JP2005147372A - Tandem duplex angular ball bearing and separation method thereof - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tandem duplex angular ball bearing and a separation method thereof, having a raceway surface with little working resistance and high accuracy, facilitating assembling and disassembling, and hardly scattered in the course of conveying. <P>SOLUTION: Counter bores 12, 13 are provided in each one raceway surface 6, 7 of inner and outer rings of a tandem duplex angular ball bearing 1 having inner and outer rings 4, 5 integrated with two columns of ball groups 2, 3 having the same pitch circle diameter P, and grinding undercut parts 14, 15 are provided on the counter bore side of the other raceway surfaces 8, 9 on the anti-counter bore side. Further, the counter bore amount δis set smaller than the radial clearance gap Δs between the ball groups and the inner and outer raceway surfaces. The diameters Dg, Dn of the boundary parts 16, 17 between the grinding undercut parts and the raceway surfaces are set intermediate between the other raceway bottom diameters dg, dn and the diameters Rg, Rn of the axial internal contact corresponding positions. The bearing is placed with the axis set vertical, and an upper cage 20 is picked up to separate the inner ring and the outer ring from each other. While the bearing is rotated with the axis set horizontal, the inner ring and the outer ring are separated from each other. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a parallel combination type double row angular contact ball bearing and a method for separating the same.

  Conventionally, a parallel angular single row has used two single row angular ball bearings combined in parallel. In this case, since the load needs to be evenly distributed to the two bearings, it is necessary to manage the difference width (DT clearance). Therefore, in Patent Documents 1 and 2, as shown in FIG. 13, the inner and outer rings 34 and 35 are integrated, and the inner and outer rings are double-row counterbore side raceways 36 and 37, and counter counterbore side raceway 38. , 39 are formed. That is, two rows of ball groups 32 and 33, an integrated inner ring 34 having two raceway surfaces on the outer periphery, which are adapted to roll the two rows of ball groups at the same pitch circle diameter, and two races of the inner ring. A parallel combination type double row angular ball bearing 30 is formed by an integral outer ring 35 having two raceway surfaces corresponding to the inner surface. Further, in order to increase the number of balls 32 and 33 and increase the load capacity, a counter bore (with a smaller or larger diameter than the inner / outer ring end side of the raceway surface on the inner / outer ring end side of one of the raceway surfaces 36 and 37 of the inner / outer ring) Shoulder shoulders) 42 and 43 are provided so that the counter bores of the inner and outer rings are arranged in the opposite direction. The axial internal contact line 51 of the parallel combination type double row angular ball bearing 30 is parallel to the left and right as shown in FIG. 13, and the direction is the left direction. For example, by combining these with two sets or tapered roller bearings, etc. It is used for supporting a pinion of a terminal reduction gear of an automobile as described in Patent Document 1.

Further, in assembling such a parallel combination type double row angular contact ball bearing, as shown in FIG. 14, the inner ring assembly 52 is held while holding the ball 32 by the cage 20 on the other raceway surface (counterbore side) 38 of the inner ring. Assemble as. On the other hand, the outer ring assembly 53 is assembled while holding the ball 33 by the cage 20 on the other raceway surface (on the counter-bore side) 39 of the outer ring. For example, the outer ring assembly 53 is moved in the direction of the arrow and inserted into the inner ring assembly 52 for assembly. By the way, as described in claims 2 and 3 of Patent Document 1, if the counter bores (shoulder shoulders) 42 and 43 and the balls 33 and 32 do not have an interference amount, assembly and disassembly are easy. . However, parallel type double-row angular contact ball bearings require adjustment of the inner and outer clearances by adjusting the race diameter and ball diameter of the outer and inner rings with respect to a set of bearings in the manufacturing process. For this reason, if there is no compatibility with combinations other than the combined parts and the disassembly is easy, it will be scattered during transportation and the like, making the correct combination difficult and management very complicated. On the other hand, if the counter bores (shoulder shoulders) 42 and 43 and the balls 33 and 32 have an interference amount, they are not separated. However, if the amount of interference is given, it cannot be simply assembled. Therefore, in Patent Document 1, the outer ring 35 is heated and expanded in the radial direction so that the counterbore and the ball do not interfere with each other. Further, the one disclosed in Patent Document 2 discloses an assembly in which the interference amount is made elliptical, the outer ring 35 is deformed by pressing, and the normal line of the ball is made elliptical to eliminate interference.
Japanese Utility Model Publication No. 05-066327 [Patent Document 1] Japanese Patent Laid-Open No. 61-184216 FIG.

  However, when machining a plurality of raceway surfaces into an integral inner / outer ring, there is a problem that the machining load resistance and the number of man-hours increase because of the use of an overall grinding wheel. Further, the cross-section of the raceway surfaces 36 and 37 on the side having the counter bores 42 and 43 of the plurality of raceway surfaces is approximately 1/4 to 1/8 arc, whereas the cross-section of the other track surface 38 and 39 is approximately 1/2 to. Since it is a 1/4 arc and the machining area is different by about twice, there is a problem that a grinding resistance difference occurs and the grinding accuracy is deteriorated. On the other hand, when assembling and disassembling, the outer ring is heated or deformed by a press, so that there is a problem that assembling and disassembling takes time, and considerable equipment is required and costs are increased. Furthermore, when assembling the bearing to the device / device, the outer ring side and the inner ring side may be assembled separately. In this case, it is almost impossible to heat the outer ring at the assembly site or to deform it with a press. As described in claims 2 and 3 of Patent Document 1, the amount of interference between the counterbore and the ball is eliminated. If the assembly / disassembly is facilitated, the outer ring side and the inner ring side may be separated at the time of transportation, and there is a problem that packing and management are troublesome.

  In view of the above-mentioned problems, an object of the present invention is to provide a parallel combination type double row angular contact ball bearing having a highly accurate raceway surface with low machining resistance. Furthermore, it is to provide a parallel combination type double row angular contact ball bearing which is easy to assemble and disassemble and which is not easily broken even during transportation.

  In the present invention, two rows of ball groups arranged at the same pitch circle diameter, and an integral inner ring having two raceway surfaces on the outer periphery, each of which is configured to roll with the same pitch circle diameter. A parallel combination type double-row angular contact ball bearing having an inner ring having two raceway surfaces corresponding to the two raceway surfaces of the inner ring, the inner ring end of one raceway surface of the inner ring A counter bore with a smaller diameter than the end of the raceway surface opposite the inner race is provided on the side of the raceway, and a relief portion is provided on the raceway side of the other raceway surface of the inner race, corresponding to the other raceway side of the inner race. A counter bore having a diameter larger than that of the outer ring end side of the raceway surface is provided on the outer ring end side of the one raceway surface of the outer ring, and a relief portion is provided on the one raceway side of the other raceway surface of the outer ring. To provide a parallel combination type double row angular contact ball bearing provided Ri was to solve the problems described above.

  That is, the inner and outer rings are integrated into a double row raceway surface, and the inner and outer ring counterbore counter bores are arranged in opposite directions on the other raceway surface on the side without the counterbore. Since the relief portion is provided on one of the raceway surfaces (counter bore side), the shape of the double-row raceway surfaces can be made substantially the same, and the resistance difference between the raceway surfaces is small or absent during processing. In use after assembly, the ball receives a force in an oblique direction, and contacts the rolling surface of the inner and outer rings opposite to the counter bore side and the corresponding rolling surface of the outer and inner rings to support the load. Therefore, even if the relief portion is provided, the bearing performance is not affected.

  Such a parallel combination type double row angular contact ball bearing having a relief portion may be provided with a counter bore similar to the conventional one, but in the invention according to claim 2, the diameter of one raceway bottom of the outer ring and the A parallel arrangement in which the difference between the diameter of the counter bore of the outer ring and the difference between the diameter of the counter bore of the inner ring and the diameter of one track bottom of the inner ring is made smaller than the radial gap between the ball group and the inner and outer ring raceway surfaces. Combined type double row angular contact ball bearing.

  That is, in the conventional one, the difference between the track bottom of the outer ring (inner ring) and the diameter of the counter bore, that is, the height of a part or all of the counter bore is made larger than the radial clearance between the inner and outer ring raceway surfaces of the ball. On the other hand, in the present invention described in claim 2, it is made smaller. As a result, the conventional product cannot be assembled and separated because it interferes with the ball and the counterbore as they are, so heating and deformation are required, whereas in the present invention, the ball and the counterbore are dimensioned. Therefore, the ball and the inner and outer rings can be easily assembled without any great resistance.

  On the other hand, in the present invention, the raceway is provided with a relief portion, and when the inner and outer rings are separated, some of the balls move to the relief portion due to gravity, friction, etc., and the moved ball, the relief portion and the corresponding raceway The gap with the surface disappears. As a result, a part of the ball does not interfere with the counterbore or is not easily separated due to the frictional resistance due to the wedge action, or is not separated. Thus, in the second aspect of the invention, assembly is easy and difficult to separate.

  As for the size of the relief portion, if it is too large, the overall bearing strength is weakened, and the opposite raceway surface cannot be secured. On the other hand, if it is too small, the machining allowance cannot be secured or it becomes easy to separate. Therefore, in the invention according to claim 3, the diameter of the boundary portion between the escape portion of the inner ring and the other raceway surface of the inner ring is larger than the other raceway bottom diameter of the inner race, and the ball and the inner race It is smaller than the diameter of the position corresponding to the axial internal contact with which the other raceway surface comes into contact, and the diameter of the boundary between the escape portion of the outer ring and the other raceway surface of the outer ring is smaller than the other track bottom diameter of the outer ring. A parallel combination type double row angular contact ball bearing having a diameter larger than a diameter corresponding to an axial internal contact position where the ball and the other raceway surface of the outer ring come into contact with each other is provided. In addition, the length should just have the length which can ensure a track surface in a longitudinal direction.

  In the second aspect of the present invention, when separating after assembling, the ball comes into contact with the escape portion as it is, and is difficult or cannot be separated due to a wedge action or the like. Accordingly, in the invention of claim 4, the parallel combination type double-row angular ball bearing according to claim 2 is placed with its axis vertical, and a cage for holding the upper ball group upward is picked up, and the inner ring Provided is a method for separating a parallel combination type double row angular contact ball bearing that separates the outer ring from the outer ring. Since the entire ball is lifted by the cage, the ball does not fall into the escape portion due to gravity. In addition, one of the inner ring and the outer ring (the one on which the counter bore is disposed on the lower side) is lifted together with the ball. Therefore, there is no wedge action, the radial clearance of the ball is maintained, and the counter bore does not interfere with the counter bore of the inner ring or outer ring on the upper side, so that the ball, cage, inner ring or outer ring is pulled up. Can do. Note that the cage only needs to be mounted as an assembly on the inner and outer rings without causing the balls to fall apart, and the shape and material of the cage are those used in conventional double-row angular ball bearings as described in the background art. It's okay.

  Furthermore, separation in a state of being arranged in the horizontal direction is also possible. Accordingly, in the invention described in claim 5, the parallel combination type double row angular contact member that separates the inner ring and the outer ring while rotating the shaft of the parallel combination type double row angular contact ball bearing described in claim 2 in a substantially horizontal direction. A ball bearing separation method was adopted. According to this, it is possible to release the axial movement of the ball to the escape portion by rotating it, reduce the wedge action and the resistance against the counter bore, and separate the inner ring and the outer ring.

  In the present invention, since the relief portion is provided on one raceway side of the other raceway surface on the side where the counterbore of the double row raceway surface is not present, turning or forging finishes the relief portion after the grinding step. The process load can be reduced, and furthermore, the raceway surface shape is made substantially the same, and the machining resistance difference is reduced, so that the grinding accuracy is improved.

  Further, in the invention described in claim 2, since the dimensional interference between the ball and the counterbore is eliminated and the assembly is facilitated, the outer and inner rings are not easily separated by the behavior of the escape portion and the ball. The present invention provides a bearing that can be easily assembled, is difficult to separate during transportation, and can separate the outer and inner rings by simple work. As a result, when using incompatible bearing outer and inner rings in the device, it is possible to maintain a pair reliably until just before the assembly, separate them during assembly, and assemble each into the device, making management easy. It became a thing. In the invention according to claim 3, a more preferable shape can be obtained, and assembly / disassembly is also reliable.

  Furthermore, in the inventions according to claims 4 to 5, the cage can be easily separated by pulling it up with the ball or moving it while rotating, and there is almost no separation during transportation. In addition, there are effects such as easy separation and assembly at the assembly site, and easy management and handling. Furthermore, since heating and pressing are not required, facilities are not required and cost is low. In the present invention, as long as the pitch circle diameters of the two rows of balls are the same, the balls are not limited to the same diameter, and the same effect can be obtained even when the ball diameters are different.

  Embodiments of the present invention will be described with reference to the drawings. 1 is a partial sectional view of a parallel combination type double row angular contact ball bearing of the present invention, FIG. 2 is a partial enlarged sectional view of a raceway surface of an outer ring, and FIG. FIG. 4A is a partially enlarged cross-sectional view showing the relationship between the counter bore and the ball, FIG. 4A is an explanatory view of the present invention, and FIG. In addition, in each figure including the figure mentioned later, the same code | symbol is attached | subjected similarly and some description is abbreviate | omitted. For the sake of explanation, the gaps and the like are exaggerated. As shown in FIG. 1, the parallel combination type double row angular contact ball bearing 1 of the present invention has two rows of ball groups 2 and 3 arranged at the same pitch circle diameter P, and each ball group rolls at the same pitch circle diameter. An integral inner ring 4 having two raceway surfaces 6 and 8 arranged on the outer periphery and an integral outer ring 5 having two raceway surfaces 7 and 9 corresponding to the two raceway surfaces of the inner ring on the inner periphery are provided. doing. A counter bore 12 having a smaller diameter is provided on the inner ring end side of one raceway surface 6 of the inner ring 4 than on the inner ring end side of the raceway surface. Furthermore, an escape portion 14 is provided on one raceway side of the other raceway surface 8 of the inner ring 4. A connecting portion 24 is formed following the escape portion 14, and one raceway surface 6 is formed at the end of the connecting portion. Similarly, a counter bore 13 having a diameter larger than that of the outer race end side of the raceway surface is provided on the outer race end side of one raceway surface 7 of the outer race 5 corresponding to the other raceway surface 8 side of the inner race 4, and is the same as the inner race. In addition, an escape portion 15 and a connection portion 25 are provided on one raceway surface 7 side of the other raceway surface 9 of the outer ring. When such a parallel combination type double row angular ball bearing 1 is assembled to a device or the like, the raceway surfaces 6, 7, 8, and 9 are paired in an oblique direction as in the prior art. In FIG. The axial internal contact lines 51, 51 that receive the light are parallel to the left and right, and the direction is the left direction.

  As shown in FIG. 2, the diameter Dn of the boundary portion 16 between the escape portion 14 of the inner ring 4 and the other raceway surface (counterbore side raceway surface) 8 of the inner race is larger than the other raceway bottom diameter dn of the inner race, It is made smaller than the diameter Rn of the position corresponding to the axial internal contact (the intersection of the axial internal contact line and the raceway surface) 18 where the ball 3 and the other raceway surface 8 of the inner ring come into contact with each other. Further, the diameter Dg of the boundary portion 17 between the escape portion 15 of the outer ring 5 and the other raceway surface 9 of the outer ring is smaller than the other raceway bottom diameter dg of the outer ring, and the ball 2 and the other raceway surface of the outer ring come into contact with each other. It is made larger than the diameter Rg of the axial internal contact portion position 19. The escape portions 14 and 15 connect the boundary portions 16 and 17 and the connection portions 24 and 25 in an oblique direction with straight lines or arcs. As shown in the figure, the escape portions 14 and 15 are arranged on the connection portions 24 and 25 side from the boundary portion. Further, as shown in FIG. 3, the difference between the diameter dg of one track bottom of the outer ring 5 and the diameter Rcg of the counter bore 13 of the outer ring, and the diameter Rcn of the counter bore of the inner ring and the diameter dn of one track bottom of the inner ring. , That is, the counter bore amount δ is smaller than the radial gap Δs between the ball groups 2 and 3 and the inner and outer ring raceway surfaces. In such a dimensional relationship, the balls 2 and 3 do not interfere with the counter bores 12 and 13 or have a low resistance.

  In grinding of the relief portions 14 and 15 of the inner and outer rings 4 and 5 having such a configuration, as shown in FIG. 4, the raceway groove of the outer ring 5 that has been pre-machined with a grinding wheel 32 formed into a predetermined raceway shape 31. 33 (shown exaggerated by bold lines) is pressed and ground. In the prior art shown in FIG. 4B, since there is no escape portion, the entire raceway groove without the counterbore 13 is processed, so there is a difference between the left and right loads, and the load is large. On the other hand, in the present invention shown in FIG. 4 (a), since the grinding wheel 32 does not contact the escape portion 15, both the raceway surfaces 7 and 9 can have the same shape. In addition, the load is reduced by the amount of the escape portion, the number of processing steps is reduced, and the accuracy is improved.

  Next, the assembly of the parallel combination type double row angular ball bearing 1 of the present invention will be described. FIG. 5 is an assembly explanatory view of the above-described parallel combination type double row angular ball bearing shown in FIG. 1, wherein (a) is an outer ring assembly (b) is an inner ring assembly, and (c) is another inner ring or outer ring side cage. FIG. FIG. 6 is an assembly explanatory diagram when the inner ring assembly is inserted with the counter bore side of the outer ring assembly facing upward, and FIG. 7 is the case when the outer ring assembly is inserted with the counter bore side of the inner ring assembly facing upward. FIG. First, in FIG. 5, the ball 3 and the cage 20 are mounted on the counter-bore side (the other) raceway surface 9 of the outer ring 5 so as not to be removed, and the outer ring assembly 53 shown in FIG. Next, the inner ring assembly 52 is formed by mounting the ball 2 and the cage 20 ′ on the counter-bore side (the other) raceway surface 8 of the inner ring 4 so as not to be detached. The cages 20 and 20 'are, for example, a general type of a crown type that is integrally formed of a resin as shown in FIG. 5C and has a plurality of pockets 20a in which a ball is stored and held circumferentially. May be used. However, the cage described in (c) is a different type from the cage described in (a) and (b). Next, as in the prior art, when the inner ring assembly 52 is inserted into the outer ring assembly 53, the balls 3 and 2 are pressed against the raceway surfaces 8 and 9, respectively, and the counterbore side raceway surfaces 6 and 7 and the axial internal contact portion position. Made to contact. Since the difference between the diameter of the counter bore and the diameter of the track bottom of the inner and outer rings, that is, the counter bore amount δ is smaller than the radial gap Δs between the ball groups 2 and 3 and the inner and outer ring raceway surfaces, the ball group does not interfere with the counter bore. Alternatively, the inner and outer ring assemblies 52 and 53 are assembled as parallel combination type double row angular ball bearings with low resistance.

  In the case shown in FIG. 6, when the outer ring assembly 53 is placed with the counter bore 13 side up and the inner ring assembly 52 is pushed in the direction of arrow A, the lower ball 3 is urged against the raceway surface 9 by its own weight. The upper ball 2 receives the resistance of the counter bore 13 and is urged to the raceway surface 8 so that the balls 3 and 2 easily pass through the counter bores 12 and 13 in both the upper and lower sides and can be easily assembled. Similarly, in the case shown in FIG. 7, when the inner ring assembly 52 is placed with the counter bore 12 side up, and the outer ring assembly 53 is pushed in the direction of arrow A, the lower ball 2 is caused by its own weight. The ball 3 on the upper side receives the resistance of the counterbore 12 and is urged to the raceway surface 9 so that the ball can easily pass through the counterbore and be assembled easily.

  After the inner and outer ring assemblies 52 and 53 are assembled, the separation of the bearings is hindered for the following reason, and the parallel combination type double row angular ball bearings can be conveyed without being separated. FIG. 8 is an explanatory view showing the influence of the external force when the outer ring is arranged on the lower side, and FIG. 9 is an explanatory view showing the influence of the external force when the inner ring is arranged on the lower side. In FIG. 8, when the outer ring 5 is placed down and the inner ring 4 is lifted in the direction of arrow A, the balls 2 and 3 try to hang downward in the vertical direction due to their own weight. At this time, in order to separate the bearings, the upper ball 2 of the inner ring assembly 52 passes through the counter bore 13 of the outer ring 5 and the counter bore 12 of the inner ring 4 moves the lower ball 3 of the outer ring assembly 53 upward. You have to go through. However, the upper ball 2 comes into contact with the relief portion 14 on the counter-bore side of the inner ring 4 and the ball 2 receives a force in the direction of arrow B spreading outward in the radial direction. As a result, the ball 2 and the counter bore side raceway surface 7 of the outer ring 5 are brought close to or in contact with each other, the radial gap is narrower or disappears than the normal radial gap, and the ball 2 cannot get over the counter bore 13 or comes out due to the wedge action. It becomes difficult. Therefore, the outer and inner rings cannot be separated. Considering only the lower ball 3, it is separable in dimension, but cannot be separated because the upper ball 2 does not come off.

  In FIG. 9, when the inner ring 4 is placed down and the outer ring 5 is lifted in the direction of arrow A, the balls 2 and 3 try to hang downward in the vertical direction due to their own weight. At this time, in order to separate the bearings, the ball 3 of the outer ring assembly 53 passes through the counter bore 12 of the inner ring 4 and the counter bore 13 of the outer ring 5 passes through the lower ball 2 of the inner ring assembly 52 upward. There must be. However, the upper ball 3 comes into contact with the clearance 15 of the counter-bore side track 9 of the outer ring 5 and the ball receives a narrowing force in the direction of arrow B inward in the radial direction. 8, the ball 3 and the inner ring raceway surface 6 on the counter bore side are close to or in contact with each other, the radial gap is narrower or disappears than the normal radial gap, and the ball 3 can get over the counter bore 12. It disappears or it becomes difficult to come off due to the wedge action. Therefore, the outer and inner rings are not separated regardless of the movement of the lower ball 2.

  Next, the case of disassembling will be described. FIG. 10 is an explanatory view showing a method for separating the cage by picking up the cage, and FIG. 11 is an explanatory view showing a method for separating the bearing while rotating. First, a method for picking up the cage 20 will be described. In FIGS. 8 and 9 described above, the ball cannot be disassembled because the balls 2 and 3 hang down due to their own weight and come into contact with the escape portions 14 and 15, thereby eliminating the radial gap and inhibiting the separation. Therefore, as shown in FIG. 10, when disassembling the outer ring in the direction of arrow A with the counter bore 13 of the outer ring 5 down, the cage 20 on the outer ring 5 side is picked up and held upward (in the direction of arrow C). The upper ball 3 is lifted upward (in the direction of arrow B) through the vessel. Thereby, the ball 3 is in contact with the counter-bore side raceway surface 9 of the outer ring 5 and moves upward while maintaining a radial play with the counterbore 12 side raceway surface 6 of the inner ring 4. Therefore, the counter bore 12 of the inner ring 4 is easily overcome by the amount of the radial gap that should be present. On the other hand, even if the lower ball 2 hangs down due to its own weight, it only comes into contact with the raceway surface 8 on the counter-counter side of the inner ring 4, so that it remains in the original radial gap, so it easily gets over the counter bore 13 of the outer ring 5. Therefore, the outer and inner rings can be separated. In addition, when arrange | positioned upside down with respect to FIG. 10, it can isolate | separate similarly, if the inner ring side holder is picked up.

  Next, a method for separating the bearing while rotating will be described. In the state where the axial direction of the bearing is directed to the vertical direction as shown in FIGS. 8 and 9, the ball falls into the escape portion even if the bearing is rotated, and it is difficult to disassemble the bearing. Therefore, as shown in FIG. 11, the shaft of the bearing 1 is approximately horizontal, and the outer ring 5 or the inner ring 4 of the bearing is rotated (arrow D). By rotating, the balls 2 and 3 rotate on the rolling surfaces 6, 7, 8 and 9, so that there is no drop into the escape portions 14 and 15, and a radial gap can be maintained. The outer and inner ring assemblies 52 and 53 can be separated by getting over. As described above, it is difficult to separate the inner and outer ring assemblies 52 and 53 simply by pulling them in the axial direction or rotating them, and the parallel combination type double row angular ball bearings do not fall apart during transportation. On the other hand, the inner and outer ring assemblies can be easily separated by a simple operation such as pulling together with the ball by a cage or rotating horizontally, etc., and handling is easy and easy when assembling the bearing into the equipment on site. Can be managed.

  In addition, although it has a relief part, when there is little or no counterbore amount, since the part which a ball | bowl catches is lose | eliminated, isolation | separation (detachment | attachment) is easy. This case is shown in FIG. In addition, about the same part as mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted. As shown in FIG. 12, even if the ball moves, the counter bore can be easily slipped through. FIG. 12 shows an example in which the escape portions 14 and 15 are once formed in a concave cross section from the boundary portion and then connected to the connection portions 24 and 25. Thus, it goes without saying that the shape of the escape portion has various forms.

It is a fragmentary sectional view of the parallel combination type double row angular contact ball bearing of the present invention. (A) of the present invention is a partially enlarged cross-sectional view of the raceway surface of the inner ring, and (b) is a partial enlarged cross-sectional view of the raceway surface of the outer ring. It is a partial expanded sectional view which shows the relationship between the counterbore of this invention and a ball | bowl. (A) is this invention, (b) is explanatory drawing of the grinding process of the conventional outer ring raceway surface. It is assembly explanatory drawing of the parallel combination type double row angular contact ball bearing of this invention shown in FIG. 1, (a) is an outer ring assembly (b) is an inner ring assembly, (c) is another example of the inner ring or outer ring side cage. FIG. It is assembly explanatory drawing of this invention in the case of putting an inner ring | wheel assembly so that the counterbore side of an outer ring | wheel assembly may become an upper side. It is assembly explanatory drawing of this invention in the case of placing an outer ring assembly so that the counterbore side of the inner ring assembly is on the upper side. It is explanatory drawing which shows the influence of external force when the outer ring | wheel of this invention is arrange | positioned below. It is explanatory drawing which shows the influence of external force when the inner ring | wheel of this invention is arrange | positioned below. It is explanatory drawing which shows the method of isolate | separating by picking up the holder | retainer of this invention. It is explanatory drawing which shows the method of isolate | separating, rotating the bearing of this invention. It is a fragmentary sectional view of the separation type parallel combination type double row angular contact ball bearing of the present invention. It is a fragmentary sectional view of the conventional parallel combination type double row angular contact ball bearing. It is assembly explanatory drawing of the conventional parallel combination type double row angular contact ball bearing.

Explanation of symbols

1,2,22 Parallel combination type double row angular contact ball bearings 2, 3 balls (group)
4 Inner ring 4a Inner ring outer periphery 5 Outer ring 5a Outer ring inner periphery 6 One raceway surface (counterbore side raceway surface on the inner race side)
7. One raceway surface (outer ring side counterbore side raceway surface)
8 The other raceway surface (Inner ring side counter-bore side raceway surface)
9 Other raceway surface (outer ring side counter-counter side raceway surface)
10 Inner ring end 11 Outer ring end 12 Counter bore (inner ring side)
13 Counterbore (outer ring side)
14 Escape part (inner ring side)
15 Escape part (outer ring side)
16 border (inner ring)
17 border (outer ring)
18 Axial internal contact equivalent position (inner ring)
19 Axial internal contact equivalent position (outer ring)
20, 20 'Cage dg Outer ring track bottom diameter dn Inner ring track bottom diameter Dg Outer ring boundary diameter Dn Inner ring boundary diameter P Pitch circle diameter Rg Outer ring axial inner contact equivalent diameter Rn Inner ring axial Diameter of position corresponding to internal contact δ Counter bore amount (difference between the diameter of one track bottom of the outer ring and the diameter of the counter bore of the outer ring, difference between the diameter of the counter bore of the inner ring and the diameter of one track bottom of the inner ring)
Δs Radial gap between balls and inner and outer ring raceways

Claims (5)

  Two rows of ball groups arranged at the same pitch circle diameter, an integral inner ring having two raceway surfaces on the outer periphery, each of which is configured to roll with the same pitch circle diameter, and two of the inner rings A parallel combination type double-row angular contact ball bearing having an inner ring having two raceway surfaces corresponding to two raceway surfaces on the inner ring end side of one raceway surface of the inner ring. A counter bore having a smaller diameter than the end of the inner ring on the surface is provided, a relief portion is provided on the one raceway side of the other raceway surface of the inner ring, and one of the outer rings corresponding to the other raceway side of the inner ring A counter bore having a larger diameter than the end of the raceway surface opposite the outer ring end is provided on the outer ring end side of the raceway surface, and a relief portion is provided on the one raceway side of the other raceway surface of the outer ring. Parallel combination type double-row angular contact ball bearing characterized by   The difference between the diameter of one track bottom of the outer ring and the diameter of the counter bore of the outer ring, and the difference between the diameter of the counter bore of the inner ring and the diameter of one track bottom of the inner ring are the ball group and the inner and outer rings. The parallel combination type double-row angular contact ball bearing according to claim 1, wherein the parallel combination type double-row angular contact ball bearing is smaller than a radial clearance with the raceway surface.   The diameter of the boundary portion between the inner ring escape portion and the other raceway surface of the inner ring is larger than the other raceway bottom diameter of the inner ring, which corresponds to the axial internal contact in which the ball and the other raceway surface of the inner ring come into contact with each other. A diameter of a boundary portion between the outer ring escape portion and the other raceway surface of the outer ring is smaller than the other raceway bottom diameter of the outer ring, and the ball and the other raceway surface of the outer ring. The parallel combination type double row angular ball bearing according to claim 1 or 2, wherein the diameter is larger than the diameter of the position corresponding to the axial internal contact.   A parallel combination type double-row angular ball bearing according to claim 2 is placed with its axis vertical, and a cage that holds the upper ball group upward is picked up to separate the inner ring and the outer ring. Separating method of parallel combination type double row angular contact ball bearing. A separation method of a parallel combination type double row angular ball bearing, wherein the inner ring and the outer ring are separated while rotating with the shaft of the parallel combination type double row angular ball bearing according to claim 2 rotated in a substantially horizontal direction.

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