CN103967930A - Cylindrical roller bearing with high axial bearing capacity - Google Patents

Abstract

The invention relates to the technical field of rolling bearings, in particular to a cylindrical roller bearing with high axial bearing capacity, which is used for a main cone guiding support of a main reducer of a drive axle of a truck. The cylindrical roller bearing comprises an outer ring, an inner ring, a full complement cylindrical roller clamped between the outer ring and the inner ring, and a flat check ring arranged on one side of the inner ring and one side of the cylindrical roller. Through the improvement of the strength of the retaining sides and the change of the shape of the retaining side at the contact part of the inner ring of the bearing and the end surface of the roller, the shape of the retaining side at the contact part of the outer ring of the bearing and the end surface of the roller, and the shape of the contacted end surface of the roller, the lubricating condition of the contact area of the retaining side of the inner ring of the bearing and the end surface of the roller and the lubricating condition of the contact area of the retaining side of the outer ring of the bearing and the end surface of the roller are improved to form better elastic dynaflow lubricating, so that the axial bearing capacity can be improved greatly, the breakage of the retaining side of the inner ring can be effectively prevented, and the use failure rate of the product can be reduced.

Description

Cylindrical roller bearings with high axial load capacity

technical field

The invention relates to the technical field of rolling bearings, in particular to a cylindrical roller bearing with high axial load capacity that can be used for the main cone guide support of the main reducer of the truck drive axle.

Background technique

At present, cylindrical roller bearings are generally used in the main cone guide support bearings of the main reducer of the drive axle of medium and heavy-duty vehicles, as shown in Figures 1-5. This kind of cylindrical roller bearing mainly bears radial load in design theory, and does not bear axial load. However, in actual use, affected by factors such as the processing and assembly accuracy of related parts, the overload of vehicles, and poor road conditions, cylindrical roller bearings often have to bear large axial loads, resulting in cracking of the ribs of the inner ring of the bearing. , The bearing is damaged, and the related parts are damaged, which seriously affects the driving safety of the vehicle.

Contents of the invention

The purpose of the present invention is to provide a cylindrical roller bearing with high axial load capacity for the main cone guide support of the main reducer of the drive axle of the truck. Shape and roller contact end face shape, improve the lubrication condition of bearing inner and outer ring ribs and roller end face contact area, form better elastohydrodynamic lubrication, thus can greatly improve axial bearing capacity, effectively prevent inner ring rib Crack, reduce the failure rate of product use.

Technical solution of the present invention is as follows:

A cylindrical roller bearing with high axial load capacity, which includes an outer ring, an inner ring, a full complement cylindrical roller sandwiched between the outer ring and the inner ring, and a flat roller on one side of the inner ring and the cylindrical roller. A retaining ring, characterized in that:

On the cross-section of the cylindrical roller bearing cut along the axis, the ribs of the outer ring and the inner ring are slightly convex rib arcs, and the chord line between the two ends of the rib arcs is in line with the The longitudinal sections of cylindrical roller bearings cut along the vertical axis have a rib inclination angle α of 0°15'～0°30', and the arc of the rib and the midpoint of the chord line have a maximum perpendicularity of 2～3μm Distance (also known as convexity);

On the cross-section of the cylindrical roller bearing cut along the axis, the contact position between the end surface of the cylindrical roller and the ribs of the outer ring and the inner ring is a spherical line, and the actual spherical line of the end surface of the cylindrical roller is The radius of curvature is 90% of the theoretically calculated radius of curvature of the spherical line of the roller end surface that is tangent to the arc of the rib (because the convexity of the arc of the rib is very small, it has been approximated as a straight line during calculation, that is, it is equivalent to the chord line) -95%;

The calculation formula for the theoretical calculation of the radius of curvature R of the spherical line of the roller end surface is as follows:

R=(D _we /2-H ₁ )/sinα,

R: Radius of curvature theoretically calculated on the spherical line of the roller end surface;

D _we : effective diameter of cylindrical roller;

H ₁ : The radial distance from the contact point between the end surface of the cylindrical roller and the rib to the surface of the raceway;

α: rib inclination angle.

The actual curvature radius of the spherical line of the end surface of the cylindrical roller is preferably 95% of the theoretically calculated curvature radius R of the spherical line of the roller end surface tangent to the rib arc.

In addition, in order to further increase the strength of the ribs and improve the axial bearing capacity, the above-mentioned technical solution of the present invention is further improved as follows: the overrunning groove is removed between the rib arc of the inner ring and the raceway generatrix of the inner ring, and the It is directly connected (that is, there is no overrun groove between the rib arc of the inner ring and the raceway generatrix of the inner ring).

The inner ring raceway busbar, outer ring raceway busbar and cylindrical roller busbar are in a logarithmic curve convex shape that matches each other;

① The convexity of the logarithmic curve convex shape of the outer ring raceway generatrix is 4-7 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

② The convexity of the logarithmic curve convexity shape of the inner ring raceway generatrix is 4-7 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

③ The logarithmic curve convexity shape of the cylindrical roller generatrix has a convexity of 5-8 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.31ln(1-0.1125×10 ^-3 x-17.22×10 ^-3 x ² +2×10 ^-6 x ³ );

_{Lower limit of} y=-1.445ln (1-0.1125×10 ⁻³ x−17.22×10 ⁻³ x ² +2×10 ⁻⁶ x ³ ).

Compared with the prior art, the present invention has the following advantages:

1. In the cylindrical roller bearing of the present invention, under the condition that the outer dimension of the cylindrical roller bearing does not change the bearing of the prior art, the inner and outer ring ribs of the cylindrical roller bearing are changed from the original straight ribs to slightly convex ribs with a certain inclination angle. Arc-shaped ribs, and the end faces of the rollers in contact with it are changed to spherical surfaces. On the cross-section of the cylindrical roller bearing cut along the axis, the end faces of the cylindrical rollers are in contact with the ribs of the outer ring and the inner ring The contact part of the cylindrical roller is a spherical line, and the actual curvature radius of the spherical line of the end surface of the cylindrical roller is 90%-95% of the theoretically calculated curvature radius of the spherical line of the roller end surface tangent to the arc of the rib, thus improving the inner bearing. , The lubrication condition of the outer ring rib and the contact area of the roller end surface forms better elastohydrodynamic lubrication, which can improve the axial bearing capacity and effectively prevent the inner ring rib from breaking. Compared with the prior art bearing, the present invention can increase the axial bearing capacity by 3 times under the premise of meeting the installation requirements of automobiles.

2. The cylindrical roller bearing of the present invention cancels the original inner ring overtravel groove structure and changes it to a non-overtravel groove structure, thereby increasing the effective width of the rib by 21% (as shown in Figure 4 and Figure 10, the effective width of the rib is given by The 3.3mm in Figure 4 is increased to 4.0mm in Figure 10), which increases the strength of the rib and improves the axial bearing capacity; at the same time, it can eliminate the large stress at the overtravel groove and prevent the bearing from being impacted or collided by external forces. Crack the inner ring rib.

3. The inner ring raceway busbar, the outer ring raceway busbar and the roller busbar of the cylindrical roller bearing of the present invention are changed from the original straight line to a logarithmic curve convex shape that matches each other, so that the "edge stress" can be eliminated, Improve bearing fatigue life.

4. The experiment proves that the use of the cylindrical roller bearing of the present invention reduces the failure rate by 92.6%, and can effectively meet the requirements of users.

Description of drawings

Fig. 1 is a cross-sectional view of a cylindrical roller bearing of the prior art;

Fig. 2 is a diagram of parts of the outer ring of a cylindrical roller bearing in the prior art;

Fig. 3 is a part diagram of the inner ring of the cylindrical roller bearing of the prior art;

Fig. 4 is a partial view of an inner ring rib of a cylindrical roller bearing in the prior art;

Fig. 5 is a cylindrical roller part diagram of a cylindrical roller bearing in the prior art;

Fig. 6 is a sectional view of the cylindrical roller bearing of the present invention;

Fig. 7 is a schematic diagram of the contact between the rib of the inner ring of the cylindrical roller bearing of the present invention and the end face of the cylindrical roller;

Fig. 8 is a part diagram of the outer ring of the cylindrical roller bearing of the present invention;

Fig. 9 is a part diagram of the inner ring of the cylindrical roller bearing of the present invention;

Fig. 10 is a partial view of the rib of the inner ring of the cylindrical roller bearing of the present invention;

Fig. 11 is a cylindrical roller part diagram of the cylindrical roller bearing of the present invention;

Fig. 12 is a schematic diagram of the present invention for calculating the theoretically calculated curvature radius R of the spherical line of the end surface of the roller.

Explanation of symbols in the figure:

1-outer ring, 2-inner ring, 3-cylindrical roller, 4-flat retaining ring;

2-1: The rib arc of the outer ring and inner ring;

2-2: The chord line between the two ends of the rib arc of the outer ring and the inner ring;

3-1: Spherical line of the contact part where the end face of the cylindrical roller contacts the ribs of the outer ring and the inner ring.

Detailed ways

The content of the present invention will be described in detail below in conjunction with the accompanying drawings and specific embodiments of the description:

Example 1

As shown in Figure 6-Figure 11:

A cylindrical roller bearing with high axial load capacity provided by the present invention comprises an outer ring 1, an inner ring 2, a full complement of cylindrical rollers 3 interposed between the outer ring 1 and the inner ring 2, and a The flat retaining ring 4 on the side of the inner ring 2 and the cylindrical roller 3 is characterized in that:

On the cross-section of the cylindrical roller bearing cut along the axis, the ribs of the outer ring 1 and the inner ring 2 are slightly convex rib arcs 2-1, located at the two ends of the rib arcs 2-1 There is a rib inclination angle α of 0°15'～0°30' between the chord line 2-2 and the longitudinal section of the cylindrical roller bearing taken along the vertical axis, and the rib arc line 2- 1 and the midpoint of the string 2-2 have a maximum vertical distance of 2-3 μm (also called convexity);

On the cross-section of the cylindrical roller bearing cut along the axis, the contact position between the end surface of the cylindrical roller 3 and the ribs of the outer ring 1 and inner ring 2 is a spherical line, and the end surface of the cylindrical roller 3 The actual curvature radius of the spherical line is 90%-95% of the theoretically calculated curvature radius of the roller end surface spherical line tangent to the rib arc 2-1; preferably 95%. That is, it is 928mm according to the conventional design, and 881mm can be used for reference now, but the present invention is not limited to this size.

Referring to Fig. 12, the calculation formula for the theoretical calculation of the radius of curvature R of the spherical line of the roller end surface is as follows:

R=(D _we /2-H ₁ )/sinα,

R: Radius of curvature theoretically calculated on the spherical line of the roller end surface;

D _we : effective diameter of cylindrical roller 3;

H ₁ : the radial distance from the contact point between the end surface of the cylindrical roller 3 and the rib to the surface of the raceway;

α: rib inclination angle.

The rib arc 2-1 of the inner ring 2 is directly connected to the raceway generatrix of the inner ring 2, that is, there is no overtravel groove structure between the two.

The 2 raceway busbars of the inner ring, the 1 raceway busbar of the outer ring and the 3rd cylindrical roller busbar are in a logarithmic convex shape that matches each other;

① The convexity of the logarithmic curve convex shape of the outer ring 1 raceway busbar is 4-7 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

② The logarithmic curve convexity shape of the inner ring 2 raceway generatrix has a convexity of 4-7 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ );

③ The convexity of the logarithmic curve convex shape of the 3 generatrices of the cylindrical roller is 5-8 μm, and the logarithmic curve equation is:

y _{upper limit} = -2.31ln(1-0.1125×10 ^-3 x-17.22×10 ^-3 x ² +2×10 ^-6 x ³ );

_{Lower limit of} y=-1.445ln (1-0.1125×10 ⁻³ x−17.22×10 ⁻³ x ² +2×10 ⁻⁶ x ³ ).

The above-mentioned specific implementation is only a detailed explanation of the technical solutions of the present invention, and the present invention is not limited to the above-mentioned embodiments. Those skilled in the art should understand that all improvements and substitutions based on the above-mentioned principles and spirits on the basis of the present invention should be Within the protection scope of the present invention.

Claims (4)

1. A cylindrical roller bearing with high axial load capacity, which includes an outer ring (1), an inner ring (2), and a full complement cylindrical roller bearing sandwiched between the outer ring (1) and the inner ring (2). The child (3) and the flat retaining ring (4) arranged on one side of the inner ring (2) and the cylindrical roller (3) are characterized in that: On the cross-section of the cylindrical roller bearing cut along the axis, the ribs of the outer ring (1) and the inner ring (2) are slightly convex rib arcs (2-1), located on the rib arc The chord line (2-2) between the two ends of the line (2-1) and the longitudinal section of the cylindrical roller bearing cut along the vertical axis have a rib inclination angle of 0°15'～0°30' α, and the rib arc (2-1) has a maximum vertical distance of 2-3 μm from the midpoint of the chord line (2-2); On the cross-section of the cylindrical roller bearing cut along the axis, the contact position between the end surface of the cylindrical roller (3) and the ribs of the outer ring (1) and the inner ring (2) is a spherical line, and the The actual radius of curvature of the spherical line of the end surface of the cylindrical roller (3) is 90%-95% of the theoretically calculated curvature radius of the spherical line of the roller end surface tangent to the rib arc (2-1); The calculation formula for the theoretical calculation of the radius of curvature R of the spherical line of the roller end surface is as follows: R=(D _we /2-H ₁ )/sinα, R: Radius of curvature theoretically calculated on the spherical line of the roller end surface; D _we : the effective diameter of the cylindrical roller (3); H ₁ : the radial distance from the contact point between the end surface of the cylindrical roller (3) and the rib to the surface of the raceway; α: rib inclination angle. 2. The cylindrical roller bearing with high axial load capacity according to claim 1, characterized in that: the actual radius of curvature of the spherical line of the end surface of the cylindrical roller (3) is equal to the rib arc (2-1 ) is 95% of the theoretically calculated curvature radius R of the tangent roller end spherical line. 3. The cylindrical roller bearing with high axial load capacity according to claim 1 or 2, characterized in that: the rib arc (2-1) of the inner ring (2) is the same as that of the inner ring (2) The raceway busbars are directly connected. 4. The cylindrical roller bearing with high axial load capacity according to claim 1 or 2, characterized in that: The raceway generatrix of the inner ring (2), outer ring (1) raceway and cylindrical roller (3) are in a logarithmic convex shape that matches each other; ① The convexity of the logarithmic curve convexity shape of the raceway generatrix of the outer ring (1) is 4-7 μm, and the logarithmic curve equation is: y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ ); y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ ); ② The convexity of the logarithmic curve convexity shape of the raceway generatrix of the inner ring (2) is 4-7 μm, and the logarithmic curve equation is: y _{upper limit} = -2.41ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ ); y _{lower limit} = -1.38ln(1-0.1125×10 ^-3 x-16.8×10 ^-3 x ² +2×10 ^-6 x ³ ); ③ The convexity of the logarithmic curve convex shape of the generatrix of the cylindrical roller (3) is 5-8 μm, and the logarithmic curve equation is: y _{upper limit} = -2.31ln(1-0.1125×10 ^-3 x-17.22×10 ^-3 x ² +2×10 ^-6 x ³ ); _{Lower limit of} y=-1.445ln (1-0.1125×10 ⁻³ x−17.22×10 ⁻³ x ² +2×10 ⁻⁶ x ³ ).