Deep Groove Ball Bearings
Deep Groove Ball Bearings
We are Manufacturer, Supplier, Developer, Service Provider of Deep Groove Ball Bearings, Single Row Deep Groove Ball Bearings, Ball Bearings, Bearings and our set up is situated in Kolhapur, Maharashtra, India.
Deep groove ball bearings are manufactured in a varied range, both of standard design and various constructive versions.
Deep groove ball bearings can take double direction radial and axial loads and also allow good operation at high speeds.
For these reasons, they can be widely used. Therefor, single row deep_groove_ball_bearings are manufactured in many constructive versions as shown below
Besides deep_groove_ball_bearings of basic design, bearings with UG design, with grooves on the outer ring and WL design, with grooves on both rings are also used for the purpose of mounting seals or shields on bearings, 2ZR, 2RSR or 2RS type, as shown in the bellow figure.
Sealed and shielded deep groove ball bearings
manufactures two versions of sealed and shielded bearings, namely:
bearings RS and Z type, with recess on the inner ring for sealing or shielding;
bearings RSR and ZR type, when shielding and sealing respectively are done directly on the outside surface of the inner ring;
In case of bearings with non-rubbing shields, there is a small interstice between the shield and the rib of the inner ring; in case of bearings with seals, the gasoline and oil resistant elastic rubber lip rubs on the groove on the inner ring side or directly on the outside surface.
Bearings sealed and shielded on both sides manufactured in series are delivered filled with lithium base grease and are used at temperatures between -30?C and + 110?C, in accordance with the specifications in chapter 5. Bearings can also be greased with special greases, relubrication not being necessary. Washing or heating are not allowed before bearing mounting in the assembly.
Bearings with shields have been designed first of all for cases when the inner ring rotates.
When the outer ring rotates, the lubricant can flow out of the bearing at a certain speed. In such cases, we recommend you to consult our experts.
Deep groove ball bearings with snap ring groove
Deep groove ball bearings, with snap ring groove on the outer ring can be located in the housing with snap rings.
Because of their simple and space saving mounting, these bearings simplify the assembly design. The groove for the snap ring and the snap rings are in accordance with ISO 464 and tables 7 and 8 respectively.
Paired deep groove ball bearings
If the basic load of a single bearing is inadequate or the shaft has to be axially located in both directions with a certain clearance, paired deep groove ball bearings are recommended to be used.
These bearings can be delivered matched in pairs in three versions, as follows: DT (tandem arrangement), DB (back-to-back arrangement) or DF (face-to-face arrangement). They can be delivered with axial clearance or preloaded. The values of clearance or preload are given in table 2.
The producer marks “V” on the bearing outside surface as shown in the next figure, so that paired bearings to be correctly mounted.
The speed limit of these bearings can be calculated multiplying the speed of the basic bearing by 0,8.
Paired bearings are packed and delivered in the same box.
Stainless steel deep groove ball bearings
Deep groove ball bearings can be made and constructive version of stainless steel.
The overall dimensions of deep groove ball bearings are in accordance with the stipulations of ISO 15.
Deep groove ball bearings have limited abilities to compensate for bearing errors of alignment. The permissible misalignment between the outer ring and the inner ring, which will not produce inadmissible high additional loads in the bearing, depends on the bearing size, operational radial clearance, inner bearing design and also on the magnitude of loads and moments acting upon the bearing.
Because of the complex relationship of these influence factors, definite and universally valid values of permissible misalignment cannot be determined.
Considering the above mentioned factors, under normal operation conditions the permissible misalignments are between 2 and 10 minutes of arc, depending on the bearing series and load.
It should be considered that misalignments of bearing rings in operation produce a considerably higher noise.
Deep groove ball bearings are generally manufactured to the normal tolerance class P0.
At request, they can also be manufactured to the tolerance classes P6, P5 or P4.
The values of tolerances are given in chapter 3 on page 24.
Radial and axial clearance
Deep groove ball bearings are generally manufactured with normal radial clearance. At request, they can also be manufactured with radial clearance different from the normal one, according to ISO 5753. The values of radial clearance are given in table 1.
Paired bearings can be manufactured with axial clearance (suffix A) or preloaded (suffix L). Values for axial clearance and preload are given in table 2.
If a certain axial clearance is prescribed, this has to be measured and marked on the bearing by “A”, followed by clearance actual value.
Deep groove ball bearings are generally fitted with cages of pressed steel sheet.
Cages of glass fibre reinforced polyamide 6.6 are also suitable if the operating temperature doesn’t exceed + 120 0C. They have reduced weight, low coefficient of friction and are noiseless in operation. Large-sized bearings are fitted with machined brass cages.
Cage design and some technical data are given in table 3.
Bearing minimum radial load
A minimum load must be applied on a deep groove ball bearing so that they can operate correctly, especially in case of operating under heavy loads.
The forces of inertia which occur in bearing as well as the friction in lubricant influence negatively the operating conditions and can cause detrimental sliding movements between balls and raceways.
Minimum radial load depends on the bearing size, speed and lubricant viscosity at operating temperature. It can be roughly calculated from the equation:
Frmin= 0,01 Cr, (Cr = basic dynamic radial load).
Equivalent dynamic radial load
Deep groove ball bearings can take also radial and axial combined loads.
For deep groove ball bearings, single or paired in tandem arrangement DT, equivalent dynamic radial load can be calculated using the equation:
Pr = Fr,kN, when Fa/Fr <= e
Pr = XFr + YFa, kN, when Fa/Fr > e
The greater the axial load, the greater the contact angle of these bearings.
Factors e, Xand Ydepend on the ratio f0Fa/C0r- Factor fo can be determined using the diagram in the bellow figure, as a function of dimension series and mean diameter (d+ D)/2. Fa is the axial load and Coristhestaticbasicloadofthe bearing.
The values of factors e, X, Y which depend on the bearing clearance can be determined from table 4, corresponding to the values of the ratio f0Fa/C0r- The values in table 4 apply to bearings mounted with normal fit, i.e. shafts manufactured to tolerance class j5 or k5 and housing in J6, respectively.
For bearings matched in DB or DT arrangement, equivalent dynamic radial load can be calculated using the equation:
Pr = Fr + Y1Fa , kN, when Fa/Fr <=e
Pr = 0,75Fr + Y2Fa, kN, when Fa/Fr > e
The values of factors e, Yi and Y2, as functions of ratio Fa/C0r are given in table 5.
Equivalent static radial load
For deep groove ball bearings, single or matched in tandem (DT), equivalent static radial load can be calculated using the equations:
P0 = Fr,kN, when Fa/Fr <= 0,8
P0 = 0,6Fr + 0,5Fa, kN, when Fa/Fr > 0,8
For bearings matched in DB or DF arrangement, it can be calculated from:
P0 = Fr + 1,7Fa, kN
If deep groove ball bearings are purely axial loaded, the axial load should not exceed 0,5 Cor- In case of small-sized bearings and bearings of light series (diameter series 8, 9, 0 and 1), the axial load should not exceed 0,25 C0r.
Heavy axial loads cause a significant decrease of bearing rating life. In such cases, we recommend you to consult our experts.
For a proper location of bearing rings on the shaft shoulder and housing shoulder, respectively, maximum shaft (housing) connection radius ru max should be less than minimum bearing mounting chamfer rs min.
The shoulder should have the proper height corresponding to maximum bearing mounting chamfer.
The values of the connection radius (ru) and support shoulder height (hu) as functions of mounting chamfers are given in table 6.