KR20100038916A - Single toroidal(barrel) roller bearing and method for design the same - Google Patents

Abstract

PURPOSE: An insulation spherical roller bearing and a design method thereof are provided to reduce vibration and the generation of heat by using an automatic safety function and an axial displacement function. CONSTITUTION: A design method of an insulation spherical roller bearing comprises following steps. The external diameter(D), inner diameter(d), and width(B) of a bearing is decided. The height difference of the inner circumference of the outer wheel is calculated into rate based on the average diameter of a bearing. The curvature of the inner circumference of the outer wheel is calculated using the height difference of the bearing width and the height difference.

Description

Single-row Spherical Roller Bearing and its Design Method {SINGLE TOROIDAL (BARREL) ROLLER BEARING AND METHOD FOR DESIGN THE SAME}

The present invention relates to a bearing, and more particularly, to a single-row spherical roller bearing having a self-aligning ability and an axial displacement ability is arranged between the outer ring and the inner ring in a thermal insulation, and a design method thereof.

Bearings are classified into sliding bearings and rolling bearings according to the type of friction. Sliding bearings are bearings in which the rotating shaft rotates in surface contact with the bearing. The sliding bearing requires lubrication between the rotating shaft and the bearing, and has greater frictional resistance than rolling bearings, but has the ability to support a load. On the other hand, rolling bearings are characterized in that the rolling elements such as balls or rollers are rotatably disposed between the outer and inner rings, and have a smaller frictional resistance than sliding bearings because they rotate together with the rolling elements while the rotating shaft is coupled to the inner rings. have.

Rolling bearings are composed of raceways, rolling elements, and retainers, and are divided into radial bearings and thrust bearings according to the direction of the load being loaded. The radial bearing has a right angle to the direction of the rotational axis and the load, and the thrust bearing has a parallel direction to the direction of the rotational axis.

In addition, the rolling bearing may be classified into a ball bearing in which the rolling elements are ball-shaped and a roller bearing in which the rolling elements are cylindrical, depending on the type of rolling elements. Among the roller bearings, the rolling elements are in linear contact with the raceways, so that the rolling bearings are larger in rotational friction than the ball bearings in which the rolling elements and the raceways are in point contact.

Such roller bearings may be classified into cylindrical roller bearings, needle roller bearings, tapered roller bearings, and spherical roller bearings. Cylindrical roller bearings are simple bearings in which the cylindrical rollers are in linear contact with the raceways, and are mainly subjected to radial loads and are suitable for relatively high speed rotation. Needle roller bearings have a relatively large radial load capacity because the elongated rollers are in linear contact with the raceway wheels, and the outer circumferential diameter is smaller than that of the rollers. The tapered roller bearing has a conical roller as a rolling element, and can receive an axial load in one direction along with the radial load. The spherical roller bearing uses a barrel-shaped spherical roller as a rolling element, and the raceway surface of the outer ring is also spherical.

Spherical roller bearings are known in which the spherical rollers are insulated and in two rows. Two-row spherical roller bearings are structurally short in spherical roller length and have excellent self-aligning capability, but have low axial displacement capability. On the other hand, the single-row spherical roller bearings are structurally long, so the contact area of the spherical roller is large and the radius of curvature of the raceway surface of the outer ring and the raceway surface of the inner ring is the same. Displacement ability is good. As such, the single-row spherical roller bearings can withstand high loads due to the large contact area of the spherical rollers, and have both the self-aligning ability of the two-row spherical roller bearings and the axial displacement capacity of the cylindrical roller bearings or needle roller bearings. It is advantageous for high speed rotation and can actively cope with the length deformation of the rotating shaft.

By the way, the single-row spherical roller bearing has a spherical surface having the same radius of curvature as the raceway surface of the inner ring and the raceway surface of the outer ring. In addition, in order to have the self-aligning ability and the axial displacement ability, the design is difficult because the inner ring, outer ring, spherical roller must meet structurally specific geometric conditions.

SUMMARY OF THE INVENTION The present invention has been made in view of the above, and provides an insulating spherical roller bearing and a design method thereof capable of satisfying both the conditions required for assembly, and the conditions for having self-aligning ability and axial displacement capability. There is a purpose.

The method of designing a single-sided spherical roller bearing according to one aspect of the present invention for achieving the above object is to design a single-sided spherical roller bearing that can be assembled while having the self-aligning ability and the axial displacement capacity, a) bearing outer diameter ( D) determining the bearing inner diameter d and the bearing width B, b) the ratio of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness (Dd) / 2, R _RD and Assuming a ratio R _RL of the length l _w of the spherical roller to the bearing width B, and c) The height difference Δd of the inner circumferential surface of the outer ring is the bearing average diameter (D + d). Calculation of the ratio at the ratio of / 2), d) using the bearing width (B) and the height difference (Δd) of the outer ring inner peripheral surface to calculate the radius of curvature (R) of the outer ring inner peripheral surface, the spherical roller Calculating a radius of curvature R _w as a magnification with respect to the radius of curvature R of the inner circumferential surface of the outer ring.

Here, after performing step d), the number Z of the plurality of spherical rollers that can be arranged between the outer ring and the inner ring and the interval of arrangement c are calculated, and the calculated result is not appropriate. If not, the ratio after the step b) may be repeated by adjusting the ratio R _RD of the maximum diameter dw _max of the spherical roller to the bearing thickness.

And the ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness can be selected in the range of 0.5 ~ 0.55.

In addition, in step b), the ratio R _RL of the length l _w of the spherical roller to the bearing width B is equal to the sum of the length of the spherical roller and the maximum moving distance that the spherical roller can move. It is preferably assumed to be equal to or less than the bearing width B.

Further, after performing step d), the minimum diameter (dw _min ) of the spherical roller, the maximum diameter (OR _max ) of the outer ring inner peripheral surface, the minimum diameter (OR _min ) of the outer ring inner peripheral surface, the maximum diameter of the inner ring outer peripheral surface (IR _max ), the method may further include calculating a minimum diameter IR _min of the outer circumferential surface of the inner ring.

According to another aspect of the present invention, there is provided a method for designing an insulating spherical roller bearing having an inner ring having an outer ring inner circumferential surface, an inner ring having an inner ring outer circumferential surface having the same radius of curvature as the outer ring inner circumferential surface, and a spherical outer circumferential surface. Designing a single-row spherical roller bearing having a plurality of spherical rollers disposed between the outer ring and the inner ring, a) determining the bearing outer diameter (D), bearing inner diameter (d) and bearing width (B), and b ) Ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness (Dd) / 2 and the ratio (R _w ) of the length (l _w ) of the spherical roller to the bearing width (B). _RL ), c) calculating a height difference Δd of the inner circumferential surface of the outer ring through the following equation,

(Herein, the constant C is a value in the range 8 to 9 × 10 ⁻³ )

d) The curvature radius R of the outer ring inner circumferential surface R is calculated using the bearing width B and the height difference Δd between the outer ring inner circumferential surface, and the curvature radius R _w of the spherical roller is the curvature of the outer ring inner circumferential surface. Calculating a magnification with respect to a radius (R), and e) the minimum diameter (dw _min ) of the spherical roller, the maximum diameter (OR _max ) of the outer ring inner circumferential surface, the minimum diameter (OR _min ) of the outer ring inner circumferential surface, and the inner ring Calculating a maximum diameter IR _{max of an} outer circumferential surface, a minimum diameter IR _min of the outer circumferential surface of the inner ring, and f) the number and placement intervals of the plurality of spherical rollers that may be disposed between the outer ring and the inner ring. Calculating a).

Here, after performing step f), the method may include determining whether the calculation result is appropriate, and if the calculation result is not appropriate, a ratio of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness. It can be adjusted to repeat the step after step b).

Insulating spherical roller bearing according to the present invention for achieving the above object includes the outer ring, the inner ring and the spherical roller having the dimensions derived by the design method of the insulating spherical roller bearing as described above.

The design method of the single-row spherical roller bearing according to the present invention can be easily assembled, the single-sided spherical roller bearing of various sizes having the self-aligning ability and the axial displacement capacity. In addition, when the final result data is judged to be inappropriate, the optimal design data can be obtained by feeding back to the initial stage of the design.

In addition, the single-row spherical roller bearing according to the present invention designed through such a design method has a large contact area of the spherical roller, and can withstand high loads in the radial direction. The vibration generation amount and heat generation amount are small. In addition, the friction heat generation is significantly reduced, the bearing life is significantly increased compared to other bearings.

Hereinafter, with reference to the accompanying drawings will be described a heat insulating spherical roller bearing and a design method according to an embodiment of the present invention. The size or shape of the components shown in the drawings may be exaggerated for clarity and convenience of description.

Referring to FIG. 1, an insulating spherical roller bearing 10 according to an exemplary embodiment of the present invention may include an outer ring 11 having an outer ring inner circumferential surface 11a, which is entirely or partially spherical, and all or a part of the outer ring inner circumferential surface 11a. A plurality of spherical surfaces disposed between the outer ring 11 and the inner ring 12 to rotate in contact with the inner ring 12, outer ring inner circumferential surface 11a and inner ring outer circumferential surface 12a having inner ring outer circumferential surface 12a of the same radius of curvature R. FIG. A roller 13 and a retainer 14 for supporting the plurality of spherical rollers 13 at regular intervals are included. In the plurality of spherical rollers 13, the outer peripheral surface thereof is spherical. As for the spherical roller 13, the radius of curvature R _w of the outer circumferential surface 13a is slightly smaller than the radius of curvature R of the outer ring inner circumferential surface 11a and the inner ring outer circumferential surface 12a, so that the outer ring inner circumferential surface 11a and inner ring outer circumferential surface 12a It can rotate smoothly in contact with the state and can slide on outer ring inner peripheral surface 11a or inner ring outer peripheral surface 12a.

Due to this structural feature, as shown in FIG. 2, when the inner ring 12 is subjected to an external force in the axial direction in the drawing, the inner ring 12 is left to a certain distance along the axial direction (for example, to a length of 10% of the bearing width B). ), It can be moved to the right by a distance (eg up to 10% of the bearing width B). Since the inner ring 12 is movable in this manner, the insulating spherical roller bearing 10 according to the present invention has an axial displacement capability, and can actively cope with the length deformation of the rotation shaft 20 due to heat generated during rotation. The vibration generated by the rotation of the rotary shaft 20 is small.

In addition, as shown in FIG. 3, the inner ring 12 has a predetermined angle (for example, within a range of 0.5 °) in a clockwise direction with respect to the outer ring 11 on the drawing in a state in which the rotating shaft 20 is accommodated, and a counterclockwise direction. Can be rotated at an angle (eg within a range of 0.5 °). Since the inner ring 12 is rotatable with respect to the outer ring 11 as described above, the insulating spherical roller bearing 10 according to the present invention has self-aligning ability, and bearing misalignment generated when the rotating shaft 20 is coupled. Acceptable without any effect on operation.

As described above, the heat insulating spherical roller bearing 10 according to the present invention has a large contact area between the outer ring 11, the inner ring 12, and the spherical roller 13, and can withstand high loads in the radial direction. It has a directional displacement capability, and a small amount of vibration and heat is generated. As such, the insulating spherical roller bearing 10 according to the present invention has a special geometrical condition for the outer ring 11, the inner ring 12, and the spherical roller 13 in order to be assembled while having the self-aligning ability and the axial displacement ability. Is designed to satisfy.

Hereinafter will be described a method of designing a single-sided spherical roller bearing according to an embodiment of the present invention for satisfying such special geometric conditions.

In order to be able to assemble, and to have self-aligning ability and axial displacement capability, the bearing constituent elements have dimensions related to each other in a special relation. Designing a bearing is the process of finding relations for these dimensions and obtaining various structural data, including dimensions. As shown in FIG. 4 and FIG. 5, the design factors to be determined, assumed, or calculated in bearing design include bearing basic data such as bearing outer diameter (D), bearing inner diameter (d), and bearing width (B), and bearings. Assumed data such as the maximum diameter ratio of the roller to thickness (R _RD ), the length ratio of the roller to the bearing width (R _RL ), the maximum roller diameter (dw _max ), the minimum roller diameter (dw _min ), and the roller length (l _w ), data about the spherical roller 13, such as the radius of curvature of the roller (R _w ), the number of rollers (Z), the roller spacing (c), the maximum diameter (OR _max ) of the outer ring inner peripheral surface, the minimum diameter of the outer ring inner peripheral surface ( OR _min ), data on the outer ring 11 such as the height difference (Δd) of the outer ring inner circumferential surface, the radius of curvature R of the outer ring inner circumferential surface, the maximum diameter (IR _max ) of the inner ring outer circumferential surface, and the minimum diameter of the outer ring outer circumferential surface (IR _min ) There is data on the inner ring 12, such as the radius of curvature R of the outer circumferential surface of the inner ring.

These various data can be derived through the input, calculation and analysis process according to the flow chart shown in Figure 6, the specific data derivation process proceeds in the following order.

First, bearing basic data such as bearing outer diameter D, bearing inner diameter d, and bearing width B are determined (S10). These bearing basic data are selected according to DIN616 (ISO15) which defines the bearing outer dimensions, so it is compatible with other bearings. Once the bearing basic data is determined, two assumption data are assumed according to the bearing characteristics and the assembly method (S20). Two hypothesis data are the maximum diameter ratio of the roller (R _RD ) to the bearing thickness and the roller length ratio (R _RL ) to the bearing width. Here, the maximum diameter ratio (R _RD ) of the roller to the bearing thickness is the ratio of the maximum diameter (dw _max ) of the spherical roller (13) to the bearing thickness ((Dd) / 2). The length ratio R _RL of the roller to the bearing width may be represented by the following Equation 2 as a ratio of the length l _w of the spherical roller 13 to the bearing width.

[Equation 1]

[Equation 2]

Here, in the bearing design, the assumption of the maximum diameter ratio R _RD of the roller to the bearing thickness may be repeatedly adjusted by feeding back the final calculated data. By repeatedly executing these assumptions, the appropriate range of assumptions can be found. Applicants have found that proper design results can be obtained when the maximum diameter ratio (R _RD ) of the roller to the bearing thickness is in the range of 0.5 to 0.55. This range may be supported by various design examples described below. However, the maximum diameter ratio R _RD of the roller to the bearing thickness can be selected in various values depending on the characteristics required for the bearing and the assembly method.

The length ratio R _RL of the roller to the bearing width is assumed in consideration of the distance that the inner ring 12 can move in the axial direction. That is, the length ratio R _RL of the spherical roller is assumed so that the sum of the length of the spherical roller 13 and the maximum travel distance that the spherical roller 13 can move is equal to or less than the bearing width B. For example, the inner ring 12 can move along the axial direction to the left by 5% of the bearing width B and to the right by 5% of the bearing width B, so that the maximum travel distance of the spherical roller 13 is reduced. If the width B is 10%, the length of the spherical roller 13 should be 90% or less of the bearing width B, provided that the spherical roller 13 does not protrude to the sides of the outer ring 11 and the inner ring 12. Can move. In addition, when considering the width of the retainer 14, the length of the spherical roller 13 should be at least less than 80% of the bearing width (B). In general, the spherical roller length ratio (R _RL ) is determined within the range of 0.7 to 0.8.

When the assumption about the two hypothesis data is completed, the height difference Δd of the inner circumferential surface of the outer ring is calculated (S30). Here, the height difference Δd of the outer circumferential surface of the outer ring may be represented by a magnification with respect to the bearing average diameter (D + d) / 2 as shown in Equation 3 below.

[Equation 3]

Here, C is a constant to allow the assembly of the bearing while having self-aligning ability and axial displacement capability, and may vary depending on the bearing manufacturer. In general, the constant C is in the range of 8 to 9 × 10 ⁻³ .

Once the height difference Δd of the outer ring inner circumferential surface is calculated, the radius of curvature R of the outer ring inner circumferential surface R, the radius of curvature of the roller R _w , the maximum roller diameter dw _max , the minimum roller diameter dw _min , and the maximum diameter of the outer ring inner circumference OR _max , the minimum diameter OR _{min of the} outer ring inner circumferential surface, the maximum diameter IR _max of the inner ring outer circumferential surface, and the minimum diameter IR _min of the inner ring outer circumferential surface can be calculated (S50).

First, the radius of curvature R of the outer circumferential surface of the outer ring may be calculated through Equation 5 derived through Equations 4-1 and 4-2. Here, Equations 4-1 and 4-2 can be derived through the geometric relationship between the radius of curvature R of the outer ring inner circumferential surface, the bearing width B, and the height difference Δd of the outer ring inner circumferential surface shown in FIG. 7. Can be.

[Equation 4-1]

[Equation 4-2]

Here, by substituting Equation 4-2 into Equation 4-1 and arranging the radius of curvature R of the outer circumferential surface of the outer ring, as shown in Equation 5, the radius of curvature R of the outer circumferential surface of the outer ring is defined as the bearing width B and the outer ring. It can be represented by the height difference Δd of the inner circumferential surface.

[Equation 5]

And the maximum roller diameter (dw _max ) can be calculated through the equation (1).

In addition, the roller minimum diameter dw _min may be calculated through Equation 7 derived through Equations 6-1 to 6-3. Here, Equations 6-1 to 6-3 represent the roller curvature radius R _w , the roller length l _w , the height difference Δd ′ of the outer circumferential surface of the roller, and the maximum roller diameter dw. _max ) can be derived from the geometric relationship.

[Equation 6-1]

[Equation 6-2]

Equation 6-3

Here, by substituting Equation 6-2 into Equation 6-1 and arranging the height difference Δd 'of the outer peripheral surface of the roller, and substituting the summed up equation into Equation 6-3, The roller minimum radius dw _min may be represented by the roller maximum radius dw _max , the roller curvature radius R _w , and the roller length l _w .

[Equation 7]

Here, the radius of curvature R _w of the outer circumferential surface of the roller is calculated at an appropriate magnification with respect to the radius of curvature R of the outer circumferential surface of the outer ring. If the radius of curvature R _w of the outer circumferential surface of the roller is equal to the radius of curvature R of the inner circumferential surface of the outer diameter, the spherical roller 13 cannot slide on the inner circumferential surface 11a of the outer ring, so that the bearing has self-aligning ability and axial displacement capability. It becomes impossible. Therefore, the radius of curvature R _w of the outer circumferential surface of the roller should be smaller than the radius of curvature R of the inner circumferential surface of the outer ring. For example, when the inner ring 12 is allowed to rotate by 0.5 ° clockwise and counterclockwise with respect to the outer ring 11, the radius of curvature R _w of the outer circumferential surface of the roller is 95 of the radius of curvature R of the inner circumferential surface of the outer ring. It may be set to a% size, wherein the radius of curvature R _w of the outer peripheral surface of the roller is 0.95 magnification size of the radius of curvature R of the outer peripheral surface.

In addition, the maximum diameter (OR _max ) of the outer ring inner circumferential surface (OR _max ), the minimum diameter (OR _min ) of the outer ring inner circumferential surface (IR _max ) and the minimum diameter (IR _min ) of the inner ring outer circumferential surface are geometrical features of the bearing shown in FIG. 4. It can be calculated through the following equations (8) to (11) derived from.

[Equation 8]

[Equation 9]

[Equation 10]

[Equation 11]

As such, when various data about the outer ring 11, the inner ring 12, and the spherical roller 13 are calculated, the number of spherical rollers 13 that the outer ring 11 can be accommodated between the inner rings 12 is determined. It calculates (S60). The number Z of acceptable rollers can be represented by the following equation (12).

[Equation 12]

The calculated value calculated through Equation 12 appears as a real number with a value less than or equal to the decimal point. In the calculated real value, the integer represents the number of spherical rollers 13 that can be accommodated between the outer ring 11 and the inner ring 12, and the value below the decimal point is the spacing between the adjacent spherical rollers 13 (c). ).

When the number of spherical rollers 13 that can be accommodated between the outer ring 11 and the inner ring 12 is calculated, it is determined whether the number Z of accommodated rollers and the placement interval c between the rollers are appropriate (S70). . The number of rollers required in the design and the spacing between the rollers (c) may vary depending on the load or function required for the bearings, so if the result is not appropriate, the maximum diameter ratio of the rollers (R _RD ) to the bearing thickness is Assuming again, repeat the data calculation process.

Since the design method of the single-row spherical roller bearing described above can be programmed through various computer software, design modification can be made without difficulty. The following tables show several exemplary bearing designs. Here, Table 1 shows the basic data and the assumption data of the bearing, Table 2 and Table 3 shows the spherical roller 13, the outer ring 11 and the inner ring 12 derived from the data of Table 1 and the above-described bearing design method ) Shows the resulting data. In these design examples, the constant C used to calculate the height difference Δd of the outer ring inner circumferential surface is 8.2927 × 10 ⁻³ .

Bearing Basic Data Household data D (mm) d (mm) B (mm) R _RD R _RL Design Example 1 130.000 75.000 31.000 0.550 0.700 Design Example 2 160.000 75.000 55.000 0.550 0.700 Design Example 3 140.000 80.000 33.000 0.550 0.700 Design Example 4 170.000 80.000 58.000 0.550 0.700 Design Example 5 150.000 85.000 36.000 0.550 0.700 Design Example 6 180.000 85.000 60.000 0.550 0.700 Design Example 7 150.000 90.000 72.000 0.550 0.700 Design Example 8 190.000 90.000 64.000 0.550 0.700

TABLE 1

Spherical Roller Data dw _max dw _min l _w Z R _w Design Example 1 15.125 14.249 21.700 21.290 134.661 Design Example 2 23.375 22.370 38.500 15.792 369.122 Design Example 3 16.500 15.560. 23.100 20.944 142.200 Design Example 4 24.750 23.681 40.600 15.867 385.867 Design Example 5 17.875 16.871 25.200 20.651 158.407 Design Example 6 26.125 24.992 42.000 15.933 389.589 Design Example 7 16.500 15.474 50.400 22.848 619.089 Design Example 8 27.500 26.303 44.800 15.994 419.509

TABLE 2

Paddle data Inner ring data OR max OR min Δd R IR max IR min R Design Example 1 117.625 115.925 0.850 141.748 89.075 87.375 141.748 Design Example 2 140.875 138.926 0.974 388.550 96.074 94.125 388.550 Design Example 3 126.500 124.676 0.912 149.684 95.324 93.500 149.684 Design Example 4 149.750 147.677 1.037 406.176 102.323 100.250 406.176 Design Example 5 135.375 133.426 0.974 166.745 101.574 99.625 166.745 Design Example 6 158.625 156.427 1.099 410.093 108.573 106.375 410.093 Design Example 7 136.500 134.510 0.995 651.673 105.490 103.500 651.673 Design Example 8 167.500 165.178 1.161 441.588 114.822 112.500 441.588

TABLE 3

Looking at the result data for the various design examples above, it can be seen that in Design Example 3, Design Example 6, Design Example 8, the value below the decimal point of the number Z of acceptable rollers is larger than 0.9. This means that the spacing (c) between the spherical rollers 13 disposed between the outer ring 11 and the inner ring 12 is large during bearing manufacture. If the placement interval c of the spherical roller 13 is large, the load capacity of the bearing may be lowered. Therefore, it may be determined that the design data of Design Example 3, Design Example 6, and Design 8 need to be redesigned by adjusting the assumption data.

The derived data are used as basic dimensions of bearing design, and additional design details such as clearance and tolerance of bearings are added to make detailed design for finally manufacturing single-row spherical roller bearings. Can be.

As described above, the design method of the single-row spherical roller bearing according to the present invention can be easily assembled, and the single-sided spherical roller bearing of various sizes having self-aligning ability and axial displacement capability can be easily designed. In addition, when the final result data is judged to be inappropriate, the optimal design data can be obtained by feeding back to the initial stage of the design.

The present invention described above is not limited to the configuration and operation as shown and described. That is, the present invention is capable of various changes and modifications within the spirit and scope of the appended claims.

1 is a perspective view showing a part of the heat insulating spherical roller bearing according to one embodiment of the present invention.

Figure 2 is a side cross-sectional view showing the axial displacement capacity of the insulating spherical roller bearing according to an embodiment of the present invention.

Figure 3 is a side cross-sectional view showing the self-aligning ability of the insulating spherical roller bearing according to an embodiment of the present invention.

4 and 5 are a side cross-sectional view and a front view showing various design factors of the single-sided spherical roller bearing according to an embodiment of the present invention.

Figure 6 is a flow chart showing a process of designing a single row spherical roller bearing according to an embodiment of the present invention.

FIG. 7 is an enlarged side sectional view of a portion of FIG. 4 to obtain a height difference of an inner circumferential surface of an outer ring of an insulating spherical roller bearing according to an embodiment of the present invention.

8 is an enlarged side sectional view showing a part of FIG. 4 in order to obtain a height difference between the outer circumferential surface of the spherical roller bearing of the heat insulating spherical roller bearing according to the embodiment of the present invention;

♣ Explanation of symbols for the main parts of the drawing ♣

10: single row spherical roller bearing 11: outer ring

11a: outer ring inner circumference 12: inner ring

12a: inner ring outer peripheral surface 13: spherical roller

14: retainer 20: axis of rotation

Claims (8)

The design of an insulating spherical roller bearing having an outer ring having a spherical outer ring inner circumferential surface, an inner ring having an inner ring outer circumferential surface of the same radius of curvature as the outer ring inner circumferential surface, and a plurality of spherical rollers having an outer circumferential surface disposed between the outer ring and the inner ring In the method, a) determining a bearing outer diameter (D), a bearing inner diameter (d) and a bearing width (B); b) the ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness (Dd) / 2 and the ratio of the length of the spherical roller (l _w ) to the bearing width (B) ( Assuming R _RL ); c) calculating a height difference Δd of the inner circumferential surface of the outer ring at a magnification with respect to a bearing average diameter (D + d) / 2; d) The curvature radius R of the outer ring inner circumferential surface R is calculated using the bearing width B and the height difference Δd between the outer ring inner circumferential surface, and the curvature radius R _w of the spherical roller is the curvature of the outer ring inner circumferential surface. Calculating a magnification with respect to the radius (R). The method of claim 1, After performing the step d), the number Z of the plurality of spherical rollers that can be disposed between the outer ring and the inner ring and the placement interval c are calculated, and if the calculated result is not appropriate, the bearing And adjusting the ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the thickness and repeating the steps after step b). The method of claim 2, The ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness is a value between 0.5 and 0.55. The method of claim 2, In the step b), the ratio R _RL of the length l _w of the spherical roller to the bearing width B is the sum of the length of the spherical roller and the maximum travel distance that the spherical roller can move. (B) A method of designing a single-row spherical roller bearing, characterized in that it is assumed to be less than. The method of claim 1, After performing step d), the minimum diameter (dw _min ) of the spherical roller, the maximum diameter (OR _max ) of the outer ring inner peripheral surface, the minimum diameter (OR _min ) of the outer ring inner peripheral surface, the maximum diameter of the inner ring outer peripheral surface (IR _max ), calculating the minimum diameter (IR _min ) of the outer peripheral surface of the inner ring further comprising the step of designing a spherical roller bearing. The design of an insulating spherical roller bearing having an outer ring having a spherical outer ring inner circumferential surface, an inner ring having an inner ring outer circumferential surface of the same radius of curvature as the outer ring inner circumferential surface, and a plurality of spherical rollers having an outer circumferential surface disposed between the outer ring and the inner ring In the method, a) determining a bearing outer diameter (D), a bearing inner diameter (d) and a bearing width (B); b) the ratio (R _RD ) of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness (Dd) / 2 and the ratio of the length of the spherical roller (l _w ) to the bearing width (B) ( Assuming R _RL ); c) calculating the height difference Δd of the inner circumferential surface of the outer ring through the following equation;

(Herein, the constant C is a value in the range 8 to 9 × 10 ⁻³ ) d) The curvature radius R of the outer ring inner circumferential surface R is calculated using the bearing width B and the height difference Δd between the outer ring inner circumferential surface, and the curvature radius R _w of the spherical roller is the curvature of the outer ring inner circumferential surface. Calculating the magnification with respect to the radius R; e) minimum diameter (dw _min ) of the spherical roller, maximum diameter (OR _max ) of the outer ring inner peripheral surface, minimum diameter (OR _min ) of the outer ring inner peripheral surface, maximum diameter (IR _max ) of the inner ring outer peripheral surface, the inner ring outer peripheral surface Calculating a minimum diameter IR _{min of} ; and f) calculating the number and placement intervals (c) of the plurality of spherical rollers that can be disposed between the outer ring and the inner ring. The method of claim 6, And after the step f), determining whether the calculation result is appropriate, and if the calculation result is not appropriate, adjusting the ratio of the maximum diameter (dw _max ) of the spherical roller to the bearing thickness. Method of designing a single-row spherical roller bearing, characterized in that to repeat the step after step b). A single-row spherical roller bearing comprising the outer ring, the inner ring and the spherical roller having the dimensions derived from the method for designing the single-row spherical roller bearing according to any one of claims 1 to 7.

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