce the number of machining bearing holes and journals, avoid the influence of preload and non-concentricity caused by machining errors, contribute to gear load distribution, prolong operating time, and improve operating reliability.

4. The structure described in the utility model has a wide application range, and can be used not only for the main shaft, but also for the planet carrier, the planet wheel or the low-speed shaft of the wind power gearbox.

Description of drawings

Fig. 1 is the structural representation of the utility model.

Detailed ways

Below in conjunction with accompanying drawing and embodiment the utility model is further described:

As shown in Figure 1, the utility model is composed of a front box body 1, bolts 2, double-row tapered roller bearings 3, an input oil throwing pan 4, a main shaft 5 and a planetary shaft 6, wherein the input oil throwing pan 4 is fixedly sleeved on the main shaft 5, planet shaft 6 is installed at the rear end of main shaft 5. The main shaft 5 is installed in the front box body 1, and is supported on the box body 1 by a double-row tapered roller bearing 3, and the double-row tapered roller bearing 3 is forcedly lubricated by multiple oil injections on both sides (as shown in the figure indicated by the arrow). The double-row tapered roller bearing 3 is composed of two inner rings, two rows of rollers and an outer ring, wherein the two inner rings are tightly fitted, and each inner ring is in interference fit with the main shaft 5, and the two inner rings Through the rolling fit between two rows of symmetrically arranged rollers and the outer ring, the raceway angle of the rollers is 43-47°, preferably 45° in this embodiment. The outer ring is fixed to the front box body 1 by bolts 2 .

The working principle of the utility model is: the load is transmitted to the main shaft 5, the double-row tapered roller bearing 3 has a raceway angle of 45°, and the radial load, axial load and torque are all transmitted to the front box through the double-row tapered roller bearing 3 Body 1, and then transmitted to the tower; the torque is transmitted to the planetary shaft 6 through the main shaft 5, and the force on the planetary shaft 6 is balanced by a group of parallel forces on the planetary gear, and the distribution of this group of parallel forces is transmitted to the ring gear and the sun gear. The force of the inner ring gear is transmitted to the tower through the rear box, and the force of the sun gear is transmitted to the output shaft sleeve to the motor or the second-stage meshing transmission output.

Claims (3)

1. A wind power generation gearbox drive shaft support structure, comprising a front box (1), a main shaft (5) and a planetary shaft (6), characterized in that: the main shaft (5) passes through a double-row tapered roller The bearing (3) is supported on the casing (1). 2. The transmission shaft support structure of the wind power generation gearbox according to claim 1, characterized in that: the double-row tapered roller bearing (3) is composed of two inner rings, two rows of rollers and an outer ring, The two inner rings are tightly fitted, each inner ring is in interference fit with the main shaft (5), and the two inner rings are rolled and fitted with the outer ring through two rows of symmetrically arranged rollers, and the outer ring is passed through the bolt (2) Fix it with the front box (1). 3. The drive shaft support structure of the wind power generation gearbox according to claim 2, characterized in that: the raceway angle of the rollers in the double-row tapered roller bearing (3) is 43° to 47°.

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