A rolling and sliding hybrid bearing support device for a wind power speed increasing gearbox

Abstract

The present invention relates to a rolling and sliding hybrid bearing support device for a wind power speed-increasing gearbox. The main purpose is to solve the technical problem of bearing friction and wear life under low-speed speed change and multiple start-stop conditions that exist in existing wind power gearboxes that independently use rolling bearings or sliding bearings. The technical solution adopted by the present invention is: a rolling and sliding hybrid bearing support device for a wind power speed-increasing gearbox, which includes four rolling and sliding hybrid bearing bodies, cylindrical roller bearings and radial sliding bearings, the first rolling and sliding hybrid bearing body is supported on the left side of the inner meshing planetary gear, the second rolling and sliding hybrid bearing body is supported between the inner meshing planetary gear and the outer meshing planetary gear, the third and fourth rolling and sliding hybrid bearing bodies are supported on both sides of two high-speed parallel herringbone gears, and the cylindrical roller bearings and radial sliding bearings are supported on the left and right sides of the high-speed pinion shaft. The present invention has the advantages of improving the service reliability and service life of the wind power gearbox bearings, shortening the replacement cycle, and reducing the use cost.

Description

Technical Field

[0001] The invention belongs to the technical field of speed-increasing gearbox support devices, and in particular relates to a rolling-sliding hybrid bearing support device of a wind power speed-increasing gearbox. Background Art

[0002] At present, the mainstream support technology for the shaft system of wind power gearbox is rolling bearing. With the improvement of gearbox size, weight, cost and reliability, wind power gearbox begins to study and apply sliding bearing support scheme in actual use. These two bearing support technologies have obvious advantages and disadvantages: rolling bearings are standard parts, easy to install and use, but short service life, high cost, and easy to slip, wear and cause early failure of bearings under certain working conditions. With the demand for high-power gearboxes, the contradiction between the bearing capacity and speed of rolling bearings has become more prominent; sliding bearings have simple structure and convenient installation, especially large bearing capacity, high speed, low noise, and long service life due to liquid lubrication. However, in the case of low-speed speed change and start-stop, the sliding bearing is in a mixed lubrication state due to insufficient speed, which is prone to wear and local over-temperature, seriously reducing the service life and operation reliability of the sliding bearing. Therefore, both the two independently used rolling bearing or sliding bearing support schemes have the problem of gearbox service reliability due to wear under low speed and heavy load conditions. Especially in offshore wind power equipment, the replacement of parts is difficult, costly and long, which affects the power generation efficiency. Summary of the invention

[0003] The purpose of the present invention is to solve the technical problem of bearing friction and wear life under low-speed shifting and multiple start-stop conditions that exists when existing wind power gearboxes independently use rolling bearings or sliding bearings, and to provide a rolling and sliding hybrid bearing support device for a wind power speed increase gearbox.

[0004] In order to solve the above technical problems, the technical solution adopted by the present invention is:

[0005] A rolling and sliding hybrid bearing support device for a wind power speed increasing gearbox comprises four rolling and sliding hybrid bearing bodies, cylindrical roller bearings and radial sliding bearings, wherein the first rolling and sliding hybrid bearing body is supported on the left side of an inner meshing planetary gear, the second rolling and sliding hybrid bearing body is supported between the inner meshing planetary gear and the outer meshing planetary gear, the third and fourth rolling and sliding hybrid bearing bodies are supported on both sides of two high-speed parallel herringbone gears, and the cylindrical roller bearings and radial sliding bearings are supported on the left and right sides of a high-speed pinion shaft.

[0006] Furthermore, the first rolling-sliding hybrid bearing body is composed of a No. 1 radial sliding bearing and a No. 1 tapered roller bearing and is coaxially assembled. The No. 1 radial sliding bearing is mounted on the No. 1 bearing seat by bolts and locating pins. The inner and outer rings of the No. 1 tapered roller bearing are respectively mounted on the planetary gear shaft and the No. 1 bearing seat and are located between the No. 1 radial sliding bearing and the left side of the inner meshing planetary gear.

[0007] Furthermore, the second rolling-sliding hybrid bearing body is composed of a No. Ⅱ radial sliding bearing and a No. Ⅱ tapered roller bearing and is coaxially assembled. The No. Ⅱ radial sliding bearing is installed on the No. Ⅱ bearing seat by bolts and locating pins. The inner and outer rings of the No. Ⅱ tapered roller bearing are respectively installed on the planetary gear shaft and the No. Ⅱ bearing seat and are located between the No. Ⅱ radial sliding bearing and the right side of the inner meshing planetary gear.

[0008] Furthermore, the third rolling-sliding hybrid bearing body is composed of a No. III radial sliding bearing and a No. III tapered roller bearing and is coaxially assembled. The No. III radial sliding bearing is mounted on the No. III bearing seat by bolts and locating pins. The inner and outer rings of the No. III tapered roller bearing are respectively mounted on the hollow shaft and the No. III bearing seat and are located between the No. III radial sliding bearing and the left side of the first high-speed herringbone gear; the fourth rolling-sliding hybrid bearing body is composed of a No. IV radial sliding bearing and a No. IV tapered roller bearing and is coaxially assembled. The No. IV radial sliding bearing is mounted on the No. IV bearing seat by bolts and locating pins. The inner and outer rings of the No. IV tapered roller bearing are respectively mounted on the hollow shaft and the No. IV bearing seat and are located between the No. IV radial sliding bearing and the right side of the second high-speed herringbone gear.

[0009] The beneficial effects of the present invention are:

[0010] The rolling and sliding hybrid bearing support device adopted by the present invention is composed of rolling bearings and sliding bearings. The rolling bearings support the rotating shaft under ultra-low speed conditions such as starting and stopping, and the sliding bearings support the rotating shaft under the state of forming a lubricating film such as relatively high speed. The combined work of the two can avoid the direct contact between the sliding bearing and the rotating shaft during the starting and stopping process, and can effectively improve the situation of sudden changes in friction torque of the gearbox rotating shaft during operation, effectively reduce the friction and wear of the sliding bearing under working conditions such as starting and stopping, and increase the bearing capacity and speed of the gearbox system. This complementary advantage of rolling and sliding performance can significantly improve the service reliability of the gearbox and extend the service life, especially for offshore wind power equipment gearboxes, it can reduce the number of parts replacements, reduce high operating costs, and improve power generation efficiency. It solves the technical problem of bearing friction and wear life under low-speed speed change and multiple starts and stops when the existing wind power gearbox uses rolling bearings or sliding bearings independently. Compared with the background technology, the present invention has the advantages of improving the service reliability and service life of wind power gearbox bearings, shortening the replacement cycle, and reducing the use cost. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Figure 1It is the support principle diagram of the present invention;

[0012] Figure 2 A schematic diagram of the structure of the present invention. DETAILED DESCRIPTION

[0013] The present invention is described in detail below with reference to the accompanying drawings and embodiments.

[0014] like Figures 1-2 As shown, a rolling and sliding hybrid bearing support device of a wind power speed increasing gearbox in this embodiment includes four rolling and sliding hybrid bearing bodies, a cylindrical roller bearing R5 and a radial sliding bearing S5. The first rolling and sliding hybrid bearing body is supported on the left side of the inner meshing planetary gear 2, the second rolling and sliding hybrid bearing body is supported between the inner meshing planetary gear 2 and the outer meshing planetary gear 3, the third and fourth rolling and sliding hybrid bearing bodies are supported on both sides of two high-speed parallel herringbone gears 5 and 6, the inner ring of the cylindrical roller bearing R5 is mounted on the left side of the high-speed pinion shaft 12, and the outer ring is mounted on the box component 13 and the No. III bearing seat B3 to bear the radial load of the high-speed pinion shaft 12, and the radial sliding bearing S5 is installed on the No. V bearing seat B5 by bolts and locating pins and is located on the right side of the high-speed pinion shaft 12.

[0015] The first rolling-sliding hybrid bearing body is composed of a No. Ⅰ radial sliding bearing S1 and a No. Ⅰ tapered roller bearing R1 and is coaxially assembled. The No. Ⅰ radial sliding bearing is mounted on the No. Ⅰ bearing seat B1 through bolts and locating pins. The inner and outer rings of the No. Ⅰ tapered roller bearing are respectively mounted on the planetary gear shaft 9 and the No. Ⅰ bearing seat and are located between the No. Ⅰ radial sliding bearing and the left side of the inner meshing planetary gear 2. The No. Ⅰ tapered roller bearing R1 bears the axial load of the planetary gear shaft 9.

[0016] The second rolling-sliding hybrid bearing body is composed of a radial sliding bearing S2 No. Ⅱ and a tapered roller bearing R2 and is coaxially assembled. The radial sliding bearing S2 No. Ⅱ is mounted on the bearing seat B2 No. Ⅱ through bolts and locating pins. The inner and outer rings of the tapered roller bearing R2 No. Ⅱ are respectively mounted on the planetary gear shaft 9 and the bearing seat B2 No. Ⅱ and are located between the radial sliding bearing S2 No. Ⅱ and the right side of the inner meshing planetary gear 2. The tapered roller R2 bearing No. Ⅱ bears the axial load of the planetary gear shaft 9.

[0017] The third rolling-sliding hybrid bearing body is composed of a radial sliding bearing S3 No. Ⅲ and a tapered roller bearing R3 and is coaxially assembled. The radial sliding bearing S3 No. Ⅲ is mounted on the bearing seat B3 No. Ⅲ by bolts and locating pins. The inner and outer rings of the tapered roller bearing R3 No. Ⅲ are respectively mounted on the hollow shaft 11 and the bearing seat B3 No. Ⅲ and are located between the radial sliding bearing S3 No. Ⅲ and the left side of the first high-speed herringbone gear 5; the tapered roller bearing R3 No. Ⅲ bears the axial load of the hollow shaft 11. The fourth rolling-sliding hybrid bearing body is composed of a radial sliding bearing S4 No. Ⅳ and a tapered roller bearing R4 and is coaxially assembled. The radial sliding bearing S4 No. Ⅳ is mounted on the bearing seat B4 No. Ⅳ by bolts and locating pins. The inner and outer rings of the tapered roller bearing R4 No. Ⅳ are respectively mounted on the hollow shaft 11 and the bearing seat B4 No. Ⅳ and are located between the radial sliding bearing S4 No. Ⅳ and the right side of the second high-speed herringbone gear 6. The tapered roller bearing R4 No. Ⅳ bears the axial load of the hollow shaft 11.

[0018] The specific working principle and process of the present invention are as follows:

[0019] The rolling and sliding hybrid bearing support device of the wind power gearbox described in the present invention is composed of a sliding bearing and a rolling bearing coaxially assembled, the rolling bearing has a clearance, the sliding bearing has an oil film gap, and the clearance of the rolling bearing is smaller than the oil film gap of the sliding bearing. The rolling and sliding hybrid bearing support device has the following two stage characteristics when working: one is the ultra-low speed start-stop stage, because the clearance of the rolling bearing is smaller than the oil film gap of the sliding bearing, the rotating shaft is directly pressed on the rolling bearing under the action of gravity or other loads, and the rolling bearing supports the rotating shaft so that the rotating shaft cannot directly contact with the sliding bearing. When the rotating shaft starts or stops at an ultra-low speed, the sliding bearing cannot form enough oil film pressure to float the rotating shaft. The rolling bearing plays the role of mainly supporting the rotating shaft, achieving the purpose of smooth starting or stopping of the rotating shaft, and avoiding or reducing the friction and wear of the sliding bearing. The second is the high-speed stable operation stage. When the rotating shaft reaches a certain speed, the sliding bearing can form a stable oil film pressure and suspend the rotating shaft. At this time, the inner ring of the rolling bearing installed on the rotating shaft floats up with the rotating shaft and is out of contact with the rolling body. The rolling bearing no longer bears the load of the rotating shaft, and the sliding bearing independently carries and supports the rotating shaft to rotate.

[0020] The rolling bearings used in the present invention are all tapered roller bearings R1, R2, R3, R4, which not only support the rotating shaft in the start-stop stage, but also bear the axial load of the rotating shaft in the stable operation stage. The gearbox input torque Tin drives the inner ring gear 1 to rotate, and the inner ring gear 1 drives the inner meshing planetary gear 2 to rotate. The outer meshing planetary gear 3 and the inner meshing planetary gear 2 are the same planetary gear shaft 9 and rotate together. The outer meshing planetary gear 3 drives the sun gear 4 to rotate. The hollow shaft 11 is installed on the sun gear shaft 10. The first and second high-speed parallel herringbone gears 5 and 6 are installed on the hollow shaft 11. The sun gear 4, the sun gear shaft 10, the hollow shaft 11 and the first and second high-speed parallel herringbone gears 5 and 6 rotate together as a whole. The first and second high-speed parallel herringbone gears 5 and 6 drive the first and second high-speed parallel herringbone pinion gears 7 and 8 to rotate. The first and second high-speed parallel herringbone pinion gears 7 and 8 are installed on the high-speed pinion shaft 12. The high-speed pinion shaft 12 serves as the output shaft of the gearbox and outputs the torque Tout. During ultra-low-speed movements such as when the gearbox is started and stopped, the radial load and axial load generated by the inner ring gear 1 and the inner meshing planetary gear 2 and the outer meshing planetary gear 3 and the sun gear 4 on the planetary gear shaft 9 are jointly borne by the No. Ⅰ tapered roller bearing R1 and the No. Ⅱ tapered roller bearing R2; the radial load and axial load generated by the outer meshing planetary gear 3 and the sun gear 4 and the radial load generated by the first and second high-speed parallel herringbone pinions 7, 8 and the first and second high-speed parallel herringbone gears 5, 6 on the hollow shaft 11 are jointly borne by the No. Ⅲ tapered roller bearing R3 and the No. Ⅳ tapered roller bearing R4; the radial load generated by the first and second high-speed parallel herringbone pinions 7, 8 and the first and second high-speed parallel herringbone gears 5, 6 on the high-speed pinion shaft 12 is jointly borne by the cylindrical roller bearing R5 and the radial sliding bearing S5. When the gearbox is running stably, the radial load generated by the inner gear ring 1 and the inner meshing planetary gear 2 and the outer meshing planetary gear 3 and the sun gear 4 on the planetary gear shaft 9 is jointly borne by the radial sliding bearing S1 No. Ⅰ and the radial sliding bearing S2 No. Ⅱ, and the axial load generated by the inner gear ring 1 and the inner meshing planetary gear 2 and the outer meshing planetary gear 3 and the sun gear 4 on the planetary gear shaft 9 is jointly borne by the tapered roller bearing R1 No. Ⅰ and the tapered roller bearing R2 No. Ⅱ; the hollow shaft 11 is borne by the outer meshing planetary gear 3 and the sun gear 4 and the first and second high-speed parallel herringbone pinions 7, 8 and The radial loads generated by the first and second high-speed parallel herringbone gears 5 and 6 are jointly borne by radial sliding bearings No. III and No. IV, and the axial loads generated by the hollow shaft 11 due to the external meshing planetary gears 3 and the sun gear 4 are jointly borne by tapered roller bearings No. III and No. IV, R4; the radial loads generated by the first and second high-speed parallel herringbone pinions 7 and 8 and the first and second high-speed parallel herringbone gears 5 and 6 on the high-speed pinion shaft 12 are jointly borne by cylindrical roller bearings R5 and radial sliding bearings S5.

Claims

1. A rolling and sliding hybrid bearing support device for a wind power speed increasing gearbox, characterized in that: The invention comprises four rolling and sliding hybrid bearing bodies, a cylindrical roller bearing (R5) and a radial sliding bearing (S5), wherein the first rolling and sliding hybrid bearing body is supported on the left side of the inner meshing planetary gear (2), the second rolling and sliding hybrid bearing body is supported between the inner meshing planetary gear (2) and the outer meshing planetary gear (3), the third rolling and sliding hybrid bearing body and the fourth rolling and sliding hybrid bearing body are supported on both sides of two high-speed parallel herringbone gears (5, 6), and the cylindrical roller bearing (R5) and the radial sliding bearing (S5) are supported on the left and right sides of the high-speed pinion shaft (12); The first rolling-sliding hybrid bearing body is composed of a No. 1 radial sliding bearing (S1) and a No. 1 tapered roller bearing (R1) and is coaxially assembled. The No. 1 radial sliding bearing is mounted on the No. 1 bearing seat (B1) through bolts and positioning pins. The inner and outer rings of the No. 1 tapered roller bearing are respectively mounted on the planetary gear shaft (9) and the No. 1 bearing seat and are located between the No. 1 radial sliding bearing and the left side of the inner meshing planetary gear (2); The second rolling-sliding hybrid bearing body is composed of a No. II radial sliding bearing (S2) and a No. II tapered roller bearing (R2) and is coaxially assembled. The No. II radial sliding bearing (S2) is mounted on the No. II bearing seat (B2) by bolts and positioning pins. The inner and outer rings of the No. II tapered roller bearing (R2) are respectively mounted on the planetary gear shaft (9) and the No. II bearing seat (B2) and are located between the No. II radial sliding bearing (S2) and the right side of the inner meshing planetary gear (2); The third rolling-sliding hybrid bearing body is composed of a No. III radial sliding bearing (S3) and a No. III tapered roller bearing (R3) and is coaxially assembled. The No. III radial sliding bearing (S3) is mounted on the No. III bearing seat (B3) by bolts and positioning pins. The inner and outer rings of the No. III tapered roller bearing (R3) are respectively mounted on the hollow shaft (11) and the No. III bearing seat (B3) and are located between the No. III radial sliding bearing (S3) and the left side of the first high-speed herringbone gear (5); The fourth rolling-sliding hybrid bearing body is composed of a No. IV radial sliding bearing (S4) and a No. IV tapered roller bearing (R4) and is coaxially assembled. The No. IV radial sliding bearing (S4) is mounted on the No. IV bearing seat (B4) by bolts and positioning pins. The inner and outer rings of the No. IV tapered roller bearing (R4) are respectively mounted on the hollow shaft (11) and the No. IV bearing seat (B4) and are located between the No. IV radial sliding bearing (S4) and the right side of the second high-speed herringbone gear (6).

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