JP2009192049A - Nonseparable angular contact ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a nonseparable angular contact ball bearing which is low in heating temperature during assembling, is easy in operation, causes no damage of a ball during assembling, keeps the outer ring or the inner ring not separated during handling, and also is long in bearing life during use. <P>SOLUTION: The nonseparable angular contact ball bearing 1 comprises suitably setting an upper and a lower limit values of a hanging allowance in response to a radius of a circumscribed circle in which a ball is arranged when the ball 4 is moved to the inner ring 3 or a maximum radius of a truck surface of the outer ring 2, (heating temperature of outer ring-room temperature during assembling), a coefficient of thermal expansion of a material of the outer ring, and a clearance inside a radial. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

The present invention relates to a non-separable angular contact ball bearing that is assembled by assembling a ball between an inner ring and an outer ring by heating an outer ring, and more particularly to a non-separable angular contact ball bearing with a specified allowance.

Angular contact ball bearings are angular contact type radial bearings that use balls as rolling elements, and at least one of the inner ring and outer ring that make up the angular contact, the one side in the axial direction of the shoulder adjacent to the raceway surface is scraped and counter A bore is formed (see, for example, Patent Document 1).
In the non-separable angular contact ball bearing, the dimension of the allowance (hereinafter, a value corresponding to the radius) is set. Specifically, in the case of a non-separable angular contact ball bearing with a counter bore formed on the outer ring, the difference between the radius of the circumscribed circle where the balls are arranged and the minimum radius of the counter bore of the outer ring when the ball is brought close to the inner ring In the case of a non-separable angular contact ball bearing with a counter bore formed in the inner ring, the difference between the maximum radius of the counter bore of the inner ring and the radius of the inscribed circle where the balls are arranged when the ball is brought to the outer ring, This is called a bill. At the time of assembly, in the non-separable angular ball bearing, the outer ring is heated and thermally expanded to hit the ball, and the ball is assembled between the raceway surfaces of the inner and outer rings. When handling after assembly, the presence of the allowance makes it difficult for the outer ring or the inner ring to come off, thereby realizing a non-separable angular ball bearing.
Conventionally, in a non-separable angular contact ball bearing in which a counter bore is formed on an outer ring, it has been proposed that the allowance: W (mm) is 0.005 Dw ≦ W ≦ 0.030 Dw (see Patent Document 2). ). Here, Dw is the diameter of the ball. Further, a temperature of about 100 ° C. is recommended as the heating temperature of the outer ring during assembly.
Practical registration 2069438 (Figs. 6 and 7) JP 2005-009643 A

Generally, in a non-separable angular contact ball bearing, when the allowance is small, the heating temperature of the outer ring during assembly can be lowered, so that the assembly of the bearing is easy, but there is a problem that the outer ring or the inner ring is easily detached during handling. . On the other hand, when the cost is large, it is necessary to increase the heating temperature of the outer ring at the time of assembly, so that it is difficult to assemble the bearing, and when the heating temperature is insufficient, the ball may be damaged. is there.
The problem of the prior art (Japanese Patent Laid-Open No. 2005-009643) will be described with reference to FIG. 1 in the case of an angular ball bearing in which a counter bore is formed on the outer ring of the reference number 7906A. In the figure, the central axis of the inner ring and the central axis of the outer ring are overlapped. In FIG. 1, 1 is a bearing, 2 is an outer ring, 3 is an inner ring, and 4 is a ball. The cage was omitted.
The external dimensions of 7906A are inner diameter × outer diameter × width = 30 mm × 47 mm × 9 mm, ball diameter: Dw = 4.763 mm, and radial internal gap corresponding to a contact angle of 30 degrees: Δr = 0.0574 mm. From the diameter of the ball, the recommended value of the allowance W is calculated as 0.024 mm ≦ W ≦ 0.143 mm.

Here, in the case of W = 0.143 mm which is the maximum value of the recommended allowance, the allowance H when the outer ring is heated to 100 ° C. is calculated. The bearing material is bearing steel (SUJ2). Various dimensions before heating are as follows.
・ Center radius of the outer periphery and inner periphery of the bearing: R ₀ = (30 + 47) /4=19.250 mm
The radius of the circumscribed circle in which the balls are arranged when the balls are brought to the inner ring: R ₁ = R ₀ + Dw / 2−Δr / 4 = 21.617 mm
・ Minimum radius of counter bore of outer ring: R ₂ = R ₁ −W = 21.474 mm
Assuming that the room temperature is 20 ° C. and the linear expansion coefficient of the bearing material (SUJ2) is α = 12.5 × 10 ⁻⁶ (° C. ⁻¹ ),
・ Minimum radius of counter bore of outer ring at 100 ° C .: R ₃ = R ₂ × (1 + α × (100−20)) = 21.495 mm
Therefore,
Cost for heating to 100 ° C .: H = R ₁ −R ₃ = 0.122 mm
It becomes. The allowance (H) of 0.122 mm is a large value, and at a heating temperature of 100 ° C., the assembly of the bearing is not easy, and there is a problem that the occurrence of ball scratches is inevitable when forcibly assembled. Temporarily, in an outer ring with a allowance W of 0.143 mm, in order to set the allowance H at the time of heating to 0 mm, it is necessary to heat to about 550 ° C., and there is a problem that assembly is impossible in practice.

Further, in order to set the cost (H) during heating at 100 ° C. to 0 mm, the cost W needs to be 0.021 mm. This value is indicated by the prior art (Japanese Patent Laid-Open No. 2005-009643). There is also a problem that the allowance is not realized because the allowance W is below the minimum value 0.024 mm.
Furthermore, the minimum value 0.024 mm of the starting allowance W in the prior art (Japanese Patent Laid-Open No. 2005-009643) is examined. The state of the bearing after assembly is as shown in FIG. The lower half of the bearing (not shown) also has a value of 0.0287 mm, which is half the radial internal clearance. Therefore, when the bearing is actually handled, in FIG. 1, the inner ring of the bearing is lowered by 0.0287 mm, and the circumscribed circle in which the balls are arranged is also moved by 0.0287 mm. Therefore, the position of the circumscribed circle where the balls are arranged is located below the position of the minimum radius of the counterbore in the outer ring, and there is a problem that the outer ring is easily detached.

As described above, in the conventional non-separable angular contact ball bearing, there are problems that the heating temperature is low and the operation is easy, the ball is not damaged during assembly, and it is not completely satisfied that the ball is not separated during handling. is there.
And in the non-separable angular contact ball bearing in which the solid lubricating film is formed on the ball, there is a problem that the solid lubricating film is damaged at the time of assembly and the bearing life in use is shortened. Also, in non-separable angular contact ball bearings formed on the raceway surfaces of the inner ring and outer ring, where the solid lubricating film is not formed on the balls, if the balls are damaged during assembly, the balls will be scratched on the inner and outer rings. There is a problem that the solid lubricating film formed on the raceway surface is damaged and the bearing life in use is shortened. Furthermore, as the heating temperature of the outer ring at the time of assembly increases, there is a problem that the solid lubricating film deteriorates by oxidation during heating and the bearing life in use is shortened. For this reason, in conventional non-separable angular contact ball bearings in which a solid lubricating film is formed on one or more of the ball surface, the inner ring raceway surface, and the outer ring raceway surface, the solid lubricating film is damaged during assembly, Due to oxidative deterioration, there is a problem that the life of the solid lubricating film is reduced and the life of the bearing in use is shortened.
As described above, the conventional non-separable angular contact ball bearings are not designed with appropriate margins, so the heating temperature during assembly is high and the work is difficult, the balls are damaged during assembly, and the outer ring is handled during handling. Or there was a problem that the inner ring was separated and the bearing life in use was short.

  The present invention has been made in view of such problems, and by appropriately designing the allowance, the heating temperature at the time of assembly is low and the operation is easy, the ball is not damaged during assembly, It is an object of the present invention to provide a non-separable angular contact ball bearing in which an outer ring or an inner ring is not separated during handling and a bearing life in use is long.

In order to solve the above problems, the present invention is configured as follows.
In addition, the unit of dimensions, such as a radius, a diameter, a margin, a clearance gap, described below is mm.
According to the first aspect of the present invention, one side in the axial direction of the shoulder adjacent to the inner raceway surface of the outer ring made of bearing steel is scraped to form a counterbore, and the inner ring and the outer ring are heated by heating the outer ring. In non-separable angular contact ball bearings assembled with balls in between,
0.0125mm barbs margin is the difference between the minimum radius of counterbore radius R ₁ and the outer ring of the circumscribed circle of the sequence of balls when asked the balls to the inner ring, or half the value of the radial clearance From the larger numerical value of 1.25 × 10 ⁻⁵ × R ₁ × (heating temperature of the outer ring−room temperature during assembly) +0.010 mm.
According to the second aspect of the present invention, a counter bore is formed by cutting one side in the axial direction of the shoulder adjacent to the outer raceway surface of the inner ring facing the outer ring made of bearing steel, and heating the outer ring in non-separable angular contact ball bearing assembled by incorporating a ball between the inner ring and the outer ring, the maximum radius of the raceway surface of the outer ring when the R _7, the outer ring of the ball and the maximum radius of the inner ring of the counterbore From the larger value of 0.0125 mm, or half of the radial internal gap, the difference between the radius of the inscribed circle where the balls are arranged when the ball is moved to 1.25 × 10 ⁻⁵ × R ₇ × (outer ring heating temperature−room temperature during assembly) +0.010 mm.
According to a third aspect of the present invention, there is provided a counterbore formed by shaving one axial side of the shoulder adjacent to the inner raceway surface of the outer ring made of martensitic stainless steel, and the inner ring is heated by heating the outer ring. In the non-separable angular contact ball bearing assembled by incorporating balls between the outer ring and the outer ring, a radius R ₁ of a circumscribed circle in which the balls are arranged when the balls are brought close to the inner ring and a minimum radius of the counter bore of the outer ring The difference, which is the difference, is 0.0125 mm or half of the radial internal gap, whichever is larger, 1.01 × 10 ⁻⁵ × R ₁ × (heating temperature of outer ring−room temperature during assembly) +0 The range is .010 mm.
According to a fourth aspect of the present invention, one side in the axial direction of the shoulder adjacent to the outer raceway surface of the inner ring facing the outer ring made of martensite stainless steel is scraped to form a counterbore, and the outer ring is heated. wherein the inner ring and the non-separable angular contact ball bearing assembled by incorporating a ball between the outer ring, the maximum radius of the raceway surface of the outer ring when the R _7, wherein the maximum radius of the inner ring counterbore ball by From the larger value of 0.0125 mm or half of the radial internal clearance, 1.01 × 10 6 is calculated as the difference between the radius of the inscribed circle in which the balls are arranged when the ball is moved to the outer ring. ^-5 × R ₇ × (outer ring heating temperature−room temperature during assembly) +0.010 mm.
In the fifth aspect of the present invention, the difference between the heating temperature of the outer ring and the room temperature during assembly is set to 150 ° C. or less.
According to a sixth aspect of the present invention, a solid lubricating film is formed on any one or more of the surface of the ball, the raceway surface of the inner ring and the outer ring.

First, the effect relating to the upper limit of the allowance will be described. From an experiment of an angular ball bearing in which a solid lubricating film is formed on a ball, it has been found that if the cost is 0.010 mm or less, the solid lubricating film will not be damaged. Based on this,
According to the first and third aspects of the present invention, when the outer ring is heated, the ball is brought close to the “minimum radius of the counterbore of the outer ring” which causes a change in thermal expansion of the allowance. Paying attention to the "radius of the circumscribed circle where the balls are arranged", and the allowance according to the linear expansion coefficient of the outer ring material (heating temperature of the outer ring-room temperature during assembly) and the allowance for heating Is 0.010 mm or less, and the ball is not damaged during assembly.
Further, in the inventions of claims 2 and 4, paying attention to the dimension of the “maximum radius of the race groove of the outer ring” that causes a change in thermal expansion when the outer ring is heated, -Room temperature at the time of assembly) and the allowance according to the linear expansion coefficient of the material of the outer ring are set, so the allowance during heating is 0.010 mm or less, and the ball is not damaged during assembly. .
Next, effects related to the lower limit of the allowance will be described. First, from an experiment of an angular ball bearing in which a solid lubricating film is formed on a ball, it was found that the bearing is difficult to separate if the cost is 0.0125 mm or more. However, it has also been found that even if the cost is 0.0125 mm or more, if the half value of the radial internal gap is larger than 0.0125 mm, the bearings are easily separated.
From this result, in the invention according to claims 1 to 4, the cost is set to 0.0125 mm or half of the radial internal gap, whichever is larger. In this case, the bearing is difficult to separate.
In the invention according to claim 5, by setting the difference between the heating temperature of the outer ring and the room temperature at the time of assembly to 150 ° C. or less, in addition to the above effect, the heating temperature is lowered and the assembly work is further facilitated. It becomes.
In the invention according to claim 6, in the non-separable angular bearing in which the solid lubricating film is formed on any one or more of the ball surface, the inner raceway surface, and the outer raceway surface, In addition, the occurrence of scratches on the solid lubricating film is avoided, and the oxidation deterioration of the solid lubricating film is reduced, so that the bearing life in use is extended.

Hereinafter, specific examples of the method of the present invention will be described with reference to the drawings and tables.

A cross-sectional view of the first embodiment in which the counter bore is formed by cutting one axial side of the shoulder adjacent to the inner raceway surface of the outer ring from the non-separable angular contact ball bearing of the present invention. As shown in FIG. In the figure, 1 is a non-separable angular ball bearing, 2 is an outer ring, 3 is an inner ring, 4 is a ball, and 5 is a counter bore of the outer ring 2.
The rotation center axis of the outer ring 2 and the rotation center axis of the inner ring 3 are overlapped, and the illustration of the cage is omitted. R ₀ is the center radius of the outer periphery and inner periphery of the bearing 1, R ₁ is the radius of the circumscribed circle in which the balls 4 are arranged when the balls 4 are brought close to the inner ring 3, and R ₂ is the counter bore 5 of the outer ring 2. The minimum radius. When the radial internal clearance is Δr, there is a clearance of Δr / 2 between the ball 4 and the outer ring 2, and the center of the ball 4 is lowered by Δr / 4 from the pitch circle radius R _0. To position. W is a cost that is the difference between the radius R _{1 of the} circumscribed circle in which the balls 4 are arranged when the ball 4 is brought close to the inner ring 3 and the minimum radius R ₂ of the counter bore 5 of the outer ring 2.
The assembly of the bearing 1 is performed as follows. In a state where the balls 4 are brought close to the inner ring 3, the outer ring 2 heated to a predetermined temperature by a high frequency induction heating device or the like is inserted from the counter bore 5 and assembled. By heating the outer ring 2, the minimum radius of the counterbore 5 of the outer ring 2 expands in R _3, the difference between R ₁ and R _3, the heating time of the take cash H. R ₃ and H are not shown. There is also a negative value for the allowance H during heating.
Usually, if the cost H during heating is 0 mm or less, it is considered that the ball is not damaged during assembly. However, if the cost H during heating is unnecessarily set to a large negative value, the heating temperature becomes high and assembly becomes difficult, or the cost W after assembly becomes small and the bearing is separated. There is a fear that it becomes easy to do.

Here, a non-heating assembly experiment was performed using an angular ball bearing in which a solid lubricating film was formed on the ball. As a result, it was found that the solid lubricating film formed on the ball would not be damaged if the cost W during non-heating is 0.010 mm or less. The reason why W is allowed up to a slightly positive value is considered to be caused by the inner ring or the outer ring being inclined during actual assembly and deviating from the state shown in FIG. From this result, it is inferred that the solid lubricant film formed on the ball is not damaged if the cost H during heating is 0.010 mm or less.
Therefore, in the inventions according to claims 1 and 3, “balls that are close to the dimension of the“ minimum radius of the counterbore of the outer ring ”, which causes a change in thermal expansion when the outer ring is heated, are produced. Focusing on the radius of the circumscribed circle in which the balls are arranged at the time of the movement: R ₁ ”, depending on the material of the outer ring (heating temperature of the outer ring−room temperature at the time of assembly): ΔT (° C.) and R ₁ The maximum value of the allowance was set to the value represented by the following formula.

・ For bearing steel: 1.25 × 10 ⁻⁵ × R ₁ × ΔT + 0.010
In the case of martensitic stainless steel: 1.01 × 10 ⁻⁵ × R ₁ × ΔT + 0.010
In the case of # 7906 used in the description of the prior art, a numerical value of the allowance is examined. When the bearing material is bearing steel (SUJ2), the room temperature of the assembly chamber is 20 ° C., the heating temperature is 200 ° C., and the above-mentioned numerical value of R ₁ : 21.617 mm is used, the cost: W
It becomes 1.25 × 10 ⁻⁵ × 21.617 × 180 + 0.010 = 0.0586 mm.
The minimum radius of the counter bore of the outer ring is R ₂ = R ₁ −W = 21.558 mm. When the room temperature is 20 ° C. and the linear expansion coefficient of the bearing steel (SUJ2) is α = 12.5 × 10 ⁻⁶ (° C. ⁻¹ ), the minimum radius of the counter bore of the outer ring at 200 ° C .: R ₃ is
R ₂ × (1 + α × (200−20)) = 21.707 mm
And cost when heated to 200 ° C .: H = R ₁ −R ₃ = 0.010 mm
It becomes. Therefore, the ball is not damaged during assembly. Furthermore, when the heating temperature is lowered to 150 ° C., the cost is set to 0.0452 mm, and the assembly operation is facilitated by lowering the heating temperature.

Next, the setting of the lower limit value of the allowance will be described. We conducted an unheated assembly experiment using angular contact ball bearings with a solid lubricant film on the balls. As a result, it was found that the bearing is difficult to separate if the unloading allowance W is 0.0125 mm or more. At the same time, it has also been found that even if the allowance is 0.0125 mm or more, the bearing is easily separated if it is larger than half the radial internal clearance. The state of the bearing after assembly is as shown in FIG. The lower half of the bearing, not shown, also has a value that is half the radial internal clearance. Therefore, when the bearing is actually handled, in FIG. 1, the inner ring of the bearing is lowered by half the value of the radial internal gap, and the circumscribed circle in which the balls are arranged moves by the same dimension. Therefore, even if the cost is 0.0125 mm or more, if the half value of the radial internal gap is larger than 0.0125 mm, the bearings are easily separated.
Accordingly, since the lower limit value of the allowance is set to 0.0125 mm or half the radial internal gap, whichever is larger, the bearings are difficult to separate during handling after assembly.

FIG. 2 is a sectional view showing a second embodiment of the present invention.
This embodiment is an example in which one side in the axial direction of the shoulder adjacent to the outer raceway surface of the inner ring is cut out from the non-separable angular contact ball bearing to form a counterbore. In the figure, 1 is a non-separable angular contact ball bearing, 2 is an outer ring, 3 is an inner ring, 4 is a ball, and 6 is a counter bore of the inner ring 3. In the figure, the rotation center axis of the outer ring 2 and the rotation center axis of the inner ring 3 are overlapped, and the illustration of the cage is omitted. R ₀ is the central radius of the outer periphery and inner periphery of the bearing 1, R ₄ is the maximum radius of the counterbore 6 of the inner ring 3, and R ₅ is the inscribed arrangement of the balls 4 when the balls 4 are brought close to the outer ring 2. The radius of the circle, R _7, is the maximum radius of the raceway groove of the outer ring 2. When the radial internal clearance is Δr, there is a clearance of Δr / 2 between the ball 4 and the inner ring 3, and the center of the ball 4 is located at a position that is Δr / 4 higher than the pitch circle radius _R0. To do. W is a margin that is the difference between the radius R _{4 of the} inscribed circle in which the balls 4 are arranged when the balls 4 are brought close to the outer ring 2 and the maximum radius R ₅ of the counter bore 6 of the inner ring 3.
The assembly of the bearing 1 is performed as follows. In a state where the balls 4 are brought close to the outer ring 2, the outer ring 2 is heated to a predetermined temperature by a high frequency induction heating device or the like, and the inner ring 3 is inserted into the outer ring 2 from the counter bore 6 side and assembled. By heating the outer ring 2, the maximum radius R ₇ of the raceway groove of the outer ring 2 expands, and as a result, the balls 4 move upward in the figure and the balls 4 are arranged when the balls 4 are brought close to the outer ring 2. radius of an inscribed circle becomes larger in R ₆ to. Then, the difference between the maximum radii R ₄ and R ₆ of the counter bore 6 of the inner ring 3 is a cost H during heating. R ₆ and H are not shown. There is also a negative value for the allowance H during heating.

Usually, if the cost H during heating is 0 mm or less, it is considered that the ball is not damaged during assembly. However, if the cost H during heating is unnecessarily set to a large negative value, the heating temperature becomes high and assembly becomes difficult, or the cost W after assembly becomes small and the bearing is separated. There is a fear that it becomes easy to do.
Here, as a result of performing an unheated assembly experiment using an angular ball bearing in which a solid lubricating film is formed on the ball, the solid formed on the ball is less than 0.010 mm when the unloading allowance W is 0.010 mm or less. It was found that the lubricating film was not damaged. The reason why W is allowed up to a slightly positive value is considered to be caused by the inner ring or the outer ring being inclined during actual assembly and deviating from the state shown in FIG. From this result, it is inferred that the solid lubricant film formed on the ball is not damaged if the cost H during heating is 0.010 mm or less.
Therefore, in the inventions according to claims 2 and 4, paying attention to the “maximum radius R _{7 of the} race groove of the outer ring” that causes a change in thermal expansion when the outer ring is heated, (Heating temperature of outer ring—room temperature during assembly): For ΔT (unit ° C.) and R ₇ , the maximum value of the allowance was set to a value represented by the following equation.

・ For bearing steel: 1.25 × 10−5 × R ₇ × ΔT + 0.010
In the case of martensitic stainless steel: 1.01 × 10 ⁻⁵ × R ₇ × ΔT + 0.010
In the case of # 7906 used in the description of the prior art, a numerical value of the allowance is examined. The material of the bearing was bearing steel (SUJ2), the room temperature of the assembly chamber was 20 ° C, and the heating temperature was 200 ° C. If the diameter of the ball is Dw and the radial internal gap is Δr, the dimensions before heating are as follows.
・ Center radius of the outer periphery and inner periphery of the bearing: R ₀ = (30 + 47) /4=19.250 mm
The radius of the inscribed circle where the balls are arranged when the balls are brought close to the outer ring: R ₅ = R ₀ −Dw / 2 + Δr / 4 = 16.883 mm
・ Maximum radius of outer raceway groove: R ₇ = R ₀ + Dw / 2 + Δr / 4 = 21.646 mm
From this, cost: W is
It becomes 1.25 × 10 ⁻⁵ × 21.646 × 180 + 0.010 = 0.0587 mm.
The maximum radius of the counter bore of the inner ring is R ₄ = R ₅ + W = 16.942 mm. When the room temperature is 20 ° C. and the linear expansion coefficient of the bearing steel (SUJ2) is α = 12.5 × 10 ⁻⁶ (° C. ⁻¹ ), an inscribed circle in which the balls are arranged when the balls at 200 ° C. are brought close to the outer ring. The radius R ₆ of
R ₅ + (R ₇ × α × (200−20)) = 16.932 mm
And cost when heated to 200 ° C .: H = R ₄ −R ₆ = 0.010 mm
It becomes. Therefore, the ball is not damaged during assembly. Furthermore, when the heating temperature is lowered to 150 ° C., the cost is set to 0.0452 mm, and the assembly operation is facilitated by reducing the heating temperature.

Next, the setting of the lower limit value of the allowance will be described. We conducted an unheated assembly experiment using angular contact ball bearings with a solid lubricant film on the balls. As a result, it was found that the bearing is difficult to separate if the unloading allowance W is 0.0125 mm or more. At the same time, it has also been found that even if the allowance is 0.0125 mm or more, the bearing is easily separated if it is larger than half the radial internal clearance. The state of the bearing after assembly is as shown in FIG. The lower half of the bearing, not shown, also has a value that is half the radial internal clearance. Therefore, when the bearing is actually handled, in FIG. 1, the inner ring of the bearing is lowered by half the value of the radial internal gap, and the circumscribed circle in which the balls are arranged moves by the same dimension. Therefore, even if the cost is 0.0125 mm or more, if the half value of the radial internal gap is larger than 0.0125 mm, the bearings are easily separated.
Therefore, since the lower limit of the allowance is set to 0.0125 mm or half the radial internal clearance (unit: mm), whichever is larger, the bearing is difficult to separate during handling after assembly. Become.
In a non-separable angular bearing in which a solid lubricating film is formed on one or more of the ball surface, the inner ring raceway surface, or the outer ring raceway surface, the solid lubricating film is damaged during heating during assembly. Since generation | occurrence | production is avoided and the oxidative degradation of a solid lubricating film is reduced, the bearing life at the time of use becomes long.

As described above, in a non-separable angular contact ball bearing that is assembled by assembling a ball between the inner ring and the outer ring by heating the outer ring, the radius of the circumscribed circle in which the balls are arranged when the ball is brought to the inner ring, or , The maximum radius of the raceway surface of the outer ring, (heating temperature of the outer ring-room temperature during assembly), the coefficient of thermal expansion of the material of the outer ring, and then by appropriately designing the allowance according to the radial internal clearance, during assembly Therefore, it is possible to provide a non-separable angular contact ball bearing in which the heating temperature is low, the work is easy, the ball is not damaged during assembly, and the outer ring or the inner ring is not separated during handling.
In particular, in the non-separable angular contact ball bearings in which a solid lubricating film is formed on one or more of the ball surface, the inner ring raceway surface, and the outer ring raceway surface, the heating temperature during assembly is reduced by the above measures. It is possible to provide a non-separable angular contact ball bearing that is easy to work, does not damage the ball during assembly, does not separate the outer ring or the inner ring during handling, and has a long bearing life in use.

This embodiment is suitable for non-separable angular contact ball bearings lubricated with lubricating oil or lubricating grease. This is more effective for non-separable angular contact ball bearings lubricated with a solid lubricating film.

Sectional drawing of the non-separable angular contact ball bearing which shows 1st Example of this invention Sectional drawing of the non-separable angular contact ball bearing which shows 2nd Example of this invention

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Non-separable angular contact ball bearing 2 Outer ring 3 Inner ring 4 Ball 5 Outer ring counter bore 6 Inner ring counter bore R ₀ Center radius R of the outer circumference and inner circumference R ₁ Radius R ₂ Minimum radius R of outer ring counter bore R ₄ Maximum radius of counter bore R of inner ring R ₅ Radius of inscribed circle in which balls are arranged when they are brought close to outer ring R ₇ Maximum radius W of outer ring raceway surface Generation

Claims (6)

One side in the axial direction of the shoulder adjacent to the inner raceway surface of the outer ring made of bearing steel is scraped to form a counterbore, and the outer ring is heated to assemble a ball between the inner ring and the outer ring. In the separated angular contact ball bearing,
0.0125mm barbs margin is the difference between the minimum radius of counterbore radius R ₁ and the outer ring of the circumscribed circle of the sequence of balls when asked the balls to the inner ring, or half the value of the radial clearance A non-separable angular contact ball bearing characterized by a range of 1.25 × 10 ⁻⁵ × R ₁ × (heating temperature of outer ring−room temperature during assembly) +0.010 mm. One side in the axial direction of the shoulder adjacent to the outer raceway surface of the inner ring facing the outer ring made of bearing steel is scraped to form a counterbore, and by heating the outer ring, a ball is inserted between the inner ring and the outer ring. In non-separable angular contact ball bearings assembled and assembled,
When the maximum radius of the raceway surface of the outer ring is R ₇ , the margin is the difference between the maximum radius of the counter bore of the inner ring and the radius of the inscribed circle in which the balls are arranged when the balls are brought close to the outer ring. From the larger value of 0.0125 mm or half of the radial internal clearance, 1.25 × 10 ⁻⁵ × R ₇ × (outer ring heating temperature−room temperature during assembly) +0.010 mm Non-separable angular contact ball bearings. A counterbore is formed by shaving the axial side of the shoulder adjacent to the inner raceway surface of the outer ring made of martensitic stainless steel, and a ball is incorporated between the inner ring and the outer ring by heating the outer ring. In non-separable angular contact ball bearings to be assembled,
The engagement allowance is the difference between the minimum radius of counterbore radius R ₁ and the outer ring of the circumscribed circle of arrangement of the ball when asked the balls into inner ring, 0.0125 mm, or half of the radial clearance A non-separable angular contact ball bearing characterized in that the larger value is 1.01 × 10 ⁻⁵ × R ₁ × (heating temperature of outer ring−room temperature during assembly) +0.010 mm. One side in the axial direction of the shoulder adjacent to the outer raceway surface of the inner ring facing the outer ring made of martensitic stainless steel is scraped to form a counterbore, and the outer ring is heated between the inner ring and the outer ring. In non-separable angular contact ball bearings assembled with balls,
When the maximum radius of the raceway surface of the outer ring is R ₇ , the margin is the difference between the maximum radius of the counter bore of the inner ring and the radius of the inscribed circle in which the balls are arranged when the balls are brought close to the outer ring. From the larger value of 0.0125 mm or half of the radial internal clearance to 1.01 × 10 ⁻⁵ × R ₇ × (heating temperature of outer ring−room temperature during assembly) +0.010 mm Non-separable angular contact ball bearings.   The non-separable angular contact ball bearing according to claim 1, wherein a difference between a heating temperature of the outer ring and a room temperature at the time of assembly is set to 150 ° C. or less.   6. The non-separable angular contact ball bearing according to claim 1, wherein a solid lubricating film is formed on at least one of the surface of the ball and the raceways of the inner ring and the outer ring.

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