JP3511782B2 - Rolling bearing - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [0001] BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a roll having a collar.
BACKGROUND OF THE INVENTION The present invention relates to a ball bearing, and more particularly, to reduction of its vibration. [0002] 2. Description of the Related Art Rolling bearings have a small vibration damping ability.
Therefore, in order to suppress vibration of the system including the rolling bearing,
Or put a viscous damper structure in the housing.
Is generally well known. Further, in a rolling bearing having a flange portion, a
From the viewpoint of seizure prevention in
To improve the roughness of the contact area between the collar and the rolling element.
To reduce the frictional resistance at the contact area.
ing. [0004] However, the elastic body
Or a vibrating damper structure
The effect is not sufficient with the motion suppression method, and the structure
Unsolved problem that the application becomes complicated and the scope of application is limited
There is. [0005] In addition, the roughness of the contact surface between the collar portion and the rolling element is reduced.
With this setting, problems such as seizures can be solved, but low vibration
It is also unsolved that the effect on reduction can be counterproductive
Remains. Accordingly, the present invention provides such a prior art.
The focus was on unresolved issues.
In the case of a rolling bearing having
The roughness of at least one of the end faces of the rolling elements in contact with
Specific relationship to inner / outer ring and rolling surface roughness of rolling elements
Is determined so that the vibration level of the rolling bearing
The purpose is to reduce the cost. [0007] According to a first aspect of the present invention, there is provided:
The invention relates to a rolling bearing having a flange surface,
At least one of the end faces of the rolling element in contact with the surface or collar
Of the inner and outer raceway surfaces and rolling elements
It has the following relationship with the surface roughness. 2 (σ₁ ^Two+ Σ_Two ^Two)^1/2<(Σ_Three ^Two+ Σ_Four ^Two)^1/2<4 (σ
₁ ^Two+ Σ_Two ^Two)^1/2 Where σ₁; Inner / outer ring raceway surface roughness (center line average roughness)
Sa) σ_Two; Track surface roughness of rolling elements σ_Three; Inner / outer ring collar roughness σ_Four; Rolling element end surface roughness Vibration (for example, radial vibration)
Rolling), the rolling element that is normally in contact with the collar surface
Friction occurs between the rim and the collar surface. According to the present invention,
The roughened contact area increases the damping effect
To effectively attenuate vibrations. [0008] BRIEF DESCRIPTION OF THE DRAWINGS FIG.
This will be described with reference to FIG. FIG. 1 shows the outer ring mounted on the drive shaft 1.
Above cylindrical roller bearing (NU type) 2 with double flange
It is a half sectional view and the explanatory outline figure of the vibration measurement. The inner race 3 is fitted and fixed to the drive shaft 1.
The outer race 4 has two flange surfaces 4a, 4a. Rolling element 5
The end faces 5a, 5a of the head are
a, 4a. 6 is a retainer. In this cylindrical roller bearing 2, the roughness is partially
Examples 1 and Comparative Example 1 and Comparative Example
2 was subjected to a vibration test, and the results were compared. Test method
The method is as follows. A sample cylindrical roller bearing (model number N
U218) and add # 60 spindle oil at room temperature
Rotate at 1800 rpm with a motor (not shown) while lubricating
Turned over. The vibration level at that time is applied to the outer diameter of the outer ring 4.
Measured with attached acceleration pickup 7, vibration spectrum
Recorded. [0012] Each component of each sample of the embodiment and the comparative example
Table 1 shows the surface roughness (center line average roughness; μm Ra). table
1, σ₁Are the raceway surfaces 3R and 4R of the inner ring 3 and the outer ring 4
Surface roughness, σ_TwoSurface roughness of rolling surface 5b of roller 5, σ_ThreeIs
Surface roughness of rim surface 4a of outer ring 4, σ_FourEnd face of roller 5
The surface roughness is 5a. [0013] [Table 1] For each sample, the inner and outer raceway surfaces 3R, 4R
And the surface roughness of the rolling surfaces 5b of the rollers are all the same (σ₁= Σ_Two
= 0.05μmRa), and the surface roughness of the flange surface 4a of the outer ring
σ_ThreeAnd the surface roughness σ of the head end face 5a at the time of contact with this_Four
And changed each. The surface roughness σ of the flange surface_ThreeAnd roller head
Surface roughness of the end face σ_Four(Hereinafter, collectively, "roller-brim contact
Surface roughness "σ_Three, Σ_FourThe following three, depending on the degree of
Of cases. Case 1 (Example): Roller / rim contact surface roughness
Sa_Three, Σ_FourIs the surface roughness σ of each raceway surface of the inner and outer rings.₁as well as
Roller contact surface roughness σ_Two(Hereafter, collectively, "race surface
Roughness ”σ₁, Σ_TwoAbout 2 times worse than
group. The degree of roughness is 2 (σ ₁ ^Two+ Σ_Two ^Two)^1/2Expressed by Case 2 (Comparative Example): Roller / rim contact surface roughness
Sa_Three, Σ_FourWith the race surface roughness σ₁σ_TwoAbout 4 times worse than
Comb bearing group. The degree of roughness is 4 (σ₁ ^Two+ Σ_Two ^Two)
^1/2Expressed by Case 3 (Comparative Example): Roller / rim contact surface roughness
Sa_Three, Σ_FourThere are good bearing groups. Roughness degree (σ_Three
^Two+ Σ_Four ^Two)^1/2Expressed by FIG. 2 shows the vibration spectrum.
The measurement results are shown. Roller / collar contact surface roughness σ_Three, Σ_FourGood ratio of
In case 3 of the comparative example, when vibration occurs in the drive shaft 1,
The vibration level at the outer diameter portion of the outer ring 4 is high. Especially human
4kHz, which is the frequency that ears feel most uncomfortable
Become. In comparison with this, the roller / collar contact surface roughness σ_Three, Σ_Four
However, in case 1 of the rougher embodiment, the vibration level is low.
However, roller and collar contact surface roughness σ_Three, Σ_FourWorse
In case 2 of the comparative example, the vibration was reduced as much as case 1.
No decay effect is seen, rather frequency band of 0-10kHz
It is high throughout. The reason will be discussed with reference to FIG.
You. On the vertical axis, at a frequency of 4 kHz measured at the outer diameter of the outer ring
And the horizontal axis represents (σ_Three ^Two+ Σ_Four ^Two)^1/2of
(Σ₁ ^Two+ Σ_Two ^Two)^1/2Take the value of the ratio to
The values for each sample were plotted. (Σ₁ ^Two+ Σ_Two ^Two)^1/2
Is the race surface (with the raceway at each raceway surface of the inner and outer rings)
Is the roughness factor that determines the oil film parameter between
Since this is a factor that indicates the lubrication state of the moving surface,
And roller contact surface roughness (σ_Three ^Two+ Σ_Four ^Two)^1/2Rate
I do. As is apparent from FIG. 3, case 3
All the values of the ratio are in the range below 2 and the vibration level
Is at a high level of several tens dB to tens of dB. The reason
The reasons are as follows. Oscillating inner ring 3 generated by drive shaft 1
It is transmitted to the outer ring 4 through the rollers 5,
Relative to vibration due to vibration at head end face 5a and brim face 4a of outer ring 4
Movement occurs. Normally, roller 5 contacts outer ring flange surface 4a
So that the relative movement between the two causes friction at the contact
appear. Therefore, this friction should be increased,
Contact surface roughness σ_Three, Σ_FourVibration damping effect
It is possible to attenuate the vibration by increasing the
In roller 3, the roller / collar contact surface roughness is good and its degree (σ_Three
^Two+ Σ_Four ^Two)^1/2Is small, so there is no vibration damping effect
by. On the other hand, in case 2, all of the ratio values are 4
And the vibration level is the same as Case 3.
It is at a high level of several tens dB to tens dB. The reason
Is the degree of roughness of the roller / collar contact surface (σ_Three ^Two+ Σ_Four ^Two)^1/2
Is too large, for example, the flange face 4a and the head end face 5
The seizure with a occurs and slips between the three inner rings
Vibration (noise) of the bearing itself increases, or
Abnormal wear of the flange surface 4a and the head end surface 5a increases.
The result is a higher vibration level
You. On the other hand, in case 1 of the embodiment,
If the value of the ratio is in the range of 2 to 4,
The bell is as low as less than 10 dB. Roller / Brim connection
Contact surface roughness is appropriate, and this is
Acts as a kind of brake on vibrations in different directions to reduce vibration
Probably due to playing. Here, the value of the ratio is
When the vibration level is within the range of 2.25 to 3.75, the vibration level is reduced.
It can be suppressed to a very preferable level of about 10 dB or less.
It is possible. Table 2 is shown in Table 1 based on the results of FIG.
Surface roughness (center line average roughness) of each component₁~ Σ_Four
Of the race surface roughness, ie, twice and four times, that is, 2 times
(Σ₁ ^Two + Σ_Two ^Two)^1/2And 4 (σ₁ ^Two+ Σ_Two ^Two)^1/2And this
Degree of contact surface roughness between filter and brim (σ _Three ^Two+ Σ_Four ^Two)^1/2And each
Calculated for each case, outside the bearing outer ring at a frequency of 4 kHz
It shows the relationship between the diameter and the vibration level. [0025] [Table 2] Based on the above results, the rolling shaft of the present invention
In the case of the bearing, the degree of the roller / collar contact surface roughness (σ_Three ^Two+
σ_Four ^Two)^1/2And degree of race surface roughness (σ₁ ^Two+ Σ_Two ^Two)^1/2
Is defined as the following equation (1), and the vibration
Reduction could be achieved. 2 (σ₁ ^Two+ Σ_Two ^Two)^1/2<(Σ_Three ^Two+ Σ_Four ^Two)^1/2<4 (σ₁ ^Two+ Σ_Two ^Two)^1/2                                                             ...... (1) In addition, the surface roughness of each raceway surface 3R and 4R of the inner ring 3 and the outer ring 4
Sa₁And the surface roughness σ of the rolling surface 5b of the roller 5_TwoDue to the influence of
Can be expected to have a vibration damping effect, but
Roller / rim contact surface roughness σ_Three, Σ_FourThe big effect is
Could not be obtained. In the above embodiment, the inner and outer ring collars are used.
Surface roughness σ_Three And roller head (end face) roughness σ_FourAbout both
And inner and outer race surface roughness σ₁And rolling elements
Surface roughness σ_TwoAbout two to four times coarser
However, the present invention is not limited to this._ThreeOr σ_FourOne of
It may be rough. In the above embodiment, the cylindrical roller bearing is used.
But other collars such as tapered roller bearings
It can also be applied to various rolling bearings having [0029] As described above, as described above, the rolling of the present invention
According to the bearing, the end of the rolling element in contact with the collar surface or collar
Surface roughness of at least one of the inner and outer raceway surfaces
And within the specified range for the roughness of the rolling surface of the rolling element.
As a result, bearing vibration such as radial vibration occurs
Friction occurs at the contact between the flange surface and the end surface of the rolling element.
This produces the effect of damping vibrations.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view of the upper half of a cylindrical roller bearing with outer ring double flanges and a schematic diagram for explaining vibration measurement thereof. FIG. 2 is a graph showing a measurement result of a vibration spectrum in FIG. FIG. 3 is a graph showing a relationship between a vibration level and a flange contact surface roughness. [Description of Signs] 1 Drive shaft 2 Rolling bearing 3 Inner ring 3R Track surface 4 Outer ring 4a Collar surface 4R Track surface 5 Rolling element 5a End face 5b Rolling face 6 Cage

Continuation of the front page (56) References JP-A-6-241235 (JP, A) JP-A-6-109021 (JP, A) JP-A-5-42754 (JP, U) JP-A-5-75520 (JP , U) (58) Fields surveyed (Int. Cl. ⁷ , DB name) F16C 19/22-19/28 F16C 19/44-19/48 F16C 33/34-33/36 F16C 33/58-33 / 64

Claims (1)

(57) [Claim 1] In a rolling bearing having a flange surface, at least one surface roughness of the flange surface or the end surface of the rolling element in contact with the collar is such that the inner and outer raceway surfaces and A rolling bearing having the following relationship with the roughness of a rolling surface of a rolling element. 2 (σ ₁ ² + σ ₂ ² ) ^1/2 <(σ ₃ ² + σ ₄ ² ) ^1/2 <4 (σ
₁ ² + σ ₂ ² ) ^1/2 where σ ₁ ; inner and outer raceway surface roughness (center line average roughness) σ ₂ ; rolling element raceway surface roughness σ ₃ ; inner and outer ring flange surface σ ₄ ; Rolling element end surface roughness