JP2013092242A - Retainer for deep groove ball bearing, deep groove ball bearing using the retainer, and bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a retainer for a deep groove ball bearing capable of reducing stagnation of a foreign substance inside the bearing and a torque loss and improving oil passing properties.SOLUTION: A taper angle of a first divided retainer 41 formed in a taper shape and a taper angle of a second divided retainer 42 formed in a taper shape are the same. Outer and inner diameters of a large-diameter end surface of the first divided retainer 41 and outer and inner diameters of a small-diameter end surface of the second divided retainer 42 are the same. A plurality of semicircular pockets 43 are equidistantly formed at a large-diameter end of the first divided retainer 41. A plurality of semicircular pockets 44 forming, together with the pockets 43 of the first divided retainer 41, circular pockets 45 are equidistantly formed at a small-diameter end of the second divided retainer 42. An engagement claw 47 is provided at a pillar part 46 between the pockets 43 of the first divided retainer 41. The engagement claw 47 is engaged with an engagement recess 49 formed at a pillar part 48 between the pockets 44 of the second divided retainer 42 to connect the first divided retainer 41 and the second divided retainer 42 in the axial direction so that the retainer 40 of the taper shape is assembled.

Description

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

  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 Patent Document 1, since the shoulder heights of the inner ring and the outer ring are asymmetrical, two divided cages having different diameters are fitted inside and outside, and one divided holding is performed. The engaging claw formed on the container is engaged with the engaging recess provided on the other divided holder, and the pair of divided holders are coupled in the axial direction to form a holder for holding the ball. Therefore, many irregularities are formed on the outer diameter surface and inner diameter surface of the cage, and foreign matters such as gear wear powder are liable to adhere and stay on the irregularities, and the lubricating oil is agitated. Therefore, there are many torque losses, and there are still points to be improved in order to reduce foreign matter retention and torque loss.

  In addition, since a radial step is formed between the outer diameter surface and the inner diameter surface of the large-diameter side split cage and the small-diameter side split cage, the flow of the lubricating oil is obstructed by the step, and the lubricating oil is contained inside the bearing. Cannot be smoothly distributed, and there are still points to be improved in improving oil permeability.

  An object of the present invention is to provide a deep groove ball bearing retainer, a deep groove ball bearing, and a bearing device capable of reducing the retention of foreign matters in the bearing, reducing torque loss, and improving oil permeability.

  In order to solve the above-mentioned problem, in the deep groove ball bearing retainer according to the present invention, the tapered first divided retainer and the taper angle of the first divided retainer are the same, and the small diameter A tapered second split cage whose outer diameter and inner diameter of the end surface are the same as the outer diameter and inner diameter of the large diameter end surface of the first split cage, and the large diameter end of the first split cage; A plurality of half-shaped pockets are formed in each of the small-diameter ends of the second split cage so as to form a circular pocket for accommodating a ball in a connected state in which the small-diameter end surface of the second split cage is brought into contact with the large-diameter end surface of the first split cage. Circular pockets are provided at equal intervals in the circumferential direction, and the end surfaces of the column portions formed between the semicircular pockets of the first divided cage and the semicircular pockets of the second divided cage are arranged. An engaging claw whose tip is a hook is provided on the outer peripheral part or inner peripheral part of one end face. Since the engaging claw can be engaged with the other end surface, and the engaging concave portion for connecting the first divided holder and the second divided holder in the axial direction in the engaged state is adopted. is there.

Further, in the deep groove ball bearing according to the present invention, the outer ring having the raceway groove formed on the inner diameter surface, the inner ring having the raceway groove formed on the outer diameter surface, and the raceway groove of the outer ring and the raceway groove of the inner ring are incorporated. And a retainer for holding the ball. The height of at least one 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 shoulder on the other side of the outer ring raceway groove. Alternatively, when the height of the shoulder on one side of the inner ring raceway groove is made higher, the shoulder height of the higher shoulder is H ₁ , and the ball diameter of the ball is d, the shoulder height H _{1 with} respect to the ball diameter d of the ball. In the deep groove ball bearing in which the ratio H ₁ / d is in the range of 0.25 to 0.50, the cage having the above-described configuration according to the present invention is employed as the cage.

  When assembling the deep groove ball bearing having the above-described configuration, a plurality of balls are assembled between the raceway grooves of the outer ring and the inner ring, and then the first split cage and the second split cage are placed between the opposing portions of the outer ring and the inner ring. insert.

  At this time, the first split cage is inserted between the opposing portions with the pocket forming side end first from the shoulder side where the height of the outer ring is high, while the second split cage is the shoulder where the height of the outer ring is low The pocket forming side end first is inserted between the opposing portions from the side, and the engaging claws formed in one of the split holders are axially opposed to the engaging recesses provided in the other split holder, and The direction of the first and second split cages is adjusted so that the semicircular pocket faces the ball in the axial direction, and the first and second split cages are pushed in in the axial direction.

  As described above, by adjusting the orientation of the first and second split cages and pushing both split cages in the axial direction, the engaging claws engage with the engaging recesses of the other split cage. The first divided cage and the second divided cage are combined with each other to form a cage, and the plurality of balls are held in the circularly combined pockets, and the deep groove ball bearing is in an assembled state. The

  Here, the first divided cage and the second divided cage forming the cage are tapered, and the outer diameter and inner diameter of the large-diameter end surface of the first divided cage are outside the small-diameter end surface of the second divided cage. Since the diameter is the same as the inner diameter, a tapered cage having no steps on the outer surface and the inner surface can be assembled. Therefore, by assembling the deep groove ball bearing using the cage, foreign matter that enters the bearing is less likely to adhere to and stay on the surface of the cage, and the retention of foreign matter can be reduced.

  In addition, the cage is tapered, and the large diameter end and the small diameter end have a difference in diameter. Therefore, when the cage rotates, a pumping action is generated due to a difference in peripheral speed between the large diameter end and the small diameter end. Lubricating oil will be fed into the inside. At this time, since the outer surface and the inner surface of the cage are smooth, the lubricating oil flows smoothly, the stirring resistance of the lubricating oil is small, and the torque loss is small.

  Here, it is preferable that the first split cage and the second split cage are molded products of synthetic resin in order to reduce costs. In this case, since the deep groove ball bearing is oil-lubricated, it is preferable to mold it with a synthetic resin having excellent oil resistance and durability. Examples of such resins include polyamide 46 (PA46), polyamide 66 (PA66), polyamide 9T (PA9T), polyetheretherketone resin (PEEK), and polyphenylene sulfide resin (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 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 retainer according to the present invention, as described above, the tapered first split retainer and the second split retainer have the same taper angle, and the first split retainer is large. The outer diameter and inner diameter of the radial end surface are the same as the outer diameter and inner diameter of the small-diameter end surface of the second split retainer, and the first split retainer and the second split retainer are connected to the engagement claw and the engagement recess. A deep groove ball that can be combined with the axial direction and tapered so that it can receive large thrust loads and radial loads by making the left and right shoulder height of the outer ring different from the left and right shoulder height of the inner ring. It can be applied to bearings.

  In addition, the cage assembled by combining the first divided cage and the second divided cage forms a smooth tapered outer surface and a tapered inner surface without a step, so that it is used in a deep groove ball bearing. A deep groove ball bearing with little foreign matter retention and little torque loss can be obtained. In addition, since the cage causes pumping action due to the difference in peripheral speed due to the difference in diameter between the large-diameter end and the small-diameter end, a deep groove ball bearing with excellent oil permeability can be obtained.

Longitudinal sectional view showing an embodiment of a deep groove ball bearing according to the present invention Sectional drawing which expands and shows a part of FIG. Sectional drawing which shows the other example of the coupling | bonding means of a 1st division holder and a 2nd division holder Side view of the cage shown in FIG. The side view which shows the state before the coupling | bonding of the 1st division | segmentation holder | retainer and the 2nd division | segmentation holder | retainer of the holder | retainer shown in FIG. FIG. 4 is a partially cutaway front view of the cage shown in FIG. 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 even if they are lower than the shoulder heights of the standard depth groove ball bearings. Good.

  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.

  As shown in FIGS. 2, 4, and 5, the holder 40 includes a first divided holder 41 and a second divided holder 42. The first split holder 41 has a tapered shape, and a plurality of semicircular pockets 43 are formed at equal intervals in the circumferential direction at the large diameter end.

  Similarly to the first divided holder 41, the second divided holder 42 also has a tapered shape, the taper angle of which is the same as the taper angle of the first divided holder 41, and the outer diameter and inner diameter of the small-diameter end face are The outer diameter and inner diameter of the large-diameter end face of the one-part cage 41 are the same.

  In addition, the same number of semicircular pockets 44 as the pockets 43 formed in the first split holder 41 are formed at equal intervals in the circumferential direction at the small-diameter end of the second split holder 42. A circular pocket 45 for accommodating a ball is formed in a connected state in which the small-diameter end face of the second split holder 42 is brought into contact with the large-diameter end face of the first split holder 41.

  As shown in FIGS. 2, 5, and 6, an end surface outer peripheral portion of the column portion 46 formed between the adjacent pockets 43 of the first divided holder 41 has a flange portion toward the second divided holder 42. An engaging claw 47 having a tip 47a is formed. On the other hand, the outer periphery of the column portion 48 formed between the adjacent pockets 44 of the second divided holder 42 is engageable with the engaging claw 47. A concave portion 49 is provided, and the first split holder 41 and the second split holder 42 are coupled in the axial direction by the engagement of the engaging claw 47 with the engaging concave portion 49 and are not separated in the axial direction. .

  Here, in FIG. 2, the engaging claw 47 is formed on the outer peripheral portion of the end surface of the column portion 46 of the first divided holder 41, and the engaging recess 49 is provided on the outer periphery of the column portion 48 of the second divided holder 42. However, as shown in FIG. 3, the engagement claw 47 is formed on the inner peripheral portion of the end surface of the column portion 46 of the first divided holder 41, and the engagement recess is formed on the inner periphery of the column portion 48 of the second divided holder 42. 49 may be provided. Although omitted in the drawing, an engaging claw may be provided on the end face of the column part 48 of the second divided holder 42, and an engaging recess may be provided in the column part 46 of the first divided holder 41.

  As shown in FIG. 3, when the engagement claw 47 is formed on the inner peripheral portion of the end surface of the column portion 46 of the first divided holder 41, the flange portion 47 a is provided upward at the distal end portion of the engagement claw 47. To do.

  Each of the first split holder 41 and the second split holder 42 is a molded product of synthetic resin. In this case, since the cage 40 is exposed to the lubricating oil that lubricates the deep groove ball bearing, a synthetic resin excellent in oil resistance is used.

  Examples of such resins include polyamide 46 (PA46), polyamide 66 (PA66), polyamide 9T (PA9T), polyetheretherketone resin (PEEK), and polyphenylene sulfide resin (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, the balls 31 are arranged at equal intervals in the circumferential direction, and the first split cage 41 and the second ring are disposed between the opposing portions of the outer ring 11 and the inner ring 21. The division holder 42 is inserted.

  At this time, the first split cage 41 is inserted between the opposing portions of the outer ring 11 and the inner ring 21 with the pocket 43 first from the shoulder 13a side where the height of the outer ring 11 is high, while the second split cage 42 is The outer ring 11 is inserted between the opposed portions of the outer ring 11 and the inner ring 21 with the pocket 44 first from the lower shoulder 13b side.

  After the insertion of the first split holder 41 and the second split holder 42, the engaging claws 47 formed in the first split holder 41 are axially inserted into the engaging recesses 49 provided in the second split holder 42. The first divided holder 41 and the second divided holder 42 are adjusted so that the semicircular pockets 43 and 44 are opposed to each other in the axial direction so that the semicircular pockets 43 and 44 are opposed to each other in the axial direction. The second split cage 42 is pushed in the axial direction.

  As described above, by adjusting the orientation of the first divided holder 41 and the second divided holder 42 and pushing both the divided holders 41 and 42 in the axial direction, as shown in FIG. The claw 47 engages with the engaging recess 49, and the first divided holder 41 and the second divided holder 42 are coupled to each other to form the holder 40, and the plurality of balls 31 are formed in the circularly combined pocket 45. The deep groove ball bearings A are held in the assembled state.

  Here, the retainer 40 that holds the ball 31 includes a tapered first split retainer 41 and a tapered second split retainer 42 having the same taper angle, and the first split retainer 41 has a large diameter. Since the outer diameter and inner diameter of the end surface are the same as the outer diameter and inner diameter of the small-diameter end surface of the second split retainer 42 abutted on the large-diameter end surface, the first split retainer and the second split retainer The outer surface and the inner surface of the cage 40 assembled by bonding form a smooth tapered surface without a step.

  For this reason, in the adoption of the cage 40 in a deep groove ball bearing, a deep groove ball bearing A with less foreign matter retention can be obtained. Further, it is possible to obtain a ball bearing A with a small stirring resistance of the lubricating oil and a small torque loss.

  Furthermore, since the retainer 40 is tapered, the peripheral speed differs depending on the difference in diameter between the large-diameter end and the small-diameter end during rotation, and a pumping action is generated inside the bearing. Due to the pumping action, the lubricating oil is forcibly fed into the bearing, and the deep groove ball bearing A having good oil permeability can be obtained.

  FIG. 7 shows a bearing device that rotatably supports a shaft 51 that supports the helical gear 50 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 50 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 drive side helical gear 52 to the driven side helical gear 50, a thrust force is applied to the shaft 51, and the thrust force is a thrust load side shoulder 23b of the inner ring 21 and the outer ring in the deep groove ball bearing A. 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 Track groove 13a Shoulder 13b Shoulder 21 Inner ring 22 Track groove 23a Shoulder 23b Shoulder 31 Ball 40 Holder 41 First divided holder 42 Second divided holder 43 Semicircular pocket 44 Semicircular pocket 45 Circular pocket 46 Column 47 Engaging claw 47a collar 48 column 49 engaging recess 50 helical gear 51 shaft

Claims (8)

  The tapered first split cage has the same taper angle as that of the first split cage, and the outer diameter and inner diameter of the small diameter end surface are the outer diameter and inner diameter of the large diameter end surface of the first split cage. A tapered second split cage having the same diameter, and a large diameter end surface of the first split cage on each of the large diameter end of the first split cage and the small diameter end of the second split cage. A plurality of semicircular pockets forming circular pockets for accommodating balls in a connected state where the small-diameter end faces of the second split cage are abutted are provided at equal intervals in the circumferential direction, and between the semicircular pockets of the first split cage Engagement of the end surface of the column portion formed on the outer peripheral portion or inner peripheral portion of one end surface between the end surface of the column portion and the end surface of the column portion formed between the semicircular pockets of the second split cage. A claw is provided, and the engaging claw can be engaged with the other end surface. 2 split cage and deep groove cage for a ball bearing, characterized in that a engaging recess that binds axially.   The deep groove ball bearing cage according to claim 1, wherein each of the first divided cage and the second divided cage is made of a synthetic resin molded product.   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is made of a polyamide resin.   The cage for deep groove ball bearings according to claim 3, wherein the polyamide resin is one of polyamide 46, polyamide 66, and polyamide 9T.   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is a polyether ether ketone resin.   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is made of polyphenylene sulfide resin. 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 height of at least one 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 higher than the height of the shoulder on the other side of the outer ring raceway groove or one side of the inner ring raceway groove. The ratio H ₁ / d of the shoulder height H _{1 with} respect to the ball diameter d is 0.25 to 0. 0, where H ₁ is the shoulder height of the high shoulder and d is the ball diameter of the ball. In deep groove ball bearings with a range of 50,
A deep groove ball bearing, wherein the retainer is a deep groove ball bearing retainer according to any one of claims 1 to 6. In a 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 bearing device characterized in that the pair of rolling bearings comprises the deep groove ball bearing according to claim 7.

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