JP2005164005A - Angular contact ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an angular contact ball bearing used for oil lubrication capable of suppressing heat generation by facilitating exhaust of lubricating oil between a retainer and an outer ring. <P>SOLUTION: The angular contact ball bearing 1 includes a shoulder part A, which is adjacent to a raceway surface 3a on an inner diameter surface on a back surface side from the raceway surface 3a of the outer ring 3, and is formed in a tapered surface 3b with an outer ring end surface side of a larger diameter. Thereby, a clearance (a) with the retainer 5 on the back surface side of the outer ring 3 is enlarged to facilitate the exhaust of the lubricating oil from the clearance (a). <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an angular ball bearing used for supporting a spindle or the like of a machine tool.

In an oil-lubricated angular contact ball bearing, for example, as shown in FIG. 11, the lubricating oil that has entered the gap between the retainer 35 and the rolling element 34 from the inner ring 32 is interposed between the retainer 35 and the outer ring 33 by centrifugal force as indicated by an arrow. Is discharged to the side of the bearing.
In such an angular ball bearing, in order to improve the inflow property of the lubricating oil, the inner diameter surface of the cage 35 is inclined so as to increase in diameter toward the rolling element 34, contrary to the illustrated example, There has been proposed one in which the lubricating oil adhering to the inclined surface is moved to the rolling element 34 side by centrifugal force (for example, Patent Document 1).
JP 2001-99161 A

  When an angular contact ball bearing is used with oil lubrication, it is necessary to suppress heat generation of the bearing due to stirring of the lubricating oil. In the proposed example, the inflow property of the lubricating oil is improved, but the gap between the retainer 35 serving as the outlet and the outer ring 33 is small as in the example of FIG. For this reason, the lubricating oil is not easily discharged, and the lubricating oil accumulates inside the bearing and is agitated, thereby increasing heat generation.

  An object of the present invention is to provide an angular contact ball bearing capable of suppressing the heat generation due to stirring by improving the drainage of the lubricating oil between the cage and the outer ring in the angular contact ball bearing that is oil lubricated. .

The angular contact ball bearing of the present invention is an angular contact ball bearing having a cage that holds rolling elements, and the shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side from the raceway surface of the outer ring has a larger diameter on the outer ring end surface side. It is characterized by being formed on a tapered surface.
According to this configuration, since the shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side of the outer ring is formed in a tapered surface having a large diameter on the outer ring end surface side, the outer ring and the retainer on the back side of the outer ring where clearance is difficult to obtain. The gap between the two can be increased, and the lubricating oil is easily discharged from this gap. For this reason, the amount of oil accumulated in the bearing and stirred can be reduced, and heat generation due to oil stirring can be suppressed.

Another angular ball bearing according to the present invention is an angular contact ball bearing having a cage for holding a rolling element, wherein a portion on the back side of the outer ring is larger than a pocket width on an outer diameter surface of the cage, and an end side in the width direction is larger. It is characterized by being formed on a tapered surface having a diameter.
According to this configuration, the outer ring rear surface portion of the outer diameter surface of the cage is formed into a tapered surface having a large diameter on the end side in the width direction, so the outer diameter of the central portion in the width direction of the cage outer diameter surface. The gap between the outer ring and the cage on the back side of the outer ring can be increased. Therefore, the lubricating oil can be easily discharged from the gap, the amount of oil accumulated in the bearing and stirred can be reduced, and heat generation due to oil stirring can be suppressed.

Still another angular contact ball bearing of the present invention is an angular contact ball bearing having a cage for holding a rolling element, wherein the shoulder adjacent to the raceway surface on the inner diameter surface on the back side of the raceway surface of the outer ring is larger on the outer ring end surface side. It is formed on a tapered surface having a diameter, and a portion on the back side of the outer ring with respect to the pocket width on the outer diameter surface of the cage is formed on a tapered surface having a large diameter on the end side in the width direction. .
According to this configuration, since the shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side of the outer ring is formed in a tapered surface having a large diameter on the end surface side of the outer ring, between the outer ring and the cage on the back side of the outer ring. The gap can be enlarged. In this configuration, the outer ring rear surface portion of the outer diameter surface of the cage is formed into a tapered surface having a large diameter at the end in the width direction, so that the outer ring inner diameter surface and the cage outer diameter surface on the rear side are both It will be opposed by a tapered surface in the same inclination direction. For this reason, the clearance between the outer ring and the retainer can be increased while the outer diameter of the retainer is increased to ensure the rigidity of the retainer, and the lubricating oil can be discharged from the clearance. Therefore, heat generation due to oil agitation can be suppressed and cage rigidity can be ensured.

In these inventions, the angular ball bearing may be used for a bearing that supports a main shaft of a machine tool.
The main spindle of a machine tool is required to rotate at high speed in order to improve machining efficiency, and it is necessary to suppress heat generation of the bearing as much as possible in order to improve machining accuracy. Therefore, the heat generation suppressing effect of the angular ball bearing of the present invention is effectively exhibited, and the main shaft can be rotated at high speed while preventing heat generation.

An angular ball bearing device with a nozzle according to the present invention includes the angular ball bearing according to any one of the above-described inventions, and a lubricating oil supply nozzle that supplies lubricating oil to an outer diameter surface of an inner ring in the angular ball bearing. . The lubricating oil supply nozzle may be provided on the back side of the bearing or on the front side.
According to this configuration, the lubricating oil supplied from the lubricating oil supply nozzle is sprayed onto the outer diameter surface of the inner ring of the angular ball bearing, and the lubricating oil is efficiently supplied into the bearing. Therefore, the lubrication of the bearing can be improved while suppressing heat generation due to oil agitation.

In the angular contact ball bearing of the present invention, the shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side from the raceway surface of the outer ring is formed into a tapered surface having a large diameter on the outer ring end surface side. The lubricating oil is better discharged between the cage and the outer ring, and the heat generation of the bearing can be suppressed.
In another angular ball bearing of the present invention, the outer ring rear surface portion of the outer diameter surface of the cage is formed into a tapered surface having a large diameter on the end side in the width direction. The gap with the outer diameter surface can be increased, and when used in oil lubrication, the lubricating oil is better discharged between the cage and the outer ring, and heat generation of the bearing can be suppressed.
Still another angular contact ball bearing of the present invention is such that a shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side of the raceway surface of the outer ring is formed into a tapered surface having a large diameter on the outer ring end surface side, and The outer ring back surface portion of the outer diameter surface is formed into a tapered surface with a large diameter at the end in the width direction, improving the drainage of lubricating oil between the cage and outer ring while ensuring the rigidity of the cage. Heat generation of the bearing can be suppressed.

  A first embodiment of the present invention will be described with reference to FIGS. This angular ball bearing 1 has a cage 5 that holds a rolling element 4, and a plurality of rolling elements 4 held in a pocket 5 a of the cage 5 are arranged between the raceway surfaces 2 a and 3 a of the inner ring 2 and the outer ring 3. It is interposed. The rolling element 4 consists of a ball. In the outer ring 3, the entire inner diameter surface on the back side of the raceway surface 3a is formed into a tapered surface 3b having a large diameter on the outer ring end surface side. The inner diameter surface on the back side of the outer ring 3 may be at least the shoulder A adjacent to the raceway surface 3a, that is, the vicinity of the raceway surface 3a may be a tapered surface 3b having a large diameter on the outer ring end surface side. The entire surface does not necessarily have to be the tapered surface 3b. In FIG. 2, the outer ring inner diameter surface of the conventional example corresponding to the tapered surface 3b is indicated by a two-dot chain line for comparison with the conventional example. In the conventional example, the vicinity of the end portion of the inner surface of the outer ring is a tapered surface, but the shoulder A ′ is a cylindrical surface.

  According to the angular ball bearing 1 of this configuration, when used in oil lubrication, the shoulder A of the inner diameter surface of the outer ring 3 is formed on the tapered surface 3b having a larger diameter on the outer ring end surface side. As can be seen from comparison with the conventional example shown in FIG. 3, the clearance a between the outer ring 3 and the cage 5 on the back side becomes larger. For this reason, the lubricating oil that has flowed into the bearing can be easily discharged from the gap a. Therefore, the amount of oil accumulated and stirred in the bearing can be reduced, and heat generation due to oil stirring can be suppressed.

  FIG. 3 shows another embodiment of the present invention. The angular ball bearing device with nozzle 6 of this embodiment includes the angular ball bearing 1 of the embodiment of FIG. 1 and a lubricating oil supply nozzle 7 that supplies lubricating oil to the outer diameter surface of the inner ring 2 in the angular ball bearing 1. Prepare. The lubricating oil supply nozzle 7 is attached to the inner surface of a housing (not shown) to which the outer ring 3 of the angular ball bearing 1 is attached, adjacent to the angular ball bearing 1. The lubricating oil supply nozzle 7 is provided with a discharge hole 8 facing the outer diameter surface of the inner ring 2 on the bearing back side (that is, the inner ring front side) and having a discharge port 8a. The discharge holes 8 are provided at one or a plurality of locations in the circumferential direction of the lubricating oil supply nozzle 7. The inlet of the discharge hole 8 communicates with an oil supply passage 9 provided from the lubricant supply nozzle 7 to the housing, and is connected to a lubricant supply source (not shown).

  According to the angular ball bearing device 6 with a nozzle having this configuration, the lubricating oil supplied from the lubricating oil supply nozzle 7 is sprayed onto the outer diameter surface of the inner ring 2 of the angular ball bearing and efficiently supplied into the bearing. As described above, since the inner diameter surface on the back side of the outer ring 3 is the tapered surface 3b, the lubricating oil can be discharged from the gap a between the outer ring 3 and the cage 5, so that the oil can be agitated. Lubricity can be improved while suppressing the generated heat.

  FIG. 4 shows a spindle device 10 using the angular ball bearing 1 of FIG. The spindle device 10 is applied to a machine tool, and a tool or workpiece chuck is attached to an end portion 15 a of a main shaft 15. The main shaft 15 is supported by a plurality of angular ball bearings 1 separated in the axial direction, and the lubricating oil supply nozzle 7 shown in FIG. 3 is provided adjacent to the angular ball bearings 1. The inner ring 2 of each angular ball bearing 1 is fitted to the outer diameter surface of the main shaft 15, and the outer ring 3 is fitted to the inner diameter surface of the housing 11. These inner and outer rings 2 and 3 are fixed in the housing 11 by an inner ring retainer 25 and an outer ring retainer 26. The housing 11 has a double structure of an inner peripheral housing 11A and an outer peripheral housing 11B, and a cooling medium flow path 16 is formed between the inner and outer housings 11A and 11B. The inner peripheral housing 11A is provided with the oil supply passage 9 (FIG. 3) and its supply port 9a. The housing 11 is installed on a support base 17 and fixed with bolts 18. Further, the housing 11 is provided with an oil drain groove 22 in the vicinity of the installation portion of the angular ball bearing 1 on the inner diameter surface, and an oil drain path 23 opened to the outside from the oil drain groove 22.

  Thus, by using the angular ball bearing 1 having the above-described configuration excellent in the heat generation suppressing effect to support the main shaft 15 of the spindle device 10 of the machine tool, the high speed of the main shaft 15 is prevented without causing a reduction in machining accuracy due to heat generation. Rotation is possible.

  5 and 6 show still another embodiment of the present invention. This angular ball bearing 1 </ b> A replaces the angular ball bearing 1 (FIG. 1) of the first embodiment with the shoulder A on the inner diameter surface of the outer ring 3 being formed on the tapered surface 3 b, instead of the cage 5. A portion B1 on the rear side of the outer ring and a portion B2 on the front side of the outer surface with respect to the pocket width on the outer diameter surface are tapered surfaces 5b and 5c having a large diameter on the end side in the width direction. The said pocket width says the width | variety part with the pocket 5a in the holder | retainer 5. FIG. By forming the tapered surfaces 5b and 5c in this way, the cage 5 is formed so as to have a cross-sectional shape in which the central portion in the width direction of the outer diameter surface is gently recessed. Other configurations are the same as those in the first embodiment. In FIG. 6, the cage outer diameter surface B ′ of the conventional example is indicated by a two-dot chain line for comparison with the conventional example.

  When the angular ball bearing 1A having this configuration is used in oil lubrication, a portion B1 on the outer ring rear surface side of the outer diameter surface of the cage is formed on a tapered surface 5b having a large diameter on the end side. By reducing the outer diameter of the central portion of the outer diameter surface of the vessel, the gap a between the outer ring 3 and the cage 5 on the back side can be increased as compared with the conventional example. As a result, the lubricating oil can be easily discharged from the gap a, the amount of oil accumulated in the bearing and agitated can be reduced, and heat generation due to oil agitation can be suppressed.

  7 and 8 show still another embodiment of the present invention. This angular ball bearing 1B is the angular ball bearing 1 according to the first embodiment, wherein a portion B1 on the rear side of the outer ring and a portion B2 on the front side of the outer ring with respect to the pocket width on the outer diameter surface of the cage 5 The tapered surfaces 5b and 5c have a large diameter on the part side. By using the tapered surfaces 5b and 5c as described above, the cage 5 is formed so that the central portion in the width direction of the outer diameter surface has a gently concave cross-sectional shape. That is, the shoulder A (FIG. 1) on the inner diameter surface of the outer ring 3 is formed on the tapered surface 3b, and the outer diameter surface portion B1 and the portion B2 of the cage 5 are tapered such that the end side in the width direction has a large diameter. It forms in the shape surfaces 5b and 5c. Other configurations are the same as those in the first embodiment. In FIG. 8, for comparison with the conventional example, the outer ring inner diameter surface shoulder A ′ and the cage outer diameter surface B ′ of the conventional example corresponding to the portions of the tapered surfaces 3 b, 5 b, 5 c are indicated by two-dot chain lines. ing.

  In the angular ball bearing 1B having this configuration, the shoulder A adjacent to the raceway surface in the inner diameter surface on the back side of the outer ring 3 is formed in a tapered surface having a large diameter on the outer ring end surface side. The gap a between 3 and the cage 5 can be increased. In this configuration, the outer ring rear surface portion B1 on the outer diameter surface of the cage 5 is formed into a tapered surface having a large diameter on the end side in the width direction, so that the outer ring inner diameter surface and the cage outer diameter surface on the rear surface side However, the tapered surfaces 3b and 5b having the same inclination direction are opposed to each other. For this reason, the clearance a between the outer ring 3 and the retainer 5 is increased while the outer diameter of the retainer 5 is increased to ensure the rigidity of the retainer 5, and the lubricating oil from the clearance a improves the discharge performance. be able to. Therefore, heat generation due to oil agitation can be suppressed and cage rigidity can be ensured.

  FIG. 9 shows still another embodiment of the present invention. This angular ball bearing 1C is a tapered surface in which the outer diameter surface on the bearing front side (inner ring rear side) is smaller than the raceway surface 2a of the inner ring 2 and the inner ring end surface side is smaller in the angular ball bearing 1 of the first embodiment. 2b. The tapered surface 2b may be provided on the entire inner ring outer diameter surface on the front side of the bearing with respect to the raceway surface 2a. In this example, the shoulder C adjacent to the raceway surface 2a is left in a cylindrical shape, and the remaining outer surface The radial surface portion is a tapered surface.

  As described above, when the outer diameter surface of the inner ring 2 is formed in the tapered surface 2b, when the lubricating oil is supplied from the bearing front side, the inflow property of the lubricating oil into the bearing is improved. For this reason, the lubricity can be further improved in combination with the fact that the shoulder A on the inner diameter surface of the outer ring 3 is formed on the tapered surface 3b to improve the oil discharge performance. Other configurations and effects are the same as those in the first embodiment.

  FIG. 10A shows a reference proposal example. This angular ball bearing 1D is the angular ball bearing 1C of the embodiment of FIG. 9, in which the shoulder A on the inner diameter surface of the outer ring 3 is replaced with a cylindrical surface instead of the shape formed on the tapered surface 3b. The outer ring end portion side portion is a tapered surface. That is, the outer ring 3 has the same shape as that of the conventional example shown in FIG. 11, the outer diameter surface on the bearing front side (inner ring rear side) with respect to the raceway surface 2 a of the inner ring 2, and the tapered surface 2 b having a smaller diameter on the inner ring end surface side. Is formed. Other configurations are the same as those in the embodiment of FIG.

  In the angular ball bearing 1D having this configuration, the outer diameter surface on the bearing front side of the inner ring 2 is formed in the tapered surface 2b, so that the inner diameter surface of the cage 5 and the inner ring outer diameter surface are tapered on the bearing front side. A gap b between the surface 2b is increased. Therefore, even if the lubricating oil supply nozzle 7 as shown in FIG. 3 is arranged adjacent to the bearing front side, the lubricating oil supplied from the lubricating oil supply nozzle 7 can be sufficiently supplied into the bearing. In addition, the strength of the groove shoulder portion on the bearing front side (inner ring back side) which is the load side of the inner ring 2 can be sufficiently secured.

  Compared with a general angular contact ball bearing 31 with a cage shown in FIG. In a general angular contact ball bearing 31 as shown in the figure, the bearing back side (inner ring front side) of the inner ring 32 is the non-load side, so the outer diameter of the inner ring 32 can be reduced. Is on the load side, the outer diameter of the inner ring is set large in order to ensure the groove shoulder dimension. For this reason, on the bearing front side, the gap b between the inner diameter surface of the cage 35 and the outer diameter surface of the inner ring 32 is smaller than that on the bearing back side (gap c). Insufficient lubrication inside the bearing. Such a problem can be solved by the theta-like surface 2b of the inner ring outer diameter surface of FIG.

3 shows an example of the angular ball bearing device 6 with a nozzle in which the lubricating oil supply nozzle 7 is disposed adjacent to the angular ball bearing 1 of FIG. 1, each angular ball shown in FIGS. You may comprise the angular ball bearing apparatus with a nozzle by arrange | positioning the lubricating oil supply nozzle 7 adjacent to the bearings 1A-1C.
4 shows an example of the spindle device 10 in which the angular ball shaft 1 of FIG. 1 is incorporated together with the lubricating oil supply nozzle 7. However, the angular ball bearings 1A to 1C shown in FIGS. The structure incorporated with the nozzle 7 may be sufficient.

It is sectional drawing which shows the angular ball bearing concerning 1st Embodiment of this invention. It is a partial expanded sectional view which shows the same bearing compared with the conventional angular contact ball bearing. It is sectional drawing which shows the angular ball bearing apparatus with a nozzle concerning other embodiment of this invention. It is sectional drawing which shows the spindle apparatus using the angular ball bearing of FIG. It is sectional drawing which shows the angular ball bearing concerning other embodiment of this invention. It is a partial expanded sectional view which shows the same bearing compared with the conventional angular contact ball bearing. It is sectional drawing which shows the angular ball bearing concerning further another embodiment of this invention. It is a partial expanded sectional view which shows the same bearing compared with the conventional angular contact ball bearing. It is sectional drawing which shows the angular ball bearing concerning further another embodiment of this invention. (A) is sectional drawing which shows the angular ball bearing concerning a reference proposal example, (B) is sectional drawing of a prior art example. It is explanatory drawing which shows the supply / discharge flow path of the lubricating oil in the conventional angular contact ball bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,1A-1C ... Angular contact ball bearing 2 ... Inner ring 3 ... Outer ring 3a ... Raceway surface 3b ... Tapered surface 4 ... Rolling element 5 ... Cage 5b ... Tapered surface 6 ... Angular ball bearing device 7 with nozzle ... Lubricating oil supply Nozzle 15 ... Main shaft A ... Shoulder B1 on the inner surface of the outer ring B1 ... Shoulder on the outer surface of the cage

Claims (5)

  In the angular contact ball bearing having a cage for holding the rolling elements, the shoulder adjacent to the raceway surface on the inner diameter surface on the back side of the raceway surface of the outer ring is formed in a tapered surface having a larger diameter on the outer ring end surface side. Angular contact ball bearing.   In the angular ball bearing having a cage for holding the rolling elements, a portion on the rear side of the outer ring with respect to the pocket width on the outer diameter surface of the cage is formed in a tapered surface having a large diameter on the end side in the width direction. Angular contact ball bearings.   In the angular ball bearing having a cage for holding the rolling element, a shoulder portion adjacent to the raceway surface on the inner diameter surface on the back side from the raceway surface of the outer ring is formed into a tapered surface having a larger diameter on the outer ring end surface side, An angular contact ball bearing characterized in that a portion on the back side of the outer ring with respect to the pocket width on the outer diameter surface of the cage is formed in a tapered surface having a larger diameter on the end side in the width direction.   4. The angular ball bearing according to claim 1, wherein the angular ball bearing is used as a bearing that supports a main shaft of a machine tool. An angular ball bearing device with a nozzle comprising the angular ball bearing according to any one of claims 1 to 3 and a lubricating oil supply nozzle for supplying lubricating oil to an outer diameter surface of an inner ring of the angular ball bearing. .

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