JP2009281399A - Deep groove ball bearing cage and deep groove ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a deep groove ball bearing cage capable of suppressing breakage, wear and deformation of an engaging member during assembly and high-speed rotation, and to provide a deep groove ball bearing. <P>SOLUTION: The deep groove ball bearing cage includes first and second elements 30, 40 having annular portions 31, 41 and columnar portions 32, 42 arranged at a predetermined space, respectively, and a fixed piece 50. The first element 30 has a through-hole 34 passing through the columnar portion 32 in the axial direction and formed with a stepped portion 37 on one peripheral side. The second element 40 has a protruded portion 44 protruded from a front end face 45 of the columnar portion 42 in the axial direction, and the protruded portion 44 has a hook portion 47 engageable with the stepped portion 37. In such a state that the stepped portion 37 of the first element 30 engages with the hook portion 47 of the second element 40, the fixed piece 50 is inserted into the other peripheral side of the through-hole 34 to fill a clearance to the protruded portion 44. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a deep groove ball bearing retainer used for a deep groove ball bearing that is operated at high speed, for example, in an automobile transmission, and a deep groove ball bearing incorporating the deep groove ball bearing retainer.

  As a resin cage generally used in a deep groove ball bearing, for example, there is a cage 101 called a crown type cage shown in FIG. The cage 101 is formed by injection molding of synthetic resin, and an annular rim portion 102 and a plurality of pillar portions arranged at predetermined intervals in the circumferential direction on the axial end surface of the rim portion 102. 103, a pocket portion 104 formed between the pillar portions 103 and 103 so as to be adjacent to each other, and holds a plurality of balls so as to be able to roll in the circumferential direction at substantially equal intervals, and a circle on the inner peripheral surface of the pocket portion 104 A pair of claw portions 105a and 105b formed at both ends in the circumferential direction, and an opening portion 106 formed between the tips of the pair of claw portions 105a and 105b. Then, by pushing the ball into the pocket 104 while expanding the pair of claws 105a and 105b from the opening 106, the ball is held in the pocket 104 so as to be able to roll through a minute gap.

  However, the crown type cage 101 incorporated in the conventional deep groove ball bearing is a ball guide type cage, and the end portion on the pocket inner diameter side comes into contact with the ball 107 in response to the recent high speed rotation. By wearing, as shown in FIG. 9, the centrifugal force due to the rotation of the cage 101 acts on the axial end portion 108 on the cage opening side, and the elasticity or the axial end portion 109 on the rim side is used as the torsion axis. Torsional deformation due to plastic deformation may occur, and the cage outer diameter surface may come into contact with the inner diameter surface of the outer ring, causing the cage to wear, and problems such as abnormal heat generation and increased torque may occur.

  In order to cope with this problem, Patent Document 1 discloses a cage 201 whose synthesis is enhanced by connecting an annular lid 203 to the side surface of the pocket opening side of the cage body 202 shown in FIG. Yes. As a connecting means between the cage body 202 and the lid 203, a coupling leg 206 is formed between the claws 205 of the cage body 202, and an engagement recess 207 that opens at the tip surface is provided on the coupling leg 206, The lid 203 is provided with an engagement shaft portion 208, and both members are connected by adopting a method of inserting the engagement shaft portion 208 into the engagement recess 207.

Further, in Patent Document 2, two annular bodies 302 and 303 are integrally formed by providing both engagement claws 304 and engagement holes 305 on two annular bodies 302 and 303 having the same shape shown in FIG. A corrugated cage 301 is disclosed which is fixed to the above.
Japanese Utility Model Publication No. 6-1648 JP 2003-34357 A

  However, in the structures described in Patent Documents 1 and 2, in order to assemble the cage without rattling, it is necessary to push at least one member into the other member while elastically deforming it. That is, in Patent Document 1, it is necessary to increase the diameter of the engagement recess 207 and insert the engagement shaft 208, and in Patent Document 2, it is necessary to insert the engagement claw 304 into the engagement hole 305. There is. Therefore, if the amount of elastic deformation is increased, breakage is likely to occur during assembly, and if the amount of elastic deformation is small, the engagement force is reduced.

  Further, when the bearing is rotated at a high speed, the engaging portion may be worn by vibration of the cages 201 and 301, or the engaging member may be deformed or damaged due to centrifugal force or heat. When the engaging member is damaged or the engaging force is reduced, the cages 201 and 301 are separated and cannot hold the balls, thereby impairing the function as a bearing.

  Furthermore, in the case of a conventional crown-type cage or wave-type cage, the cage shape is uneven on the axial side of the cage, so that the agitation resistance of the lubricating oil increases when the bearing rotates, and the bearing torque increases. Problem occurs.

  The present invention has been made to eliminate such inconveniences, and its purpose is for a deep groove ball bearing capable of suppressing breakage, wear, and deformation of an engaging member during assembly and high-speed rotation. The object is to provide a cage and a deep groove ball bearing.

The above object of the present invention is achieved by the following configurations.
(1) A deep groove ball bearing retainer comprising an annular portion and pillar portions arranged at a predetermined interval, and having a pocket for holding a ball,
A first element having a through-hole formed in the pillar portion in the axial direction and provided with a step portion on one circumferential side;
A second element having a protruding portion protruding in the axial direction on a front end surface of the column portion, and having a flange portion engageable with the stepped portion on the protruding portion;
A fixing piece that fills a gap between the projecting portion inserted in the other circumferential direction of the through hole in a state where the step portion of the first element and the flange portion of the second element are engaged with each other. A cage for deep groove ball bearings.
(2) When inserting the protruding portion into the through hole, the phase of the pocket surfaces of the first and second elements is configured to deviate from each other phase where the pocket is formed. The deep groove ball bearing retainer according to (1).
(3) The deep pocket ball bearing according to (1) or (2), wherein the pocket has a spherical shape, and the ball is positioned in the radial direction by engagement between the ball and the pocket. Cage.
(4) In the deep groove ball bearing in which the outer ring and the inner ring are raceways, and a plurality of balls are rotatably held by a cage.
The deep groove ball bearing, wherein the cage is the deep groove ball bearing cage according to any one of (1) to (3).
(5) Used in oil lubrication,
On both side surfaces of the outer ring, shield plates extending in the radial direction are installed,
The deep groove ball bearing according to (4), wherein an opening is provided between the tip of the shield plate and the inner ring.

  According to the crown type cage for deep groove ball bearings and the deep groove ball bearing of the present invention, in the synthetic resin combination cage, the flange of the second element as the engaging portion and the first element as the engaged portion When engaging the step portion, the amount of elastic deformation of the engaging portion can be reduced or eliminated. In addition, in a state where both elements are engaged, a fixing piece that fills the gap between the protrusions is inserted into the through hole, and by fixing both elements integrally with the fixing piece, the engaging force of both elements can be increased. it can. Thereby, wear, deformation, and breakage of the engaging portion when the bearing is used can be suppressed.

  Hereinafter, each embodiment of the deep groove ball bearing according to the present invention will be described in detail with reference to the drawings.

(First embodiment)
FIG. 1 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to a first embodiment of the present invention.
As shown in FIG. 1, the deep groove ball bearing 10 includes an outer ring 11 having an outer ring raceway surface 11a on the inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on the outer peripheral surface, the outer ring raceway surface 11a and the inner ring raceway surface 12a. And a plurality of balls 13 provided between the inner ring 12 and the outer ring surface of the inner ring 12 to hold the plurality of balls 13 in a rollable manner. And a metal shield plate 14 fixed to grooves 11b provided at both axial ends of the inner peripheral surface of the outer ring 11.

  A cage 20 shown in FIG. 2 is a combination cage in which a first element 30 and a second element 40 are combined in the axial direction. The cage 20 includes annular portions 31 and 41 on both sides in the axial direction. This is a so-called ladder-type cage that includes a plurality of column portions 22 that connect the annular portions 31 and 41 to each other from a plurality of locations at intervals in the circumferential direction. The opposing surfaces of the column portions 22 adjacent to each other in the circumferential direction are formed with a partial spherical pocket 25 having a slightly larger radius of curvature than the ball rolling surface, and the cage 20 is engaged with the ball 13 and the pocket 25. Thus, positioning in the axial direction and the radial direction is performed, and a ball guiding system is guided by the ball 13 during rotation.

  The cage 20 is formed of a resin, and as a resin material, a polyamide resin such as polyamide 46 or polyamide 66, polybutylene terephthalate, polyferlen salside (PPS), polyamideimide (PAI), thermoplastic polyimide, polyetheretherketone ( Examples include PEEK) and polyether nitrile (PEN). Moreover, the rigidity and dimensional accuracy of the cage 20 can be improved by appropriately adding about 10 to 50 wt% of a fibrous filler such as glass fiber or carbon fiber to the resin.

In FIG. 3, the disassembled perspective view of each component of a combination holder | retainer is shown.
The cage 20 includes an annular first element 30, a second element 40, and a plurality of substantially rectangular parallelepiped fixing pieces 50. The first element 30 and the second element 40 are respectively connected to the annular portions 31, 41 and a predetermined number. Column portions 32 and 42 that are disposed at intervals and constitute the column portion 22 are provided. Further, a plurality of hemispherical pocket surfaces 33 (43) that follow the outer periphery of the ball 13 are provided between the column portions 32 and 32 (42, 42) adjacent in the circumferential direction.

  Each column part 32 of the first element 30 and the annular part 31 that is continuous with each column part 32 are provided with a through hole 34 that penetrates in the axial direction, and a step is formed on one circumferential wall part 36 that forms the through hole 34. A portion 37 is formed. Therefore, the opening area on the annular part side is larger than the opening area on the tip part side of the column part of the first element 30.

  The tip surface 45 of each column portion 42 of the second element 40 is provided with a protrusion 44 protruding perpendicularly to the axial direction from a position offset in one circumferential direction, and the tip of the protrusion 44 is offset. A flange portion 47 that slightly protrudes from the wall portion 46 is formed in the same direction as the direction. The circumferential length of the protrusion 44 is smaller than the circumferential length of the through hole 34, and the circumferential length t (see FIG. 4) of the flange 47 is substantially the same as the circumferential length of the step 37. The flange portion 47 is formed by inserting the protrusion 44 of the second element 40 into the through hole 34 of the first element 30 and then slightly shifting the phases of the elements 30 and 40 to thereby form a step 37 of the through hole 34. It is comprised so that it may engage with.

  As will be described later, the fixing piece 50 is opposite to the wall portion 46 on which the flange portion 47 of the protrusion 44 is formed when the flange portion 47 of the second element 40 and the step portion 37 of the first element 30 are engaged. In the circumferential direction and the radial direction so as to be embedded in a circumferential gap formed between the side wall portion 48 and the wall portion 36 on the opposite side to the wall portion 36 where the step portion 37 of the through hole 34 is formed. Length and axial length are set. In addition, in order to eliminate the thermal expansion difference with the 1st element 30 and the 2nd element 40, it is desirable to form the fixed piece 50 with the same resin material mentioned above.

  The cage 20 including the first element 30, the second element 40, and the fixed piece 50 configured as described above has the axial lengths of the through hole 34, the protruding portion 44, and the fixed piece 50 substantially equal to each other. At the time of embedding, the axial end surface of the cage 20 is substantially flush, and the radial lengths of the through hole 34, the protrusion 44, and the fixed piece 50 are substantially equal. The protrusion 44 and the fixed piece 50 are configured to be mounted without a gap in the direction and the radial direction.

Next, a method for assembling the cage 20 will be described with reference to FIG.
As shown in FIG. 4 (a), the first element 30 and the second element 40 are arranged so that the pocket surfaces 33 and 43 face each other, and at least one of them is moved in the axial direction. ), The columnar tip surface 35 of the first element 30 and the columnar tip surface 45 of the second element 40 are brought into contact with each other. At this time, at least the circumferential length of the flange 47 is between the wall 46 on the side where the flange 47 of the protrusion 44 is provided and the wall 36 on the side where the step 37 of the through hole 33 is formed. A gap is formed by the length t, and the phases of the pocket surfaces 33 and 43 are shifted from each other's phase where the pocket 25 is formed. Subsequently, at least one of the first element 30 and the second element 40 is relatively rotated in the circumferential direction to engage the flange portion 47 of the protrusion 44 and the step portion 37 of the through hole 34, and FIG. Thus, the first element 30 and the second element 40 are positioned in the axial direction. At this time, the pockets 25 are formed by matching the phases of the pocket surfaces 33 and 43 of the first element 30 and the second element 40, and between the wall 38 of the first element 30 and the wall 48 of the protrusion 44. A predetermined gap is formed in the circumferential direction. Subsequently, as shown in FIG. 4 (d), the fixing piece 50 is press-fitted along the axial direction into the gap. As a result, as shown in FIG. 4E, the first element 30 and the second element 40 are positioned in the circumferential direction, and the elements 30 and 40 are combined together without backlash.

  The shield plate 14 is formed, for example, by pressing a metal plate material such as SPCC into a substantially annular shape, and the outer peripheral portion 14 a is a groove provided at the axial end of the inner peripheral surface of the outer ring 11. It is press-fitted and fixed to 11b, and its inner peripheral portion 14b is disposed with a gap from the outer peripheral surface of the inner ring 12. The shield plate 14 may be formed in an overall annular shape by covering a metal core with an elastic material such as rubber or synthetic resin.

  Here, the inner diameter of the shield plate 14 is the same as the inner diameter of the cage 20 and is set to be smaller than the pitch circle diameter of the balls, and between the inner peripheral portion 14 b of the shield plate 14 and the outer peripheral surface of the inner ring 12. As a result, an opening serving as a supply port or a discharge port for the lubricating oil is secured.

  The deep groove ball bearing configured as described above has one of the axial directions arranged on the lubricant supply side and the other on the discharge side. For example, the outer ring 11 is fitted in the housing, and the inner ring 12 is fitted on the rotating shaft. The deep groove ball bearing 10 is fitted into a device such as a transmission of an automobile so that the inner ring 12 and the outer ring 11 can freely rotate relative to each other. At this time, each ball 13 revolves around the inner ring 12 while rotating. Further, the cage 20 rotates around the inner ring 12 at the same speed as the revolution speed of each ball 13.

  The space between the housing and the rotating shaft acts as a supply path and a discharge path for supplying and discharging the lubricating oil. When the lubricating oil is supplied from the side of the deep groove ball bearing 10 through a supply path from a lubricating oil tank (not shown), the lubricating oil is the outer periphery of the inner peripheral portion 14 b of the shield plate 14 and the inner ring 12. It flows into the inside of the deep groove ball bearing 10 from the opening with the surface and is agitated as the deep groove ball bearing 10 rotates.

  At this time, the lubricating oil supplied to the deep groove ball bearing 10 is blown to the outer diameter side by centrifugal force, and is blocked by the shield plates 14 installed at both ends of the outer ring 11, and the inside of the deep groove ball bearing 10 is oil. It becomes a bath state. Lubricating oil lubricates the sliding surfaces of the outer ring 11, inner ring 12, ball 13, and cage 20, and then is discharged to the discharge path from the opening on the side opposite to the opening on the supply side.

  Since the deep groove ball bearing 10 configured in this way uses a cage made of synthetic resin, the inertial mass of the cage can be made sufficiently small, and accordingly, the bearing is lightened and the rotational speed is increased. Can be achieved.

  In addition, the retainer 20 shifts the first element 30 and the second element 40 by at least the circumferential length t of the flange portion 47 of the protrusion 44 and inserts the protrusion 44 into the through hole 34. The amount of elastic deformation can be reduced or eliminated.

  In addition, after the protrusion 44 is inserted into the through hole 34, the fixing piece 50 that fills the circumferential gap between the wall 48 of the protrusion 44 and the wall 38 of the through hole 33 is attached. The resultant power can be increased. Therefore, it is possible to prevent the engaging portion from being damaged during the assembly of the cage 20 and during high-speed rotation.

  Furthermore, since the cage 20 has a so-called ladder shape, the axial end face has less irregularities than a crown type or corrugated type cage, and the stirring resistance during rotation of the bearing can be reduced and the bearing torque can be reduced. it can.

  Furthermore, since there is an opening serving as a lubricant supply or discharge port between the shield plate 14 and the inner ring 12 and the supply and discharge performance of the lubricant is not impaired, the lubricant stays. The temperature rise of the deep groove ball bearing 10 can be suppressed without continuing.

  Furthermore, the shield plate 14 is provided on both side surfaces of the outer ring 11, and the inner diameter of the shield plate 14 is the same as the inner diameter of the cage, so that the cage 20 and the ball 13, and the sliding portion of the cage 20 and the outer ring 11. Since there is always lubricating oil, the lubricity of the sliding part is improved, and there is an effect of suppressing wear and reducing frictional force.

(Second Embodiment)
FIG. 5 is an explanatory view of a cage incorporated in a deep groove ball bearing according to the second embodiment of the present invention. Since the deep groove ball bearing of the second embodiment is the same as the deep groove ball bearing of the first embodiment except that the shape of the cage is different, only the cage will be illustrated and described. In the figure, the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The retainer 20 has two claw portions 51 and 51 protruding from the end surface on one circumferential end surface of the fixed piece 50 ′ in parallel in the axial direction, and a protrusion that faces the claw portions 51 and 51 of the fixed piece 50 ′. Concave portions 49 and 49 that mesh with the claw portions 51 and 51 are arranged side by side on the wall portion 48 of 44. As a result, the fixed piece 50 ′ and the second element 40 can be reliably engaged, and the fixed piece 50 ′ can be prevented from dropping out of the gap. The shape and number of the claw portions 51 can be changed as appropriate.

  Further, in the first and second embodiments, the fixing pieces 50 and 50 ′ are press-fitted into the gap between the first element 30 and the second element 40, but the attachment method is not limited to press-fitting and is attached by adhesion. Also good. Further, the fixing pieces 50 and 50 ′ may not be attached to all the through holes 34.

(Third embodiment)
FIG. 6 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to a third embodiment of the present invention. The deep groove ball bearing of the third embodiment is the same as the deep groove ball bearing of the first embodiment except that the shape of the inner ring and the length of the shield plate are different. In the figure, the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The deep groove ball bearing 10 </ b> A of the third embodiment shown in FIG. 6 secures an opening serving as a lubricant supply port or discharge port, so that the inner diameter of the shield plate 14 is the same as the inner diameter of the cage 20. The both ends of the inner ring 12 in the axial direction are notched to form a tapered surface 12b to increase the opening area. Thereby, since the supply and discharge performance of the lubricating oil is not impaired, the lubricating oil does not stay and the temperature increase of the deep groove ball bearing 10A can be suppressed.

(Fourth embodiment)
FIG. 7 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to a fourth embodiment of the present invention. The deep groove ball bearing of the fourth embodiment is the same as the deep groove ball bearing of the first embodiment except that the shape of the inner ring and the length of the shield plate are different. In the figure, the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The deep groove ball bearing 10B of the fourth embodiment shown in FIG. 7 has an inner diameter of the shield plate 14 that is the same as the inner diameter of the cage 20 in order to secure an opening serving as a lubricant supply or discharge port. The both ends of the inner ring 12 in the axial direction are notched to form stepped portions 12c to increase the opening area. Thereby, since the supply / discharge property of the lubricating oil is not impaired, the lubricating oil does not stay and the temperature increase of the deep groove ball bearing 10 can be suppressed.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimension, numerical value, form, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 1st Embodiment of this invention. It is a whole perspective view of the holder | retainer integrated in the deep groove ball bearing of FIG. It is a disassembled perspective view of each component of the holder | retainer of FIG. It is explanatory drawing explaining the assembly | attachment method of a holder | retainer. It is explanatory drawing of the holder | retainer integrated in the deep groove ball bearing which is 2nd Embodiment of this invention. It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 3rd Embodiment of this invention. It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 4th Embodiment of this invention. It is a perspective view which shows the conventional crown type cage for rolling bearings. It is principal part sectional drawing for demonstrating the malfunction of the rolling bearing incorporating the conventional crown type cage for rolling bearings. It is principal part sectional drawing of the cage for rolling bearings described in patent document 1. FIG. It is principal part sectional drawing of the combination holder | retainer of patent document 2. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10, 10A, 10B Rolling bearing 11 Outer ring 12 Inner ring 13 Ball 14 Shield plate 20 Retainer 25 Pocket 30 First element 33 Pocket surface 34 Through-hole 37 Step part 40 Second element 43 Pocket surface 44 Projection part 47 Grow part 50 Fixed piece

Claims (5)

A deep groove ball bearing retainer comprising an annular portion and pillar portions arranged at a predetermined interval, wherein a pocket for holding a ball is formed,
A first element having a through-hole formed in the pillar portion in the axial direction and provided with a step portion on one circumferential side;
A second element having a protruding portion protruding in the axial direction on a front end surface of the column portion, and having a flange portion engageable with the stepped portion on the protruding portion;
A fixing piece that fills a gap between the projecting portion inserted in the other circumferential direction of the through hole in a state where the step portion of the first element and the flange portion of the second element are engaged with each other. A cage for deep groove ball bearings.   When the protrusion of the second element is inserted into the through hole of the first element, the phase of the pocket surfaces of the first and second elements deviates from the phase of each other where the pocket is formed. The deep groove ball bearing retainer according to claim 1, wherein the retainer is a deep groove ball bearing.   The deep groove ball bearing retainer according to claim 1 or 2, wherein the pocket has a spherical shape, and the radial positioning of the ball is performed by engagement of the ball and the pocket. In deep groove ball bearings, in which the outer ring and inner ring are raceway rings, and a plurality of balls are rotatably held by a cage.
The deep groove ball bearing, wherein the cage is the deep groove ball bearing cage according to any one of claims 1 to 3. Used in oil lubrication,
Shield plates extending in the radial direction are installed at both ends of the outer ring,
The deep groove ball bearing according to claim 4, wherein an opening is provided between a tip of the shield plate and the inner ring.

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