CN216199826U - Bearing group applied to power turbine - Google Patents
Bearing group applied to power turbine Download PDFInfo
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- CN216199826U CN216199826U CN202121701207.3U CN202121701207U CN216199826U CN 216199826 U CN216199826 U CN 216199826U CN 202121701207 U CN202121701207 U CN 202121701207U CN 216199826 U CN216199826 U CN 216199826U
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Abstract
The utility model belongs to the technical field of energy power, and particularly relates to a bearing set applied to a power turbine. The utility model introduces the elastic ring into the outer ring fixing structure of the ball bearing, and controls the axial stress of the ball bearing by the precompression of the elastic ring and the clearance between the thrust bearing and the thrust bearing. The introduction of the elastic ring increases the axial crosstalk of the rotor, so that the gap between the thrust bearing and the thrust bearing under the installation condition can be increased, and the assembly process is optimized. After the power turbine is shut down, the thrust bearing and the thrust bearing can be separated due to the existence of the elastic element, so that lubricating oil is prevented from adhering to the thrust bearing and the thrust bearing, and the starting performance under a cold condition is optimized. When the power turbine is initially designed, the optimal axial stress load of the ball bearing and the stress and deformation corresponding relation of the elastic ring are known, and the pre-compression amount of the elastic ring and the gap value between the thrust bearing and the thrust bearing, which enable the ball bearing to be in the optimal axial load state, can be solved.
Description
Technical Field
The utility model belongs to the technical field of energy power, and particularly relates to a bearing set applied to a power turbine.
Background
The ball bearing is used as a key part in the power turbine, plays a role in supporting a rotor structure, and has great influence on the reliability and the service life of the power turbine in the working state. Ball bearings can bear both radial and axial loads. The size of axial load is very big to ball bearing's life-span influence, and when axial load was too big, ball bearing's fatigue wear aggravation will make the working life greatly reduced of bearing, and when axial load was too little, ball bearing took place the phenomenon of skidding easily, will also make the life greatly reduced of bearing. Therefore, the axial stress of the ball bearing in the working state needs to be reasonably controlled, the ball bearing works in the designed axial load state as much as possible, the abrasion of the ball bearing is effectively reduced, and the service life of the ball bearing is prolonged.
The axial force applied to the power turbine rotor is mainly borne by the thrust bearing and the ball bearing together. In the traditional structure, the axial load borne by the ball bearing is adjusted only by singly adjusting the gap between the thrust bearing and the thrust bearing, and the gap value is small and is difficult to control. In addition, after the power turbine is shut down, the thrust bearing and the thrust bearing are not easy to separate, and under a cold condition, the thrust bearing and the thrust bearing are adhered by lubricating oil, so that the power turbine is difficult to start.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a bearing set applied to a power turbine.
The purpose of the utility model is realized by the following technical scheme: comprises a bearing shell 1, a thrust bearing 5, a thrust bearing 6, a ball bearing 7 and an inner shaft sleeve 9; the inner shaft sleeve 9 is connected with the power turbine shaft 11 and plays a role in supporting the power turbine shaft 11; the ball bearing 7 comprises an outer ring 13, balls 15 and an inner ring 16; the device also comprises an elastic ring 3 and a pressure ring 4; the elastic ring 3 is of an annular structure, and bosses are distributed on the front side surface and the rear side surface of the elastic ring 3 in the circumferential direction; the compression ring 4 compresses the elastic ring 3 on the right end face of the outer ring 13 of the ball bearing 7, so that the elastic ring 3 generates pre-compression deformation; the left end face of the thrust bearing 5 is connected with the right end face of an inner ring 16 of the ball bearing 7 through an adjusting ring 8, and the inner surface of the thrust bearing 5 is fixed on the outer surface of the inner shaft sleeve 9; the thrust bearing 6 is arranged on the right side of the thrust bearing 5, and a gap is reserved between the left end face of the thrust bearing 6 and the right end face of the thrust bearing 5.
The present invention may further comprise:
the initial precompression quantity of the elastic ring 3 is c/3, and the clearance between the thrust bearing 5 and the thrust bearing 6 is 2 c/3; c is the total compression deformation of the elastic ring 3 under the working condition determined according to the optimal axial load of the ball bearing 7 and the corresponding relation between the pressure and the deformation of the elastic ring 3.
The thrust bearing 5 is of an annular structure, the right end face of the thrust bearing 5 is a working face, and an oil film is formed between the thrust bearing 5 and the left end face of the thrust bearing 6 during working to bear the axial force of the power turbine rotor.
The outer circle surface of an outer ring 13 of the ball bearing 7 is contacted with the inner surface of the shaft sleeve 2, and the outer circle surface of the shaft sleeve 2 is contacted with the inner surface of the bearing shell 1, so that the ball bearing 7 is radially supported; the inner hole surface of the inner ring 16 of the ball bearing 7 is contacted with the outer circle surface of the inner shaft sleeve 9.
Bosses are uniformly distributed on the front side face and the rear side face of the elastic ring 3 in a whole circle, the bosses are of a trapezoidal structure, and the bosses on the two sides are distributed in a staggered mode in the circumferential direction, so that the elastic ring 3 has certain elastic deformation capacity in the compression process.
The utility model has the beneficial effects that:
the utility model introduces the elastic ring into the outer ring fixing structure of the ball bearing, and controls the axial stress of the ball bearing by the precompression of the elastic ring and the clearance between the thrust bearing and the thrust bearing. The introduction of the elastic ring increases the axial crosstalk of the rotor, so that the gap between the thrust bearing and the thrust bearing under the installation condition can be increased, and the assembly process is optimized. After the power turbine is shut down, the thrust bearing and the thrust bearing can be separated due to the existence of the elastic element, so that lubricating oil is prevented from adhering to the thrust bearing and the thrust bearing, and the starting performance under a cold condition is optimized. When the power turbine is initially designed, the optimal axial stress load of the ball bearing and the stress and deformation corresponding relation of the elastic ring are known, and the pre-compression amount of the elastic ring and the gap value between the thrust bearing and the thrust bearing, which enable the ball bearing to be in the optimal axial load state, can be solved.
Drawings
Fig. 1 is a schematic view of the installation of the present invention.
Fig. 2 is a schematic view of a ball bearing structure.
Fig. 3 is a three-dimensional structural view of the elastic ring.
Fig. 4 is a front view of the elastic ring.
Fig. 5 is a reverse view of the elastic ring.
FIG. 6 is a flow chart of a design of ball bearing axial load adjustment.
Detailed Description
The utility model is further described below with reference to the accompanying drawings.
The utility model introduces the elastic element of the elastic ring into the outer ring fixing structure of the ball bearing innovatively, and controls the axial stress of the ball bearing by two parts of structures, one part is the pre-compression of the elastic ring, and the other part is the gap between the thrust bearing and the thrust bearing. The introduction of the elastic ring enables the axial movement amount of the rotor to be increased, further the gap between the thrust bearing and the thrust bearing under the installation condition can be increased, the assembly process is optimized, in addition, after the power turbine is stopped, the thrust bearing and the thrust bearing can be separated due to the existence of the elastic element, the lubricating oil is prevented from adhering to the thrust bearing and the thrust bearing, and the starting performance under the cold condition is optimized. When the power turbine is initially designed, the optimal axial stress load of the ball bearing and the corresponding relation between the stress and the deformation of the elastic ring are known, the total compression amount of the elastic ring in the working state of the power turbine can be solved, and the total compression amount is reasonably distributed to the pre-compression amount of the elastic ring and the gap value between the thrust bearing and the thrust bearing, so that the ball bearing is in the optimal axial load state when the power turbine runs. The utility model has the characteristics of simple structure, large adjustment freedom, convenient installation and high structural reliability.
A bearing group applied to a power turbine comprises a bearing shell 1, an elastic ring 3, a pressure ring 4, a thrust bearing 5, a thrust bearing 6, a ball bearing 7 and an inner shaft sleeve 9; the inner shaft sleeve 9 is connected with the power turbine shaft 11 and plays a role in supporting the power turbine shaft 11; the ball bearing 7 comprises an outer ring 13, balls 15 and an inner ring 16; the elastic ring 3 is of an annular structure, and bosses are distributed on the front side surface and the rear side surface of the elastic ring 3 in the circumferential direction; the compression ring 4 compresses the elastic ring 3 on the right end face of the outer ring 13 of the ball bearing 7, so that the elastic ring 3 generates pre-compression deformation; the left end face of the thrust bearing 5 is connected with the right end face of an inner ring 16 of the ball bearing 7 through an adjusting ring 8, and the inner surface of the thrust bearing 5 is fixed on the outer surface of the inner shaft sleeve 9; the thrust bearing 6 is arranged on the right side of the thrust bearing 5, and a gap is reserved between the left end face of the thrust bearing 6 and the right end face of the thrust bearing 5.
When the power turbine starts to operate, the axial force of the rotor sequentially passes through the inner shaft sleeve, the ball bearing inner ring, the balls and the ball bearing outer ring to be transmitted to the elastic ring, so that the elastic ring is further compressed, the rotor further generates axial movement, when the ball bearing reaches the optimal axial stress load, the thrust bearing just contacts with the thrust bearing to form an oil film, the continuously increased axial force of the rotor is borne, and the axial force borne by the ball bearing is not increased any more.
The total compression amount of the elastic ring consists of two parts, one part is the precompression value of the elastic ring, and the other part is the initial installation gap value of the thrust bearing and the thrust bearing. Knowing the total compression amount of the elastic ring, the axial force value borne by the elastic ring can be obtained through the corresponding relation between the pressure and the deformation amount of the elastic ring, and meanwhile, the axial force borne by the ball bearing is equal to the axial force borne by the elastic ring in magnitude, so that the axial force borne by the ball bearing during the operation of the power turbine can be obtained.
When the power turbine is initially designed, the optimal axial stress load of the ball bearing and the stress and deformation corresponding relation of the elastic ring are known, the total compression amount of the elastic ring in the working state of the power turbine can be solved, and then the total compression amount is reasonably distributed to the pre-compression amount of the elastic ring and the initial installation gap between the thrust bearing and the thrust bearing, so that the ball bearing is in the optimal axial load state when the power turbine runs.
Example 1:
when the power turbine is initially designed, the design indexes of the power turbine and the requirements of the overall structure size are known, and the model selection or design of the ball bearing is completed; after the type or the structure of the ball bearing is determined, the optimal axial load of the ball bearing under the working condition can be obtained through theoretical calculation; according to the structural size of the ball bearing, the design of an elastic ring structure is completed, and the good contact between an elastic ring boss and the end face of the outer ring of the ball bearing is ensured; after the design of the elastic ring structure is finished, applying pressure loads on two sides of the elastic ring by using a tensile testing machine to obtain the relation between the pressure and the deformation of the elastic ring; determining the total compression deformation c of the elastic ring under the working state according to the optimal axial load of the ball bearing and the corresponding relation between the pressure and the deformation of the elastic ring; the total compression deformation c of the elastic ring is distributed to the initial precompression a of the elastic ring and the initial gap b between the thrust bearing and the thrust bearing according to the ratio of 1:2, wherein a is c/3, and b is 2 c/3. The schematic flow chart of the design of the ball bearing axial load adjustment is shown in fig. 6.
Before installation, a tensile testing machine is used for pressing the two surfaces with the bosses of the elastic ring, and the corresponding relation between the pressure and the deformation of the elastic ring can be obtained. The compression of the elastic ring can be adjusted by grinding the surface a of the compression ring 4 during mounting, and the compression is denoted as a. By changing the axial thickness of the adjusting ring 8, the gap b between the thrust bearing and the thrust bearing can be adjusted.
When the power turbine starts to operate, the axial force of the rotor sequentially passes through the inner shaft sleeve 9, the ball bearing inner ring 16, the balls 15 and the ball bearing outer ring 13 and is transmitted to the elastic ring 3, so that the elastic ring is further compressed, the compression amount is b, the rotor further generates axial movement, when the ball bearing reaches the optimal axial stress load, the thrust bearing 5 just contacts with the thrust bearing 6 to form an oil film to bear the ever-increasing axial force of the rotor, and the axial force borne by the ball bearing 7 is not increased any more.
After the thrust bearing 5 and the thrust bearing 6 just contact, the total compression amount of the elastic ring 3 becomes a + b, and according to the corresponding relation between the elastic ring pressure and the deformation amount obtained earlier, the axial force value applied to the elastic ring 3 can be obtained, and meanwhile, the axial force applied to the ball bearing 7 is equal to the axial force applied to the elastic ring 3, so that the axial force applied to the ball bearing 7 during the operation of the power turbine can be obtained.
Example 2:
the thrust bearing is of an annular structure, the left end face of the thrust bearing is in contact with the right end face of the adjusting ring, the inner surface of the thrust bearing is fixed on the outer surface of the inner shaft sleeve, the right end face of the thrust bearing is a working face, and an oil film is formed between the thrust bearing and the left end face of the thrust bearing during working to bear the axial force of the power turbine rotor. The gap value between the thrust bearing and the thrust bearing in the initial state can be adjusted by changing the axial dimension of the adjusting ring.
Example 3:
the axial load adjustment structure mounting arrangement position of the ball bearing is shown in fig. 1. The ball bearing 7 is composed of an outer ring 13, a retainer 14, balls 15 and an inner ring 16, and the structure of the ball bearing is shown in fig. 2. The outer circle surface of the outer ring 13 is contacted with the inner surface of the shaft sleeve 2, and the outer circle surface of the shaft sleeve 2 is contacted with the inner surface of the bearing shell 1, so that the radial support effect on the ball bearing 7 is realized; the left end face of the outer ring 13 is in contact with the bearing shell 1, the right end face of the outer ring is in contact with the elastic ring 3, the outer ring 13 and the shaft sleeve 2 are axially fixed through the bolt 12 and the pressing ring 4, and the elastic ring 3 is enabled to have a certain degree of compression.
The surface of an inner hole of the inner ring 16 is contacted with the surface of an outer circle of the inner shaft sleeve 9, and the inner shaft sleeve 9 is connected with the shaft 11 to play a role in supporting the power turbine shaft 11; the left end face of the inner ring 16 is contacted with the end face of the inner shaft sleeve 9, the right end face of the inner ring 16 is contacted with the end face of the adjusting ring 8, and the inner ring 16 is fixed through the thrust bearing 5 and the nut 10. The thrust bearing is fixed to the bearing housing 1 by bolts 12.
Example 4:
the elastic ring is of an annular structure, the three-dimensional structure of the elastic ring is as shown in figure 4, 6 bosses are uniformly distributed on two side faces in a whole circle, the bosses are of a trapezoidal structure, and the bosses on two sides are distributed in a staggered mode in the circumferential direction and staggered at a certain angle, so that the elastic ring has certain elastic deformation capacity in the compression process. The front view land distribution is shown in fig. 5 and the back view land distribution is shown in fig. 6. Before assembly, the corresponding relation between the stress and the deformation of the elastic ring can be obtained through a tensile testing machine. In the installation, the elastic ring left side and ball bearing outer ring end face contact, right side and clamping ring inner ring end face contact, the boss of clamping ring inner ring compresses tightly the elastic ring right-hand member face for the elastic ring produces precompression and warp, and then compresses tightly ball bearing outer ring terminal surface. Meanwhile, the pre-compression deformation amount of the elastic ring can be adjusted by grinding the surface A of the compression ring. The compression ring is of an annular structure, is connected with the bearing shell through a bolt at the outer ring position, and compresses the right end face of the elastic ring at the inner ring position.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (9)
1. A bearing group applied to a power turbine comprises a bearing shell (1), a thrust bearing (5), a thrust bearing (6), a ball bearing (7) and an inner shaft sleeve (9); the inner shaft sleeve (9) is connected with the power turbine shaft (11) and plays a role in supporting the power turbine shaft (11); the ball bearing (7) comprises an outer ring (13), balls (15) and an inner ring (16); the method is characterized in that: the device also comprises an elastic ring (3) and a pressure ring (4); the elastic ring (3) is of an annular structure, and bosses are distributed on the front side surface and the rear side surface of the elastic ring (3) in the circumferential direction; the compression ring (4) compresses the elastic ring (3) on the right end face of the outer ring (13) of the ball bearing (7) so that the elastic ring (3) generates pre-compression deformation; the left end face of the thrust bearing (5) is connected with the right end face of an inner ring (16) of the ball bearing (7) through an adjusting ring (8), and the inner surface of the thrust bearing (5) is fixed on the outer surface of the inner shaft sleeve (9); the thrust bearing (6) is arranged on the right side of the thrust bearing (5), and a gap is reserved between the left end face of the thrust bearing (6) and the right end face of the thrust bearing (5).
2. A bearing set for a power turbine according to claim 1, wherein: the initial precompression amount of the elastic ring (3) is c/3, and the clearance between the thrust bearing (5) and the thrust bearing (6) is 2 c/3; c is the total compression deformation of the elastic ring (3) under the working state determined according to the optimal axial load of the ball bearing (7) and the corresponding relation between the pressure and the deformation of the elastic ring (3).
3. A bearing set for a power turbine according to claim 1 or 2, wherein: the thrust bearing (5) is of an annular structure, the right end face of the thrust bearing (5) is a working face, and an oil film is formed between the thrust bearing and the left end face of the thrust bearing (6) during working to bear the axial force of the power turbine rotor.
4. A bearing set for a power turbine according to claim 1 or 2, wherein: the outer circle surface of an outer ring (13) of the ball bearing (7) is in contact with the inner surface of the shaft sleeve (2), and the outer circle surface of the shaft sleeve (2) is in contact with the inner surface of the bearing shell (1) to radially support the ball bearing (7); the surface of an inner hole of an inner ring (16) of the ball bearing (7) is contacted with the surface of the excircle of the inner shaft sleeve (9).
5. A bearing set for a power turbine according to claim 3 wherein: the outer circle surface of an outer ring (13) of the ball bearing (7) is in contact with the inner surface of the shaft sleeve (2), and the outer circle surface of the shaft sleeve (2) is in contact with the inner surface of the bearing shell (1) to radially support the ball bearing (7); the surface of an inner hole of an inner ring (16) of the ball bearing (7) is contacted with the surface of the excircle of the inner shaft sleeve (9).
6. A bearing set for a power turbine according to claim 1 or 2, wherein: bosses are uniformly distributed on the front side face and the rear side face of the elastic ring (3) in a whole circle, the bosses are of a trapezoidal structure, and the bosses on the two sides are distributed in a staggered mode in the circumferential direction, so that the elastic ring (3) has certain elastic deformation capacity in the compression process.
7. A bearing set for a power turbine according to claim 3 wherein: bosses are uniformly distributed on the front side face and the rear side face of the elastic ring (3) in a whole circle, the bosses are of a trapezoidal structure, and the bosses on the two sides are distributed in a staggered mode in the circumferential direction, so that the elastic ring (3) has certain elastic deformation capacity in the compression process.
8. A bearing set for a power turbine according to claim 4 wherein: bosses are uniformly distributed on the front side face and the rear side face of the elastic ring (3) in a whole circle, the bosses are of a trapezoidal structure, and the bosses on the two sides are distributed in a staggered mode in the circumferential direction, so that the elastic ring (3) has certain elastic deformation capacity in the compression process.
9. A bearing set for a power turbine according to claim 5 wherein: bosses are uniformly distributed on the front side face and the rear side face of the elastic ring (3) in a whole circle, the bosses are of a trapezoidal structure, and the bosses on the two sides are distributed in a staggered mode in the circumferential direction, so that the elastic ring (3) has certain elastic deformation capacity in the compression process.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121701207.3U CN216199826U (en) | 2021-07-26 | 2021-07-26 | Bearing group applied to power turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121701207.3U CN216199826U (en) | 2021-07-26 | 2021-07-26 | Bearing group applied to power turbine |
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| Publication Number | Publication Date |
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| CN216199826U true CN216199826U (en) | 2022-04-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202121701207.3U Active CN216199826U (en) | 2021-07-26 | 2021-07-26 | Bearing group applied to power turbine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115143192A (en) * | 2022-04-18 | 2022-10-04 | 中国航发沈阳发动机研究所 | Ball bearing series assembly for realizing axial large thrust |
| CN115949670A (en) * | 2023-03-09 | 2023-04-11 | 中国航发四川燃气涡轮研究院 | Elastic structure for axial compression of bearing |
-
2021
- 2021-07-26 CN CN202121701207.3U patent/CN216199826U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115143192A (en) * | 2022-04-18 | 2022-10-04 | 中国航发沈阳发动机研究所 | Ball bearing series assembly for realizing axial large thrust |
| CN115949670A (en) * | 2023-03-09 | 2023-04-11 | 中国航发四川燃气涡轮研究院 | Elastic structure for axial compression of bearing |
| CN115949670B (en) * | 2023-03-09 | 2023-06-30 | 中国航发四川燃气涡轮研究院 | Elastic structure for axial compression of bearing |
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