JP2011007286A - Deep groove ball bearing and gear support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an easily assembled deep groove ball bearing capable of bearing a large thrust load, and preventing loosening of a retainer even when a large moment load is applied.SOLUTION: Heights of a shoulder 13a of one side of an outer ring 11 and a shoulder 23b of the other side of an inner ring 21 are provided higher than remaining shoulders 13b, 23a, and thrust force is supported by the shoulders 13a, 23b with higher heights to prevent running of a ball 31 on the shoulders 13a, 23b. An opposing pair of pocket pawls 44, 49 are formed at equal intervals in a circumferential direction on each of an axial one side part of an annular body in a first split retainer 41 and the axial other side part of a second split retainer 42, and pockets 45, 50 for ball retention are formed between each of the opposing pair of pocket pawls 44, 49. Engaging pawls 46, 51 are formed between adjacent pocket pawls 44, 49, the engaging pawls 46, 51 are engaged with engaging recessed parts 47, 52 formed on counterpart split retainers 41, 42, and separation of the first split retainer 41 and the second split retainer 42 in an axial direction is prevented.

Description

  The present invention relates to a deep groove ball bearing in which a ball is incorporated between an outer ring and an inner ring, and a gear support device using the deep groove ball bearing.

  As shown in FIG. 12, the rotation of the final drive gear 1 of the transmission is transmitted from the final driven gear 2 to the differential case 3 that supports the gear 2, and the rotation of the differential case 3 is transmitted from a pair of pinions 5 fixed to the pinion shaft 4. In the differential that is transmitted to the side gears 6a, 6b meshing with the left and right axles 7a, 7b that support the side gears 6a, 6b, the cylindrical portions 8a formed at both ends of the differential case 3, 8b is rotatably supported by a pair of bearings B supported by the housing 9.

  In the differential, since a helical gear is employed for the final driven gear 2 supported by the differential case 3, when the final driven gear 2 rotates, a thrust load is applied to the differential case 3.

  For this reason, it is necessary to use a bearing that can support both radial load and thrust load as the bearing B that supports the differential case 3.

  A tapered roller bearing has a large load capacity and can receive both a thrust load and a radial load. Therefore, it is suitable for a bearing for supporting the differential case 3. However, this tapered roller bearing has a large loss torque and a fuel loss. The problem that the amount of consumption increases. In order to reduce fuel consumption, it is preferable to use a deep groove ball bearing with a small loss torque.

  By the way, in a standard deep groove ball bearing, when an excessive thrust load is applied, there is a concern that the ball rides on the shoulder on the load side receiving the thrust load and the shoulder edge is damaged.

  In order to eliminate such inconvenience, in the deep groove ball bearing described in Patent Document 1, of the shoulders formed on both sides of the outer ring raceway groove and the inner ring raceway groove, the shoulder on the side receiving the thrust load. Is increased to prevent the ball from climbing and to suppress a decrease in the durability of the bearing.

JP 2000-145795 A

  By the way, in the deep groove ball bearing described in the above-mentioned Patent Document 1, a cage made of metal in which a pair of press-molded corrugated cages are coupled by rivets is adopted as a cage for holding the balls. There is a problem that it takes time to assemble the deep groove ball bearing.

  Here, as a cage, a crown-shaped cage made of a synthetic resin has been conventionally known, and by adopting the crown-shaped cage, the above problem can be solved, but a large moment load is generated. When loaded, the crown-shaped cage may fall off due to the delayed advance of the ball.

  Also, if the outer diameter surface is the same diameter throughout the axial direction and the inner diameter surface is the same diameter throughout the axial direction, the cage interferes with the higher shoulder and is damaged. There was a risk.

  An object of the present invention is to provide a deep groove ball bearing and a deep groove ball bearing that can receive a large thrust load and that are easy to assemble and that do not drop off even when a large moment load is applied. It is to provide a used gear support device.

  In order to solve the above problems, in the deep groove ball bearing according to the present invention, an outer ring having a raceway groove formed on the inner diameter surface, an inner ring having a raceway groove formed on the outer diameter surface, and a raceway groove of the outer ring, A ball assembled between the inner ring raceway grooves and a retainer for holding the balls. Of the total four shoulders located on both sides of the outer ring raceway groove and the inner ring raceway groove, the outer ring raceway groove In the deep groove ball bearing, the height of the shoulder on one side and the shoulder on the other side of the inner ring raceway groove is higher than the height of the shoulder on the other side of the outer ring raceway groove and one side of the inner ring raceway groove. A cylindrical first split cage made of synthetic resin, and a cylindrical second split cage made of synthetic resin fitted inside the first split cage, the first split cage and Each of the second split cages has an annular body, and one axial side surface of the annular body A pair of opposed pocket claws are formed at equal intervals, and a crown holding shape is provided with a ball holding pocket having a size of more than half a circle for punching the annular body between the opposed pair of pocket claws. The one split cage is inserted into the bearing from the shoulder side of the outer ring where the shoulder height is low, and the second split cage is inserted into the bearing from the side where the shoulder height of the inner ring is low so that the opening end of the pocket is in the opposite direction. It is a combination that is suitable, and a connecting means is provided between the first split cage and the second split cage by engaging the two cages so that the two cages are not separated in the axial direction. The configuration was adopted.

  When assembling the deep groove ball bearing having the above-described configuration, the required number of balls are assembled between the outer ring raceway groove and the inner ring raceway groove, and the plurality of balls are arranged at equal intervals in the circumferential direction. The first split cage is inserted into the bearing from one side so that the ball is accommodated in a pocket formed in the first split cage, and the bearing is inserted from the other side between the outer ring and the inner ring. The second divided holder is inserted inside the second divided holder so that the ball is accommodated in a pocket formed in the second divided holder, and the second divided holder is fitted into the first divided holder.

  As described above, by fitting the second divided cage into the first divided cage, the connecting means are engaged with each other so that the first divided cage and the second divided cage are not separated in the axial direction. As a result, the assembly of the deep groove ball bearing is completed. At this time, the first split cage and the second split cage having different diameters are asymmetrical combinations in which both end portions are shifted in the axial direction (left-right direction), and the rear end portion in the insertion direction when assembled is the shoulder of the outer ring. Since it is built in between the shoulders of the inner ring, it does not interfere with the shoulders of the inner and outer rings.

  In the assembly of the deep groove ball bearing as described above, the pocket of the first split cage and the pocket of the second split cage have a pair of opposed pocket claws that embed the ball at the open end, and the first split cage The pair of opposed pocket claws and the pair of opposed pocket claws provided on the second divided cage are combined in opposite directions, and in the combined state, the first divided holder and the second divided cage Are connected in a non-separated state in the axial direction by the connecting means. For this reason, even if a large moment load is applied and the ball is delayed or advanced, the cage does not fall off.

  In addition, the pocket for holding the ball is a pocket of a size larger than a half circle formed in the first divided cage and a pocket of a size larger than a half circle formed in the second divided cage. Therefore, the ball guide surface is wide and a highly strong cage can be obtained.

  Here, as the connecting means, an inward engagement claw is provided between the pocket claws of the adjacent pockets of the first divided holder, and an outward engagement claw is provided between the pocket claws of the adjacent pockets of the second divided holder. Engaging the engaging claw of the first split cage with the engaging recess formed in the outer diameter surface of the second split cage, and engaging the engaging claw of the second split cage with the first split cage. What consists of the structure engaged with the engagement recessed part formed in the internal-diameter surface is employable.

  In adopting the connecting means as described above, the number of the engagement portions of the engagement claw and the engagement recess is three or more, so that the first divided holder and the second divided holder are more reliably coupled. be able to.

  In addition, by setting the circumferential clearance formed between the engaging claw and the engaging recess larger than the circumferential pocket clearance formed between the ball and the pocket, a large moment load is applied and the ball is delayed. Even if the first split cage and the second split cage rotate relative to each other, the engaging claws do not come into contact with the opposite side surfaces in the circumferential direction of the engaging recess, and the engaging claws are damaged. It can be effective for prevention.

  Further, the first split retainer and the second split retainer are formed by making the axial clearance formed between the engaging claw and the engaging recess larger than the axial pocket clearance formed between the ball and the pocket. When the axial force in the direction separating from each other is applied, the inner surfaces of the pair of opposing pocket claws abut against the outer peripheral surface of the ball, and the engaging claws abut against the axial end surface of the engaging recess. The effect of preventing damage to the engaging claws can be obtained.

  When assembling a deep groove ball bearing to a gear support device using a helical gear, the inner shoulder is located on the helical gear side, and the thrust load generated by torque transmission to the helical gear is applied to the outer and inner rings. Receiving with a high shoulder to prevent the ball from climbing.

  Here, if there is an error in the mounting direction of the deep groove ball bearing, the thrust load cannot be received, and the ball may ride on the shoulder with a low height. Therefore, if an identification display portion indicating the thrust load receiving side is provided on at least one width surface side of the outer ring, the inner ring, the first divided cage, and the second divided cage, incorrect assembly can be prevented and the gear can be prevented. The assemblability of the support device can be improved. The identification display section may be displayed in color or may be by marking.

  Since the deep groove ball bearing is lubricated with lubricating oil, the first split cage and the second split cage are preferably formed of a synthetic resin excellent in oil resistance. Examples of such a resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS). Among these resins, polyphenylene sulfide (PPS) has excellent oil resistance compared to other resins, and therefore, considering the oil resistance, it is most preferable to use polyphenylene sulfide (PPS).

  In view of the price of the resin material, it is preferable to use polyamide 66 (PA66), which may be determined appropriately according to the type of the lubricating oil.

In the deep groove ball bearing according to the present invention, if the height of the high shoulder becomes larger than necessary, the ball cannot be assembled, and if it is too low, the ball rides up. For this reason, when the shoulder height of a high shoulder is H ₁ and the ball diameter is d, the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d is 0.25-0. A range of 50 is preferable.

  In the gear support device according to the present invention, the shaft provided with the helical gear is rotatably supported by the first bearing arranged on one side of the helical gear and the second bearing arranged on the other side of the helical gear. In the gear support device in which the thrust force applied to the shaft when the helical gear rotates in one direction is supported by the first bearing, the first bearing and the second bearing described above according to the present invention. Deep groove ball bearings were used.

  In this case, the deep groove ball bearing is designed so that the high shoulder of the inner ring is located on the helical gear side so that the thrust load applied to the shaft by the rotation of the helical gear is received by the high shoulders of the inner ring and the outer ring. To do.

  In the gear support device described above, the deep groove ball bearing according to the present invention is used for both the first bearing and the second bearing, but the second groove bearing according to the present invention is used for the first bearing, You may make it use a cylindrical roller bearing for a bearing. Further, an angular ball bearing or a tapered roller bearing may be used as the first bearing, and a deep groove ball bearing according to the present invention may be used as the second bearing.

  In either case, the deep groove ball bearing according to the present invention is built in such that the shoulder with a high height of the inner ring is located on the helical gear side.

  As described above, by supporting the shaft rotatably using the deep groove ball bearing according to the present invention, the loss torque is small, the shaft can be rotated smoothly, and the effect of reducing fuel consumption can be obtained. it can. Further, the thrust load applied to the shaft can be received by the deep groove ball bearing, and the ball is not climbed, so that the power can be transmitted reliably.

  As described above, in the deep groove ball bearing according to the present invention, of the four shoulders located on both sides of the outer ring raceway groove and the inner ring raceway groove, the outer ring raceway groove on one side and the inner ring raceway groove Since the height of the shoulder on the other side is higher than the height of the remaining shoulders, it can receive a radial load and a relatively large thrust load. For this reason, it can be incorporated into a bearing device where a tapered roller bearing is required, and the incorporation into the bearing device can reduce torque loss and achieve low fuel consumption.

  Also, a ball is assembled between the outer ring and the inner ring, the first split cage is inserted from one side of the outer ring and the inner ring, and the second split cage is inserted from the other side to the first split. Since the deep groove ball bearing can be assembled by fitting the second divided cage into the cage, the assembly is easy.

  Further, the pocket of the first split cage and the pocket of the second split cage have a pair of opposing pocket claws that embed the ball at the open end, and the pair of opposing pocket claws formed on the first split cage, The pair of opposed pocket claws provided in the second split cage are combined in a direction opposite to each other, and in the combined state, the connecting means engages to connect the first split cage and the second split cage in the axial direction. Because of non-separation, even if a large moment load is applied and the ball is delayed or advanced, the first split cage and the second split cage will not be separated in the axial direction, and the cage will fall off. It can be effective for prevention.

  Further, in the gear support device according to the present invention, since the shaft is supported using the deep groove ball bearing, torque loss can be reduced, and an effect can be achieved in reducing fuel consumption.

Longitudinal front view showing an embodiment of a deep groove ball bearing according to the present invention The right view which shows a part of cage | basket shown in FIG. The left view which shows a part of cage shown in FIG. The top view which shows a part of 1st division holder and 2nd division holder The top view which shows the pocket clearance of the circumferential direction in the state which built the ball | bowl in the pocket of the 1st division | segmentation holder | retainer shown in FIG. The top view which shows the pocket clearance of the axial direction in the state which integrated the ball | bowl in the pocket of the 1st division | segmentation holder | retainer shown in FIG. Sectional drawing which expands and shows the coupling | bond part of the 1st division | segmentation holder | retainer of FIG. 1, and a 2nd division | segmentation holder | retainer Sectional drawing which shows an example of a gear support apparatus Sectional drawing which shows the other example of a gear support apparatus Sectional drawing which shows the further another example of a gear support apparatus Sectional drawing which shows the further another example of a gear support apparatus Cross-sectional view showing differential

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. As shown in FIG. 1, in the deep groove ball bearing A, a ball 31 is incorporated between a raceway groove 12 formed on the inner diameter surface of the outer ring 11 and a raceway groove 22 provided on the outer diameter surface of the inner ring 21. Is held by the cage 40.

  Of the pair of shoulders 13a and 13b formed on both sides of the raceway groove 12 of the outer ring 11, the height of the shoulder 13a located on one side of the raceway groove 12 is higher than the height of the shoulder 13b located on the other side. It has become. On the other hand, of the pair of shoulders 23a and 23b formed on both sides of the raceway groove 22 of the inner ring 21, the height of the shoulder 23b located on the other side of the raceway groove 22 is higher than the height of the shoulder 23a located on one side. It is high.

  Here, the shoulder heights of the low shoulders 13b and 23a are the same as the shoulders of the standard depth groove ball bearings, but may be lower than the shoulder heights of the standard depth groove ball bearings. .

  For convenience of explanation, the high shoulders 13a and 23b are referred to as thrust load side shoulders 13a and 23b, and the low shoulders 13b and 23a are referred to as thrust non-load side shoulders 13b and 23a.

Assuming that the shoulder height of the shoulders 13a and 23b on the thrust load side is H ₁ and the ball diameter of the ball 31 is d, the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter of the ball d is H ₁ / d. = 0.25 to 0.50.

  The cage 40 includes a first divided cage 41 and a second divided cage 42 fitted inside the first divided cage 41.

  As shown in FIGS. 1 to 4, the first split holder 41 has a pair of opposed pocket claws 44 formed on the one side surface in the axial direction of the annular body 43 at equal intervals in the circumferential direction. It is made of a synthetic resin molded product provided with pockets 45 having a size of more than a half circle punching through the annular body 43 therebetween, and the inner diameter of the annular body 43 is substantially equal to the pitch circle diameter (PCD) of the balls 31. The outer diameter is set within the range of the inner diameter of the shoulder 13a where the height of the outer ring 11 is high and the inner diameter of the shoulder 13b where the height of the outer ring 11 is low. ing.

  On the other hand, the second split holder 42 has a pair of opposed pawls 49 formed on the other side surface in the axial direction of the annular body 48 at equal intervals in the circumferential direction, and the annular body 48 is sandwiched between each pair of opposed pocket claws 49. The molded body is made of a synthetic resin provided with a pocket 50 having a size larger than a half circle to be extracted. The outer diameter of the annular body 48 is substantially equal to the pitch circle diameter (PCD) of the ball 31 and the inner diameter is the inner ring 21. The outer diameter of the shoulder 23b having a high height is within the range of the outer diameter of the shoulder 23a having a low height. The second split cage 42 can be inserted into the bearing from the low shoulder 23a side, and can be fitted inside the first split cage 41.

  Between the first divided holder 41 and the second divided holder 42, there is provided a connecting means X that is non-separated in the axial direction in a fitted state that fits inside and outside. The connecting means X is provided with an inward engagement claw 46 between the pocket claws 44 of the adjacent pockets 45 of the first divided holder 41, and on the inner surface of the annular body 43 on the same axis as the engagement claw 46. A groove-like engagement recess 47 is formed in the second partition holder 42, an outward engagement claw 51 is provided between the pocket claws 49 of the adjacent pockets 50 of the second divided holder 42, and the outer diameter surface of the annular body 48 is An engagement recess 52 is formed on the same axis as the engagement claw 51, and the engagement claw 46 of the first split holder 41 and the engagement recess 52 of the second split holder 42 are engaged, and the second split holding is performed. The first split holder 41 and the second split holder 42 are not separated in the axial direction by the engagement of the engaging claw 51 of the holder 42 and the engaging recess 47 of the first split holder 41. Yes.

  Here, since the 1st division | segmentation holder | retainer 41 and the 2nd division | segmentation holder | retainer 42 are exposed to the lubricating oil which lubricates a deep groove ball bearing, it is made to use the synthetic resin excellent in oil resistance. Examples of such a synthetic resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS). These resins may be selected and used according to the type of lubricating oil.

  The deep groove ball bearing shown in the embodiment has the above-described structure. When the deep groove ball bearing is assembled, the inner ring 21 is inserted inside the outer ring 11, and the race groove 22 of the inner ring 21 and the race groove of the outer ring 11 are inserted. A required number of balls 31 are assembled between 12.

  At this time, the inner ring 21 is offset in the radial direction with respect to the outer ring 11, a part of the outer diameter surface of the inner ring 21 is brought into contact with a part of the inner diameter surface of the outer ring 11, and 180 degrees in the circumferential direction from the contact part. A crescent-shaped space is formed at a position deviated, and the ball 31 is assembled from one side of the space.

Upon incorporation of the balls 31, when the shoulder height H ₁ of the thrust load side of the shoulder 23b of the thrust load side of the shoulder 13a and the inner ring 21 of the outer ring 11 is higher than necessary, to inhibit the incorporation of the balls 31 However, in the embodiment, since the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d of the ball 31 does not exceed 0.50, the gap between the outer ring 11 and the inner ring 21 is The ball 31 can be reliably assembled.

  After the ball 31 is assembled, the center of the inner ring 21 is made to coincide with the center of the outer ring 11 and the balls 31 are arranged at equal intervals in the circumferential direction, and the outer ring 11 and the inner ring are arranged from one side of the shoulder 13b on the thrust non-load side of the outer ring 11. The first divided holder 41 is inserted between the first divided holder 41 so that the balls 31 fit into the pockets 45 formed in the first divided holder 41.

  Further, the second split cage 42 is inserted between the outer ring 11 and the inner ring 21 from one side of the shoulder 23a on the thrust non-load side of the inner ring 21, and the ball 31 is placed in the pocket 50 formed in the second split cage 42. The second split holder 42 is fitted into the first split holder 41 by being inserted.

  As described above, the engagement claws formed in the respective divided holders 41 and 42 by fitting the second divided holder 42 in the first divided holder 41 as shown in FIGS. 46 and 51 are engaged with engaging recesses 47 and 52 provided in the other split cage, and the assembly of the deep groove ball bearing is completed.

  As described above, after the ball 31 is assembled between the raceway groove 12 of the outer ring 11 and the raceway groove 22 of the inner ring 21, the first split holder 41 and the second split hold are internally provided from both sides between the outer ring 11 and the inner ring 12. The deep groove ball bearing can be assembled by a simple operation of inserting the second holder 42 and fitting the second divided holder 42 into the first divided holder 41.

  In FIG. 1, the height of the low-thrust shoulders 13b and 23a on the non-load side is the same as the shoulder of the standard deep groove ball bearing, but lower than the shoulder height of the standard deep groove ball bearing. Also good.

  When the height of the shoulders 13b and 23a on the thrust non-load side is made lower than the height of the shoulder of the standard type deep groove ball bearing, the thickness in the radial direction of the first split cage 41 and the second split cage 42 is reduced accordingly. Since the thickness can be increased, the strength of the cage 40 can be increased.

Here, the lower than necessary height of thrust non-load side of the shoulder 13b and 23a, because the run-up of the ball 31 may occur, for shoulder height H ₂ of the shoulder 13b of the outer ring 11, balls 31 The ratio H ₂ / d of the shoulder height H ₂ to the sphere diameter d is 0.09 to 0.50, while the shoulder height H ₃ of the shoulder 23 a of the inner ring 21 is relative to the sphere diameter of the ball 31. The ratio H ₃ / d of the shoulder height H ₃ is preferably in the range of 0.18 to 0.50.

  FIG. 8 shows a case where cylindrical portions 8a and 8b as shafts formed at both ends of the differential case 3 shown in FIG. 12 are supported using the deep groove ball bearing A shown in the embodiment. When supporting the cylindrical portions 8a and 8b, the deep groove ball bearing A is assembled so that the shoulder 23b on the load side of the inner ring 21 is located on the final driven gear 2 side.

  In the gear support device as described above, when the differential case 3 rotates in the forward traveling direction of the vehicle by torque transmission from the final drive gear 1, a thrust force is applied to the differential case 3 by the rotation of the final driven gear 2 formed of a helical gear. The thrust force is supported by the thrust load side shoulder 23b of the inner ring 21 and the thrust load side shoulder 13a of the outer ring 11 in the deep groove ball bearing A on the left side of FIG.

  At this time, a thrust force is also applied to the ball 31, and when the thrust load side shoulder 23b of the inner ring 21 and the thrust load side shoulder 13a of the outer ring 11 are lower than necessary, the ball 31 rides on the shoulders 13a, 23b, There is a possibility of damaging the edges of the shoulders 13a and 23b.

In the embodiment, since the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d of the ball 31 is set to 0.25 or more, the riding of the ball 31 can be reliably prevented.

  For comparison, a standard deep groove ball bearing 6208C having an outer diameter of the inner ring of φ53.1 mm and an inner diameter of the outer ring of φ68.1 mm is used as a comparative product, and the thrust load side of the inner ring is based on the standard deep groove ball bearing. A deep groove ball bearing in which the outer diameter of the shoulder of the outer ring is changed from φ53.1 mm to φ56.6 mm and the inner diameter of the shoulder on the thrust load side of the outer ring is changed from φ68.1 mm to φ65.5 mm. When the allowable thrust load was measured, the deep groove ball bearing of the present invention showed a value higher by 305% than the comparative deep groove ball bearing. In addition, the outer diameter of the shoulder of the inner ring where the thrust load (axial load) is not applied is changed from the standard φ53.1 mm to φ51.9 mm, and the inner diameter of the shoulder of the outer ring where the axial load is not applied is changed to the standard Even when the diameter was changed from φ68.1 mm to φ70.4 mm, even when the basic statically constant load Co was applied to the bearing, no shoulder climbing occurred.

When the differential case 3 rotates in the backward running direction of the vehicle, the thrust force applied to the differential case 3 is the thrust load side shoulder 23b of the inner ring 21 and the thrust load side of the outer ring 11 in the deep groove ball bearing A on the right side of FIG. Is supported by the shoulder 13a. Also in this case, since the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d of the ball 31 is set to 0.25 or more, it is possible to reliably prevent the ball 31 from climbing.

  Here, if there is an error in the mounting direction of the deep groove ball bearing A, there is a possibility that the ball 31 may get on the shoulders 13b and 23a having a low height without receiving a thrust load. Therefore, as shown in FIG. 1, when an identification display portion 55 indicating a thrust load receiving side is provided on at least one width surface side of the outer ring 11, the inner ring 21, the first divided holder 41, and the second divided holder 42, Incorrect assembly can be prevented, and the assembly of the gear support device can be improved. The identification display section may be displayed in color or may be by marking.

  In FIG. 8, each of the cylindrical portions 8a and 8b at both ends of the differential case 3 is supported by the deep groove ball bearing A shown in FIG. 1, but as shown in FIG. 9, one cylindrical portion 8a is shown in FIG. You may make it support by the deep groove ball bearing A to show and to support the other cylinder part 8b with the cylindrical roller bearing C. FIG.

  In the gear support device in which the thrust force is always generated in one direction, as shown in FIG. 9, the deep groove ball bearing according to the present invention is disposed on the thrust load receiving side, and the cylindrical roller bearing is disposed on the radial load receiving side. It is good to arrange.

  Further, as shown in FIG. 10, when the vehicle is traveling forward, an angular ball bearing D may be used for one bearing that receives a thrust force, and a deep groove ball bearing A shown in FIG. 1 may be used for the other bearing. .

  Furthermore, as shown in FIG. 11, when the vehicle is traveling forward, a tapered roller bearing E may be used for one bearing that receives a thrust force, and a deep groove ball bearing A shown in FIG. 1 may be used for the other bearing. .

  In the case of a gear support device in which the direction of thrust force (gear load) is opposite when the vehicle is reverse, as shown in FIG. 10, the radial load receiving side during forward movement is the deep groove ball bearing according to the present invention, and the thrust load is The receiving side may be an angular ball bearing, or, as shown in FIG. 11, the radial load receiving side during advance may be a deep groove ball bearing according to the present invention, and the thrust load receiving side may be a tapered roller bearing. .

  As shown in FIGS. 8 to 11, by supporting at least one of the cylindrical portions 8 a and 8 b with the deep groove ball bearing A shown in FIG. 1, compared to a case where both of the cylindrical portions are supported with tapered roller bearings. Torque loss can be reduced, and the effect of reducing fuel consumption can be obtained.

  In the deep groove ball bearing shown in the embodiment, a pair of opposed pocket claws 44 and 49 for embedding the ball 31 at the open ends of the pocket 45 of the first divided holder 41 and the pocket 50 of the second divided holder 42 are provided. The pair of opposed pocket claws 44 formed in the first divided holder 41 and the pair of opposed pocket claws 49 provided in the second divided holder 42 are combined to face in opposite directions. Since the claws 46 and 51 are engaged with the engagement recesses 47 and 52 and the first divided holder 41 and the second divided holder 42 are not separated in the axial direction, a large moment load is applied to the ball. Even if the delay or advance of 31 occurs, the retainer 40 does not fall off.

Here, as shown in FIGS. 4 and 5, the clearance δ ₁ of the circumferential clearance 60 formed between the engaging claws 46, 51 and the engaging recesses 47, 52 is set between the ball 31 and the pockets 45, 50. By making it larger than the clearance amount δ _{2 of the} formed pocket clearance 61 in the circumferential direction, a large moment load is applied and the ball 31 is delayed and advanced, and the first split cage 41 and the second split cage 42. The engagement claws 46 and 51 do not come into contact with the opposite sides of the engagement recesses 47 and 52 in the circumferential direction even if the rotation of the engagement claws 46 and 51 is relatively rotated. be able to.

Further, as shown in FIGS. 6 and 7, a clearance δ ₃ of the axial clearance 62 formed between the engaging claws 46 and 51 and the engaging recesses 47 and 52 is formed between the ball 31 and the pockets 45 and 50. When the axial force in the direction away from the first split holder 41 and the second split holder 42 is applied to the first split holder 41 and the second split holder 42 by making the clearance larger than the clearance amount δ ₄ of the pocket pocket 63 in the axial direction. The inner surfaces of the pocket claws 44 and 49 are not in contact with the outer peripheral surface of the ball 31, and the engagement claws 46 and 51 are not in contact with the axial end surfaces of the engagement recesses 47 and 52. , 51 can be effective in preventing damage.

  8 to 11, at least one of the cylindrical portions 8 a and 8 b at both ends of the differential case 3 is rotatably supported by the deep groove ball bearing A shown in FIG. 1, but the support target component is not limited to the differential case 3. . For example, an input shaft, a counter shaft, or an output shaft of the transmission may be used.

11 outer ring 12 raceway groove 13a shoulder 13b shoulder 21 inner ring 22 raceway groove 23a shoulder 23b shoulder 31 ball 40 retainer 41 first divided retainer 42 second divided retainer 43 annular body 44 pocket claw 45 pocket 46 engagement claw 47 engagement Recess 48 Annular body 49 Pocket claw 50 Pocket 51 Engaging claw 52 Engaging recess 60 Circumferential clearance 61 Circumferential pocket clearance 62 Axial clearance 63 Axial pocket clearance A Deep groove ball bearing C Cylindrical roller bearing D Angular contact ball bearing E Tapered roller bearing

Claims (12)

An outer ring having a raceway groove formed on the inner diameter surface, an inner ring having a raceway groove formed on the outer diameter surface, a ball assembled between the raceway groove of the outer ring and the raceway groove of the inner ring, and a cage for holding the ball The total height of the shoulders on one side of the outer ring raceway groove and the shoulders on the other side of the inner ring raceway groove among the total four shoulders located on both sides of the outer ring raceway groove and the inner ring raceway groove In deep groove ball bearings that are higher than the shoulder on the other side of the groove and the shoulder on one side of the inner ring raceway groove,
The cage includes a cylindrical first divided cage made of synthetic resin, and a synthetic resin cylindrical second divided cage fitted inside the first divided cage. Each of the split cage and the second split cage has an annular body, and a pair of opposing pocket claws are formed at equal intervals on one side surface in the axial direction of the annular body. The crown is provided with a ball holding pocket with a size of more than a half circle that punches through the annular body, and the first split cage is inserted into the bearing from the shoulder side where the shoulder height of the outer ring is low, The two split cage is inserted into the bearing from the lower shoulder height side of the inner ring so that the opening end of the pocket faces in the opposite direction, and between the first split cage and the second split cage, A connecting means for engaging both the cages by fitting them so that the two cages are not separated in the axial direction. Deep groove ball bearings, characterized in that digit.   The connecting means has an inward engagement claw between the pocket claws of the adjacent pockets of the first divided holder, and an outward engagement claw between the pocket claws of the adjacent pockets of the second divided holder. Engaging the engaging claw of the first split cage with the engaging recess formed in the outer diameter surface of the second split cage, and engaging the engaging claw of the second split cage with the first split cage. The deep groove ball bearing according to claim 1, wherein the deep groove ball bearing is configured to engage with an engaging recess formed on an inner diameter surface.   The deep groove ball bearing according to claim 2, wherein the number of engagement portions of the engagement claw and the engagement recess is three or more.   The deep groove ball bearing according to claim 2 or 3, wherein a circumferential clearance formed between the engaging claw and the engaging recess is larger than a circumferential pocket clearance formed between the ball and the pocket.   The deep groove ball bearing according to any one of claims 2 to 4, wherein an axial clearance formed between the engaging claw and the engaging recess is larger than an axial pocket clearance formed between the ball and the pocket. .   The deep groove ball bearing according to any one of claims 1 to 5, wherein the first divided cage and the second divided cage are made of one of polyamide 46, polyamide 66, and polyphenylene sulfide.   The depth according to any one of claims 1 to 6, wherein an identification display portion indicating a thrust load receiving side is provided on at least one width surface side of the outer ring, the inner ring, the first divided cage, and the second divided cage. Ball bearings. When the shoulder height of the high shoulder is H ₁ and the ball diameter is d, the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d is 0.25 to 0.50. The deep groove ball bearing according to any one of claims 1 to 7, which is a range. A shaft provided with a helical gear is rotatably supported by a first bearing arranged on one side of the helical gear and a second bearing arranged on the other side of the helical gear, and the helical gear rotates in one direction. In a gear support device that supports the thrust force sometimes applied to the shaft by the first bearing,
The said 1st bearing and the 2nd bearing consist of the deep groove ball bearing as described in any one of Claims 1 thru | or 8, and the shoulder with the high height of the said inner ring faces the said helical gear with the deep groove ball bearing. A gear support device characterized by being assembled. A shaft provided with a helical gear is rotatably supported by a first bearing arranged on one side of the helical gear and a second bearing arranged on the other side of the helical gear, and the helical gear rotates in one direction. In a gear support device that supports the thrust force sometimes applied to the shaft by the first bearing,
The first bearing is a deep groove ball bearing according to any one of claims 1 to 8, the second bearing is a cylindrical roller bearing, and the deep groove ball bearing is formed at a height of the inner ring. A gear support device characterized in that a high shoulder is set to face the helical gear. A shaft provided with a helical gear is rotatably supported by a first bearing arranged on one side of the helical gear and a second bearing arranged on the other side of the helical gear, and the helical gear rotates in one direction. In a gear support device that supports the thrust force sometimes applied to the shaft by the first bearing,
One of the first bearing and the second bearing comprises the deep groove ball bearing according to any one of claims 1 to 8, the other comprises an angular ball bearing, and the deep groove ball bearing is disposed at a height of the inner ring. A gear support device, characterized in that a tall shoulder faces the helical gear. A shaft provided with a helical gear is rotatably supported by a first bearing arranged on one side of the helical gear and a second bearing arranged on the other side of the helical gear, and the helical gear rotates in one direction. In a gear support device that supports the thrust force sometimes applied to the shaft by the first bearing,
The first bearing is an angular ball bearing or a tapered roller bearing, the second bearing is a deep groove ball bearing according to any one of claims 1 to 8, and the deep groove ball bearing is connected to the inner ring. A gear support device characterized in that the shoulder having a high height is assembled to face the helical gear.

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