JP6267851B2 - Deep groove ball bearing and bearing device - Google Patents

Description

  The present invention relates to a deep groove ball bearing and a bearing device using the deep groove ball bearing.

  The input shaft and the output shaft are arranged on the same axis, the countershaft is provided in parallel to both axes, and a plurality of gear-type reduction gears with different gear ratios are provided between the two parallel axes to rotate the input shaft. In a transmission that shifts to multiple stages and outputs from the output shaft, a helical gear is generally used for the gear-type reduction gear, so input torque is transmitted from the input shaft to the output shaft. A thrust force is applied to each of the shaft, the output shaft, and the counter shaft.

  For this reason, it is necessary to use a bearing that can support both a radial load and a thrust load as a bearing that supports the input shaft, the output shaft, and the counter shaft.

  Tapered roller bearings are suitable for transmission bearings because they have a large load capacity and can receive both thrust loads and radial loads. However, in the tapered roller bearing, there is a problem that the loss torque is large and the amount of fuel consumption increases. In order to reduce fuel consumption, there are many cases where deep groove ball bearings with less loss torque are used.

  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 load-side shoulder 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 2011-7286 A

  By the way, in the deep groove ball bearing described in the above-mentioned Patent Document 1, the height of the shoulder on the side receiving the thrust load among the pair of shoulders formed on both sides of the outer ring raceway groove and the inner ring raceway groove is a standard type. Since the height of the shoulder of the outer ring and the inner ring in the deep groove ball bearing is set higher, the groove depth of the raceway groove becomes deeper.

  For this reason, when a deep groove ball bearing is used for a transmission, if foreign matter such as abrasion powder generated by gear wear enters the outer ring raceway groove and the inner ring raceway groove, the foreign matter stays in the bearing. It is hard to be discharged from the inside, there is a possibility of damaging the rolling surface of the outer ring and the inner ring by the biting of the foreign matter, improve the discharge of intruding foreign matter, prevent the rolling surface damage due to the biting of foreign matter, The point which should be improved in suppressing the fall of durability was left.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a deep groove ball bearing and a bearing device that are capable of improving the discharge of invading foreign matter and preventing the rolling surface from being damaged by the foreign matter being caught.

In order to solve the above problems, in the deep groove ball bearing according to the present invention, a ball is incorporated between the raceway groove formed on the inner diameter surface of the outer ring and the raceway groove formed on the outer diameter surface of the inner ring, and the ball Of a total of four shoulders, a pair of shoulders formed on both sides of the outer ring raceway groove and a pair of shoulders formed on both sides of the inner ring raceway groove, The shoulder height of the other side of the inner ring raceway groove is set higher than the shoulder height of the other side of the outer ring raceway groove and the shoulder of one side of the inner ring raceway groove, and the shoulder height of the higher shoulder is set to H _1. When the ball diameter is d, the ratio H ₁ / d of the shoulder height H ₁ to the ball diameter d is in the range of 0.25 to 0.50, and the cage is a hemisphere for holding the ball. A first split cage having an axial pocket on one side in the axial direction, and fitted inside the first split cage, And a second split cage having a hemispherical pocket for holding a tool on the other side in the axial direction. The first split cage and the second split cage are connected by a connecting means in the axial direction. In a deep groove ball bearing that is non-separated and partially immersed in an oil bath, the inner peripheral surface of the pocket formed in each of the first split cage and the second split cage has a spherical shape along the outer circumference of the ball In addition, a radial groove is formed on an inner peripheral surface of the pocket along the outer periphery of the ball in each of the first divided holder and the second divided holder, and the radial groove However, the inner diameter of each split cage extends from the outer diameter surface to the inner diameter surface, the inner diameter of the first split cage is equal to the pitch circle diameter of the ball, and the outer diameter of the shoulder on the other side of the inner ring raceway groove is Smaller than the inner diameter of the single split cage, formed in the first split cage The said radial groove | channel adopted the structure arrange | positioned so that it may not overlap with the said 2nd division | segmentation holder | retainer in radial direction.

  In the use of the inner ring rotation of the deep groove ball bearing having the above-described configuration, the lubricating oil entering the bearing rotates by contact with the inner ring and contact with the ball, and is directed radially outward by centrifugal force due to the rotation. Try to move. At this time, since a radial groove is formed in the inner peripheral surface of the pocket that accommodates the ball of the cage, the lubricating oil on the inner diameter side of the cage flows into the radial groove, and the outer diameter side of the cage Will be discharged to the outside.

  For this reason, when foreign matter such as gear wear powder enters the inside of the bearing together with the lubricating oil, the foreign matter smoothly flows outside the bearing on the flow of the lubricating oil that flows radially outward inside the bearing and flows out of the bearing. It will be discharged and will not stay inside the bearing.

  Here, the first split cage and the second split cage may be formed of a synthetic resin molded product or may be formed of mild steel.

  In the case of a synthetic resin molded product, since the deep groove ball bearing is oil-lubricated, it is preferably molded with a synthetic resin excellent in oil resistance and durability. Examples of such resins include polyamide 46 (PA46), polyamide 66 (PA66), polyamide 9T (PA9T), polyetheretherketone resin (PEEK), polyphenylene sulfide resin (PPS), and polyphthalamide resin (PPA). Can do. Among these resins, polyphenylene sulfide (PPS) has excellent oil resistance compared to other resins, and therefore, considering 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 bearing device according to the present invention, in the bearing device in which a shaft provided with a helical gear is rotatably supported by a pair of rolling bearings partially immersed in an oil bath, the pair of rolling bearings described above is used as the pair of rolling bearings. The structure uses a deep groove ball bearing.

  In the deep groove ball bearing according to the present invention, as described above, the outer diameter surface of each split cage is formed on the inner peripheral surface of the hemispherical pocket formed in each of the first split cage and the second split cage. By forming the radial groove from the inner diameter surface to the inner diameter surface, the lubricating oil on the inner diameter side of the cage can smoothly move to the outer diameter side of the cage and flow out to the outside. Can be discharged smoothly to the outside. For this reason, the fall of the durability by the biting of a foreign material can be suppressed.

The lubricating oil for flow from the holding vessel diameter smoothly to the outer diameter side, smaller agitation resistance of the lubricating oil, it is possible to reduce the torque loss.

Longitudinal sectional view showing an embodiment of a deep groove ball bearing according to the present invention The top view which shows a part of cage | basket shown in FIG. Sectional view along line III-III in FIG. The top view which shows the state before the coupling | bonding of a 1st division holder and a 2nd division holder. Schematic showing an embodiment of a bearing device according to the present invention

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. 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.

Thrust load side of the shoulder 13a, the shoulder height of 23b as _{H 1,} when the spherical diameter of the ball 31 is d, the ratio _H 1 / d of the shoulder height _{H 1} relative to the spherical diameter d of the ball _{31, H} 1 / It is set as the range of d = 0.25-0.50.

  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, 2, and 4, the first split holder 41 has a pair of opposed pocket claws 44 formed at equal intervals in the circumferential direction on one side surface in the axial direction of the annular body 43. It is made of a synthetic resin molded product provided with a pocket 45 having a size of more than a half circle that punches the annular body 43 between the pocket claws 44. The inner diameter of the annular body 43 is the pitch circle diameter (PCD) of the ball 31. The outer diameter of the outer ring 11 is 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, and is inserted into the bearing from the shoulder 13b side where the height of the outer ring 11 is low. It is possible.

  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.

  As shown in FIGS. 1 to 3, the inner peripheral surface of the pocket 45 formed in the first divided holder 41 and the inner peripheral surface of the pocket 50 formed in the second divided holder 42 are A plurality of radial grooves 53 extending from the outer diameter surface to the inner diameter surface of each split cage are formed at intervals in the circumferential direction on the spherical inner peripheral surface.

  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), polyphenylene sulfide (PPS), and polyphthalamide resin (PPA). 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 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 Become. 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 ball between the outer ring 11 and the inner ring 21 31 can be incorporated reliably.

  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. 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 into 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 A is completed.

  In the specification of the inner ring rotation in which the outer periphery of the deep groove ball bearing A is immersed in an oil bath, when the inner ring 21 rotates, the ball 31 revolves while rotating, and the cage 40 rotates due to the revolution. At this time, the first split retainer 41 and the second split retainer 42 forming the retainer 40 have different outer diameters and inner diameters, so the peripheral speeds are also different. A pumping action occurs, and the lubricating oil inside the bearing is given a discharge force in the direction of being sent out from the built-in side of the first split cage 41, and the lubricating oil on the inside diameter side of the cage 40 is directed radially outward. All the suction force is loaded.

  Further, the lubricating oil on the inner diameter side of the cage 40 rotates by contact with the cage 40 and the ball 31 and tends to flow radially outward in the bearing by centrifugal force due to the rotation. At this time, since the radial grooves 53 are formed on the inner peripheral surfaces of the pockets 45 and 50 in the first divided holder 41 and the second divided holder 42, the lubricating oil on the inner diameter side of the holder 40 is the radial groove. 53, and is smoothly discharged from the outer diameter side of the cage 40 to the outside.

  In this way, the lubricating oil on the inner diameter side of the cage 40 flows from the radial groove 53 toward the outer diameter side of the cage and smoothly flows out to the outside. Therefore, when foreign matter such as gear wear powder enters the bearing together with the lubricating oil. The foreign matter is smoothly discharged outside the bearing along the flow of the lubricating oil, preventing the foreign matter from staying inside the bearing and suppressing the decrease in the durability of the bearing due to the inclusion of the foreign matter. Can do.

  Further, since the lubricating oil flows smoothly inside the bearing, the agitation resistance of the lubricating oil is reduced, and torque loss is reduced.

  In the embodiment, the first divided holder 41 and the second divided holder 42 are formed of synthetic resin, but may be formed of mild steel (SPC).

  FIG. 5 shows a bearing device that rotatably supports a shaft 61 that supports the helical gear 60 on the driven side using the deep groove ball bearing A shown in the embodiment. In this case, the deep groove ball bearing A is assembled so that the shoulder 23b on the thrust load side of the inner ring 21 is located on the helical gear 60 side. The deep groove ball bearing A is assembled so that a part thereof is immersed in an oil bath.

  In the bearing device, when the rotation is transmitted from the driving side helical gear 62 to the driven side helical gear 60, a thrust force is applied to the shaft 61, and the thrust force is applied to the thrust load side shoulder 23b of the inner ring 21 in the deep groove ball bearing A and the outer ring. 11 on the thrust load side shoulder 13a.

  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.

11 outer ring 12 raceway groove 13a shoulder 13b shoulder 21 inner race 22 raceway groove 23a shoulder 23b shoulder 31 ball 40 retainer 41 first split retainer 42 second split retainer 45 pocket 50 pocket 53 radial groove 60 helical gear 61 shaft A depth slot Ball bearing X connection means

Claims (8)

A ball is assembled between the raceway groove formed on the inner diameter surface of the outer ring and the raceway groove formed on the outer diameter surface of the inner ring, the ball is held by a cage, and a pair of the two formed on both sides of the outer ring raceway groove. Of the total four shoulders of the pair of shoulders formed on both sides of the shoulder and the inner ring raceway groove, the shoulder height of the shoulder on one side of the outer ring raceway groove and the shoulder on the other side of the inner ring raceway groove is set to the other of the outer ring raceway groove. Shoulder height relative to the ball diameter d, where H _{1 is} the height of the shoulder on the side and the shoulder height on one side of the inner ring raceway groove, and H _{1 is} the height of the shoulder of the ball. is in the range of 0.25 to 0.50 ratio H _{1 /} d of the H _1, wherein the retainer includes a first split cage having a hemispherical pockets for balls held in one side of the axial direction, the The second divided holder fitted inside the first divided holder and having a hemispherical pocket for holding the ball on the other side in the axial direction It is formed between, a non-separated axially connected by a connecting means that the first split cage and the second split cage, the ball bearing each deep part is immersed in an oil bath,
The inner peripheral surfaces of the pockets formed in each of the first split holder and the second split holder are spherical along the outer periphery of the ball, and each of the first split holder and the second split holder Further, along the outer periphery of the ball, a radial groove is formed on the inner peripheral surface of the pocket, and the radial groove extends from the outer diameter surface of each split cage to the inner diameter surface,
The inner diameter of the first split cage is equal to the pitch circle diameter of the ball, and the outer diameter of the shoulder on the other side of the inner ring raceway groove is smaller than the inner diameter of the first split cage,
The deep groove ball bearing, wherein the radial groove formed in the first split cage is arranged so as not to overlap the second split cage in the radial direction.   The deep groove ball bearing according to claim 1, wherein each of the first split cage and the second split cage is made of a synthetic resin molded product.   The deep groove ball bearing according to claim 2, wherein the synthetic resin is made of a polyamide resin.   The deep groove ball bearing according to claim 3, wherein the polyamide resin is one of polyamide 46, polyamide 66, and polyamide 9T.   The deep groove ball bearing according to claim 2, wherein the synthetic resin is a polyether ether ketone resin.   The deep groove ball bearing according to claim 2, wherein the synthetic resin is made of polyphenylene sulfide resin.   The deep groove ball bearing according to claim 2, wherein the synthetic resin is made of polyphthalamide resin. In a bearing device in which a shaft provided with a helical gear is rotatably supported by a pair of rolling bearings,
The bearing device, wherein the pair of rolling bearings comprises the deep groove ball bearing according to any one of claims 1 to 7.

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