Inner Ring-Guided Tapered Roller Retainer for Centrifugal Deformation
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Solution Overview
Problem
Tapered roller bearings of the inner ring-guided type face challenges in maintaining retainer durability due to deformation caused by centrifugal forces during revolving motions, leading to increased stress and potential failure.
Innovation Solution
The tapered roller bearing design includes specific dimensions and geometries for the inner ring and retainer, with the retainer having a flanged part and a controlled guide gap, to disperse centrifugal forces and reduce elliptical deformation, thereby enhancing retainer durability.
Engineering Contradictions & Design Principles
Engineering Contradiction Analysis
1Force
If the guide gap between the retainer and inner ring collar parts is large, then the retainer can accommodate centrifugal force, but the clearance between the tapered roller and pocket inner surface closes causing increased wear
Solution Approach 1:
The patent optimizes the guide gap dimension to a specific range (0.05-0.15 times the retainer thickness) to balance two opposing requirements: providing enough clearance for centrifugal force accommodation while maintaining sufficient contact between the tapered roller and pocket inner surface to prevent excessive wear. This parameter optimization resolves the contradiction by finding the optimal dimensional value.
2Device complexity
If the retainer is guided by the inner ring with a small guide region, then the structure is compact, but the contact force becomes concentrated causing elliptical deformation and reduced durability
Solution Approach 1:
The patent specifies that the guide region circumferential size should be at least 0.1 times the retainer inner diameter to distribute contact forces adequately. This parameter setting prevents excessive stress concentration that would cause elliptical deformation, while still maintaining a compact structure. The quantitative guideline resolves the contradiction between compactness and durability.
3Volume of moving object
If the retainer cross section is small, then the bearing is compact, but the retainer experiences higher stress under centrifugal force leading to deformation
Solution Approach 1:
The patent establishes that the retainer thickness should be at least 0.05 times the bearing outer diameter to ensure sufficient strength under centrifugal loading. This dimensional requirement provides adequate stress resistance while maintaining a compact bearing overall size. The quantitative parameter resolves the contradiction between compactness and strength.
Applied Scientific Principles
This section explains which scientific principles are used to turn an abstract innovation direction into a practical engineering solution.
Function Achieved in This Case
This configuration effectively suppresses elliptical deformation and reduces stress on the retainer, leading to improved durability and preventing failure, even under high centrifugal forces.
Implementation Method 1
A centrifugal force FG acts on the entirety of the tapered roller bearing as the tapered roller bearing undergoes a revolving motion
Implementation Method 2
the inner peripheral edge of each flanged part serves as a sliding surface by means of which the retainer is guided by an inner ring
Data Source
AI summary
Provided is a tapered roller bearing which includes an inner ring including a collar part, an outer member having an annular rolling surface in opposition to a rolling surface of the inner ring, tapered rollers interposed between the inner ring and the outer member, and a retainer configured to be guided by the inner ring, retaining the tapered rollers, and including small- and large-diameter-side annular parts, and pillars connecting the small- and large-diameter-side annular parts at more than one circumferential location. At least one of the small-or large-diameter-side annular parts includes an arcuate bent part from the pillars and a flanged part extending radially inwards from the bent part. The bearing satisfies the inequalities 0.50018<(d1/d2)/2<0.5049; and 0.50018<(d1/d2)/2<0.5056X(−00.002) involving the inner diameter of the flanged part d1, the outer diameter of the collar part of the inner ring d2, and the centrifugal acceleration of the revolution of the bearing X.