CN202209352U

CN202209352U - Structurally-improved durable tapered roller bearing

Info

Publication number: CN202209352U
Application number: CN2011202822464U
Authority: CN
Inventors: 陈其南; 陈德富; 章志慧
Original assignee: Fujian Yongan Bearing Co Ltd
Current assignee: Fujian Yongan Bearing Co Ltd
Priority date: 2011-08-05
Filing date: 2011-08-05
Publication date: 2012-05-02
Anticipated expiration: 2021-08-05

Abstract

The utility model relates to a structurally-improved durable tapered roller bearing which comprises an outer ring, an inner ring, rollers and a holding rack, and is characterized in that an inner ring rolling path bus, an outer ring rolling path bus and roller buses are in logarithmic curve convexity shapes which are matched each other. In the utility model, through improving the stress distribution on the contact surface between the rollers and the outer ring rolling path, as well as that between the rollers and the inner ring rolling path, the edge stress can be eliminated and the bearing fatigue life can be prolonged. Besides, through enlarging the width of the large retaining side root segment of the inner ring and a bearing contact angle, the axial bearing capacity is improved, and the problem that the bearing is damaged under the high-torque and high-axial-load working conditions is solved. Therefore, the bearing provided by the utility model can meet the requirements of the main gear of the drive axle main reducer of an introduced 8-ton goods wagon.

Description

The long lifetime tapered roller bearing of structure optimization

Technical field

the utility model relates to technical field of rolling bearings, particularly a kind of long lifetime tapered roller bearing that is used for the structure optimization on the automobile drive axle main cone.

Background technique

In the new eight tons of cargo vehicle ransaxles introducing of domestic certain vehicle bridge factory, the tapered roller bearing on its main cone (universal product 72212C/72487) is former to be external steel for carburizing bearing.This vehicle bridge for reducing cost by a relatively large margin, requires to select for use the GCr15 bearing steel material in the production domesticization process of introducing redevelopment.Simultaneously, for adapting to the operating mode of ubiquitous overload of domestic cargo vehicle and road conditions difference, require when doing the vehicle bridge stand test, to adopt the output test moment of torsion that surpasses rated torque 20%: 15000N.m; Bearing life is qualified to require 500,000 commentaries on classics.

Yet the general bearing that employing GCr15 steel is made is in stand test, and the bearing operation that has changes just because of large-flange breaks less than 300,000, causes bearing to lose efficacy in advance; The bearing operation that has changes with regard to fatigue failure less than 500,000.Through analyzing: under the effect of high test torque, the main cone tapered roller bearing bears sizable thrust load, and the bearing toughness that adopts the GCr15 steel to make is lower than the steel for carburizing bearing, causes large-flange to break, and bearing lost efficacy in advance.Equally, under the effect of high test torque, impel bearing fatigue to destroy and accelerate, the life-span reduces.

Summary of the invention

The purpose of the utility model provides a kind of long lifetime tapered roller bearing of structure optimization, and it is through improving the stress distribution between roller and inner ring raceway and the outer ring raceway surface of contact, thereby can eliminate edge stress, improves bearing fatigue life.

The utility model technological scheme is to constitute like this: a kind of long lifetime tapered roller bearing of structure optimization; It comprises outer ring, inner ring, roller and retainer, it is characterized in that: said inner ring raceway bus, outer ring raceway bus and roller bus are the logarithmic curve protuberance shape of mutual coupling.

In the utility model technique scheme; 1. total convexity amount of the logarithmic curve protuberance shape of inner ring raceway bus be 9～12 ; Raceway bus intermediate portion 70% length convexity amount be 1.5～2

, the logarithmic curve equation is:

2. total convexity amount of the logarithmic curve protuberance shape of outer ring raceway bus be 6.5～9 ; Raceway bus intermediate portion 70% length convexity amount be 1.45～2

, the logarithmic curve equation is:

3. total convexity amount of the logarithmic curve protuberance shape of roller bus be 6.5～9

; Roller bus intermediate portion 70% length convexity amount be 1.45～2 , the logarithmic curve equation is:

[0007]In addition, the utility model technique scheme has also been done following improvement:

In order to improve the axial carrying capacity of bearing, the large-flange root width of inner ring increases to 6.48mm, through strengthening the large-flange root width of inner ring, can increase rib intensity, improves axial carrying capacity, prevents that large-flange from breaking.

In order further to improve the axial carrying capacity of bearing, bearing contact angle adds greatly 28 ° 48 ' 39 ".

In order to remedy because of bearing contact angle strengthens and the decline of the load rating that roller bus projected length reduces to cause, guarantee that load rating is not less than former design load, roller 3 enlarged diameter are 17.808mm, and the structural parameter of corresponding other part of optimization.

Compared to prior art, the utlity model has following beneficial effect:

(1) the utility model is changed into inner ring raceway, outer ring raceway and roller bus the logarithmic curve shape and is adopted best convex value by original straight line; Thereby can provide optimum stress to distribute at roller and raceway surface of contact; Eliminate " edge stress ", improve bearing fatigue life;

(2) the utility model can increase rib intensity through strengthening inner ring large-flange root width, improves axial carrying capacity, prevents that large-flange from breaking; Compare with former general bearing, rib intensity improves 8.54%;

(3) the utility model can further improve axial carrying capacity through strengthening bearing contact angle; Compare with former general bearing, the bearing axial carrying capacity improves 9.13%.

(4) the utility model can guarantee that through indoor design parameters such as optimization roller diameters rated load is not less than former design load.

(5) owing to have above-mentioned advantage; Make that the bearing of the utility model can be under the prerequisite that adopts the boundary dimension identical with former general bearing with the installation requirement that satisfies automobile; Adopt homemade GCr15 steel to make; Thereby both reduced production costs, effectively solved the damage of bearings problem under high moment of torsion and high thrust load operating mode again, adapted to the needs of eight tons of cargo vehicle ransaxle main reducing gear master teeth introducing.The bearing that the utility model is made is through the center stand strenuous test of national car mass supervision and inspection, and the life-span reaches 55.7 ten thousand commentaries on classics, surpasses the requirement of life-span 500,000 commentaries on classics of user's proposition.

Description of drawings

Fig. 1 is the sectional view of the general bearing tapered roller bearing of prior art.

Fig. 2 is the common shaft bearing outer-ring parts drawing of prior art.

Fig. 3 is the general bearing inner race parts drawing of prior art.

Fig. 4 is the common shaft bearing roller parts drawing of prior art.

Fig. 5 is the bearing sectional view of the utility model.

Fig. 6 is the bearing outer ring parts drawing of the utility model.

Fig. 7 is the bearing inner race parts drawing of the utility model.

Fig. 8 is the bearing roller parts drawing of the utility model.

Label declaration among the figure: 1-outer ring, 2-inner ring, 3-roller, 4-retainer.

Embodiment

Below in conjunction with Figure of description and embodiment the utility model is described further:

Like Fig. 1-shown in Figure 4 is the general tapered roller bearing schematic representation of existing technology.

Embodiment's schematic representation of the long lifetime tapered roller bearing of the structure optimization that provides for the utility model like Fig. 5-shown in Figure 6, it comprises outer ring 1, inner ring 2, be located in and play a supportive role between outer ring 1 and the inner ring 2 and realize counterrotating a plurality of roller 3 and separate and the retainer 4 of guide rolls motion.

Compare with the corresponding part of existing technology, the utlity model has following improvements:

One, said inner ring 2 raceway buses, outer ring 1 raceway bus and roller 3 buses are the logarithmic curve protuberance shape of mutual coupling.

Wherein, 1. total convexity amount of the logarithmic curve protuberance shape of inner ring 2 raceway buses be 9～12 ; Raceway bus intermediate portion 70% length convexity amount be 1.5～2 , the logarithmic curve equation is:

2. total convexity amount of the logarithmic curve protuberance shape of outer ring 1 raceway bus be 6.5～9

; Raceway bus intermediate portion 70% length convexity amount be 1.45～2

, the logarithmic curve equation is:

3. total convexity amount of the logarithmic curve protuberance shape of roller 3 buses be 6.5～9

; Roller bus intermediate portion 70% length convexity amount be 1.45～2

, the logarithmic curve equation is:

[0025] Inner ring 2 raceway buses, outer ring 1 raceway bus and roller 3 buses linearly (like Fig. 1-shown in Figure 4) in the existing technology; And in the utility model; Inner ring 2 raceway buses, outer ring 1 raceway bus and roller 3 buses adopt the logarithmic curve protuberance shape of coupling each other and best convex value (like Fig. 5-shown in Figure 8); Provide optimum stress to distribute at roller 3 and inner ring 2 raceways and outer ring 1 raceway surface of contact; Thereby effectively eliminate " edge stress ", improve bearing fatigue life.

That two, the large-flange root width of inner ring 2 increases Fig. 7 by the 5.54mm of Fig. 3 be 6.48mm, raising rib intensity 8.54%, thus improved axial carrying capacity, prevent that large-flange from breaking.

Three, bearing contact angle is added 28 ° 48 ' 39 of Fig. 6 greatly by 26 ° 10 ' of Fig. 2 ", the bearing axial carrying capacity improves 9.13%.

Four, roller 3 diameters add the greatly 17.808mm of Fig. 8 by the 16.998mm of Fig. 4, remedy because of bearing contact angle strengthens and the decline of the load rating that roller bus projected length reduces to cause, and guarantee that load rating is not less than former design load.

Five, 1 raceway little internal diameter in outer ring is changed into the Φ 88.685mm of Fig. 6 by the Φ 88.386mm of Fig. 2, and inner ring 2 raceway maximum diameters are changed into the Φ 81.183mm of Fig. 7 by the Φ 81.017mm of Fig. 3.In addition, the structural parameter of other part are all done corresponding change.

Six, the identical and rated load of the boundary dimension of the long lifetime tapered roller bearing of the described structure optimization of the utility model and former general bearing is not less than the primary standard design load, has satisfied the installation requirement of automobile.

Claims

1. the long lifetime tapered roller bearing of a structure optimization; It comprises outer ring (1), inner ring (2), roller (3) and retainer (4), it is characterized in that: said inner ring (2) raceway bus, outer ring (1) raceway bus and roller (3) bus are the logarithmic curve protuberance shape of mutual coupling.

2. the long lifetime tapered roller bearing of structure optimization according to claim 1 is characterized in that:

1. total convexity amount of the logarithmic curve protuberance shape of inner ring (2) raceway bus be 9～12

; Raceway bus intermediate portion 70% length convexity amount be 1.5～2

, the logarithmic curve equation is:

2. total convexity amount of the logarithmic curve protuberance shape of outer ring (1) raceway bus be 6.5～9

; Raceway bus intermediate portion 70% length convexity amount be 1.45～2

, the logarithmic curve equation is:

3. total convexity amount of the logarithmic curve protuberance shape of roller (3) bus be 6.5～9

; Roller bus intermediate portion 70% length convexity amount be 1.45～2

, the logarithmic curve equation is:

。

3. the long lifetime tapered roller bearing of structure optimization according to claim 2, it is characterized in that: the large-flange root width of inner ring (2) is 6.48mm.

4. the long lifetime tapered roller bearing of structure optimization according to claim 2, it is characterized in that: bearing contact angle is 28 ° 48 ' 39 ".

5. the long lifetime tapered roller bearing of structure optimization according to claim 2, it is characterized in that: roller (3) diameter is 17.808mm.

6. the long lifetime tapered roller bearing of structure optimization according to claim 2, it is characterized in that: raceway little internal diameter in outer ring (1) is 88.685mm, inner ring (2) raceway maximum diameter is 81.183mm.