JP5030650B2 - Rolling bearing - Google Patents

Description

  The present invention relates to a rolling bearing that achieves a solution to grease leakage of a ball bearing used for, for example, a rotation support portion and a solution to an adsorption phenomenon.

Of the bearings used for the rotation support portion, as a countermeasure against grease leakage of a bearing that uses balls as rolling elements, a countermeasure is usually taken with a seal shape. However, when the seal type is a non-contact type, the torque is low, but there is a problem in grease leakage resistance and dust resistance. If the seal type is a contact type, the dust resistance is increased, but the torque is increased. In addition, grease leakage also occurs due to a so-called breathing phenomenon. In order to solve these problems, there is a method in which a protrusion is provided on the bearing sliding surface of the lip portion of the contact seal to ensure an air passage (for example, Patent Document 1).
JP 2000-257640 A (2nd page, lower right column, FIG. 3) JP 2003-262234 A

  In the device disclosed in Patent Document 1, after the protrusion of the lip portion is rubbed, an air passage cannot be secured and the adsorption phenomenon cannot be prevented. In addition, foreign matter enters from the outside of the bearing before the protrusions are rubbed. In addition, a technique has been proposed in which a pair of slinger is fitted and fixed to a fixed shaft to which a sealed type rolling bearing is fitted so as to sandwich the rolling bearing in the axial direction (for example, Patent Document 2). A space for providing a slinger in the axial direction is required, and the number of parts increases and the manufacturing cost increases.

  An object of the present invention is to provide a rolling bearing capable of simultaneously achieving low torque, grease leakage resistance, dust resistance and space saving at low cost.

Rolling of the first inventions of this invention (claim 1), a plurality of balls are held in a cage interposed between the inner and outer rings, closing both end surfaces of the raceway of the outer ring in the seal member, the In a rolling bearing in which one peripheral portion of the seal member is in sliding contact with a seal groove formed at the end of one track and the other peripheral portion is fixed to the end of the other track, the seal member is in sliding contact with the seal groove. The seal lip is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside of the bearing and the outside of the bearing partitioned by the seal member, and the seal lip is pushed inward. When this projection comes into contact with the inner surface of the seal groove, the seal lip in the vicinity of the contact is partially elastically deformed by the contact of the projection to form an air passage that communicates the inside of the bearing with the outside of the bearing. And a state in which the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur, and the cage has a pocket for holding a plurality of balls, respectively. It is a ring-shaped cage that has a plurality of pockets in the direction, and the inner surface of each pocket has a concave curved surface with a portion whose inner diameter side is closer to the cage inner diameter side opening edge than the ball arrangement pitch circle. Te, wherein each pocket, the cage inner surface of the portion along the sealing member, characterized in that the recess extends in the cage outer diametric side from an opening edge of the cage inner diameter side digits set.

  According to this configuration, when the adsorption phenomenon occurs, the seal lip is pushed inward. At the same time as the seal lip is pushed, the protrusion on the inner surface of the seal lip is pressed against the inner surface of the seal groove. At this time, the seal lip near the contact position of the protrusion and pressed against the inner surface of the seal groove is partially elastically deformed with respect to the other part due to the presence of the protrusion. That is, the seal lip in the vicinity of the contact position of the protrusion cannot contact the inner side surface of the seal groove, and an air passage that connects the inside of the bearing and the outside of the bearing is formed by non-contact.

Further, when both the protrusion and the seal lip tip are in contact with the inner surface of the seal groove, due to the difference in contact pressure between the protrusion and the seal lip tip, the protrusion tip has a sliding resistance of the seal lip. It becomes larger than the sliding resistance of the tip. When the bearing is rotated in this state, twisting occurs so that the tip of the seal lip undulates and an air passage is formed.
For this reason, the pressure balance inside and outside the bearing can be kept instantaneously uniform to prevent the adsorption phenomenon. Further, the air passage for maintaining the pressure balance is immediately closed when the pressure balance between the inside and outside of the bearing is uniform, that is, no pressure difference occurs, and the seal lip is in a normal state. At this time, the protrusion is not in contact with the inner surface of the seal groove. Therefore, it is possible to minimize the intrusion of foreign matters from outside, and therefore the air passage is narrow, it has name that grease leakage.
Also, by providing a recess on the inner surface of each pocket of the cage that extends from the opening edge on the inner diameter side of the cage to the outer diameter side of the cage, it is difficult for grease to adhere to the seal groove of the inner ring, and grease leakage can be prevented. . Therefore, it is not necessary to change the design of the shape of the seal groove, and it is not necessary to secure a space for providing a slinger or the like in the axial direction of the bearing. Therefore, the number of parts can be made smaller than that described in the above patent document, and the manufacturing cost can be reduced.
In this invention, you may make the width | variety of the holder circumferential direction in the said recessed part larger than the half of the width | variety of the holder | retainer circumferential direction of the said pocket.
In the present invention, the recessed portion may have two locations.
When the number of the recesses is two, the positions of the recesses may be 40 ° ± 15 ° in the circumferential orientation angle with respect to the center in the circumferential direction of the cage at the opening edge of the pocket.

In the rolling bearing according to the second aspect of the present invention (Claim 5), a plurality of balls interposed between the inner and outer rings are held by a cage, and both end surfaces of both raceways of these inner and outer rings are closed with seal members. In a rolling bearing in which one peripheral portion of the members is in sliding contact with the seal groove formed at the end of one track and the other peripheral portion is fixed to the end of the other track, the seal member is in sliding contact with the seal groove. The seal lip is used as a peripheral edge, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside and outside of the bearing partitioned by the seal member, and the seal lip is pushed inward. The protrusion contacts the inner surface of the seal groove, and the contact of the protrusion partially elastically deforms the seal lip in the vicinity of the contact to form an air passage that communicates the inside of the bearing with the outside of the bearing. And a state in which the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur, and the cage forms pockets for holding a plurality of balls, respectively. A plurality of spherical shell-shaped portions that are open only in the radial direction of the cage, and a flat plate-like portion that is a portion between adjacent pockets, which are alternately arranged, and more than the ball arrangement pitch circle in the spherical shell-shaped portion. In the inner diameter side portion, at least the thickness of the portion located at the outer diameter surface portion of the shoulder height on both sides of the raceway surface of the bearing inner ring is made thinner than the plate thickness of the flat plate portion.

Rolling of the third inventions in the present invention (Claim 6), a plurality of balls are held in a cage interposed between the inner and outer rings, closing both end surfaces of the raceway of the outer ring in the seal member, the In a rolling bearing in which one peripheral portion of the seal member is in sliding contact with a seal groove formed at the end of one track and the other peripheral portion is fixed to the end of the other track, the seal member is in sliding contact with the seal groove. The seal lip is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside of the bearing and the outside of the bearing partitioned by the seal member, and the seal lip is pushed inward. When this projection comes into contact with the inner surface of the seal groove, the seal lip in the vicinity of the contact is partially elastically deformed by the contact of the projection to form an air passage that communicates the inside of the bearing with the outside of the bearing. A condition, the projections on the inner surface of the seal groove when the pressure difference is not generated is displaceably configured over the state of the non-contact, said retainer forms a pocket for holding a plurality of balls respectively A plurality of spherical shell-shaped portions that are opened only in the radial direction of the cage, and a flat plate-like portion that is a portion between adjacent pockets, and is a circumferential portion having the pockets The inner peripheral surface of the shell-shaped part is formed in a shape in which the intermediate part of the width in the circumferential direction of the cage is recessed toward the outer diameter side when viewed from the axial direction. radius, characterized by being larger than the radius of the circumferential portions cage center of the inner diameter of between pocket.

According to this configuration, when the adsorption phenomenon occurs, the seal lip is pushed inward, and at the same time, the protrusion is pushed against the inner surface of the seal groove. At this time, the seal lip in the vicinity of the protrusion contact position is partially elastically deformed with respect to other portions, and the seal lip in the vicinity of the protrusion contact position is not in contact with the inner surface of the seal groove. An air passage that communicates the inside and the outside of the bearing is formed. When there is no pressure difference between the inside of the bearing and the inside of the bearing, the protrusion is in a non-contact state with respect to the inner surface of the seal groove. At this time, since the air passage is closed, entry of foreign matter from the outside can be minimized, and the air passage is narrow, so that the grease does not leak.
In addition, since the radius from the cage center of the inner diameter of the circumferential portion with the pocket of the cage is larger than the radius from the cage center of the inner diameter of the circumferential portion between the pockets, the inner ring shoulder and inner ring Grease hardly adheres to the seal groove. This appears particularly when the outer ring rotates. Thereby, leakage of grease can be prevented regardless of whether the seal is a contact type or a non-contact type. Further, since it is not necessary to increase the tightening force of the seal lip, the torque does not increase .
The position of the portion where the inner diameter of the circumferential portion having the pocket is increased may include a range overlapping in the axial direction with the inner ring outer diameter surface which is the shoulder height of the inner ring.

  In the present invention, the protrusions may be formed on the inner surface of the seal lip at a predetermined interval along the tip sliding contact portion. In this case, when the adsorption phenomenon occurs, the protrusion is pressed against the inner surface of the seal groove, and the seal lip near the protrusion is elastically deformed. For this reason, the tip sliding contact portion of the seal lip and the inner surface of the seal groove are separated from each other, and an air passage is formed around the protrusion so as to communicate the inside of the bearing and the outside of the bearing.

  In the present invention, the projection may be formed on the inner surface of the seal lip by a ridge protruding over the entire circumference along the tip sliding contact portion, and a notch groove may be provided in a direction crossing the ridge. In this case, when an adsorption phenomenon occurs, the protrusion is pressed against the inner surface of the seal groove, and the seal lip near the protrusion is elastically deformed. For this reason, the tip sliding contact portion of the seal lip is separated from the inner surface of the seal groove, and an air passage that communicates the inside of the bearing and the outside of the bearing is formed in the notch groove of the protrusion.

In the rolling bearing according to the first aspect of the present invention, the periphery of the seal member is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion causes a pressure difference between the inside of the bearing and the outside of the bearing. When pushed inward, the protrusion contacts the inner surface of the seal groove, so that the seal lip in the vicinity of the contact is partially elastically deformed to form an air passage, and the pressure difference does not occur. In some cases, the protrusion is displaceable over the inner surface of the seal groove over a state where the protrusion is not in contact.
Furthermore, the inner surface of each pocket of the cage is a ring-shaped cage in which the portion on the inner diameter side of the ball arrangement pitch circle is a concave curved surface having a smaller diameter as it approaches the cage inner diameter side opening edge, of each pocket, the inner surface of the retainer portion along said sealing member, since the recessed portion extending cage outer diametric side from an opening edge of the cage inner diameter side digits set, low torque, resistance to grease leakage resistance, dust It is possible to realize a rolling bearing capable of achieving high performance and space saving at the same time and at low cost.

In the rolling bearing according to the second aspect of the present invention, a plurality of balls interposed between the inner and outer rings are held by a cage, both end surfaces of both raceways of these inner and outer rings are closed with seal members, and one peripheral edge of the seal members In a rolling bearing in which the portion is in sliding contact with the seal groove formed at the end of one track and the other peripheral portion is fixed to the end of the other track, the periphery of the seal member in sliding contact with the seal groove is used as a seal lip. A protrusion is provided on the inner surface of the seal lip, and the protrusion has an inner surface of the seal groove when a pressure difference is generated between the inside of the bearing and the outside of the bearing partitioned by the seal member and the seal lip is pushed inward. The projections contact each other, and the contact between the projections partially elastically deforms the seal lip in the vicinity of the contact to form an air passage that connects the inside of the bearing and the outside of the bearing, and the pressure difference. When this does not occur, the inner surface of the seal groove is configured to be displaceable over a state in which the protrusion is not in contact, and the retainer is formed with pockets for retaining a plurality of balls, and is opened only in the retainer radial direction. A plurality of spherical shell-shaped portions and flat plate-shaped portions that are portions between adjacent pockets are alternately arranged, and at least a bearing in a portion on the inner diameter side of the ball arrangement pitch circle in the spherical shell-shaped portion The thickness of the part located on the outer diameter surface part of the shoulder height on both sides of the raceway surface of the inner ring is made thinner than the plate thickness of the flat plate part, so low torque, grease leakage resistance, dust resistance and space saving are achieved. At the same time, a rolling bearing that can be achieved at low cost can be realized.

In the rolling bearing according to the third aspect of the present invention, a protrusion is provided on the inner surface of the seal lip, and the protrusion has a pressure difference between the inside of the bearing partitioned by the seal member and the outside of the bearing, so that the seal lip is pushed inward. When this projection comes into contact with the inner surface of the seal groove, the seal lip in the vicinity of the contact is partially elastically deformed by the contact of the projection to form an air passage that communicates the inside of the bearing with the outside of the bearing. It is configured to be displaceable over a state where the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur.
Further, the cage is formed by alternately forming a plurality of spherical shell-shaped portions that form pockets that respectively hold a plurality of balls and that are opened only in the radial direction of the cage, and flat plate portions that are portions between adjacent pockets. The inner peripheral surface of the spherical shell-shaped portion, which is a circumferential portion having the pocket, has a shape in which an intermediate portion of the width in the cage circumferential direction is recessed toward the outer diameter side when viewed from the axial direction. It is the radius from the cage center as the inner diameter of the portion becomes the recessed shape, because of the greater than the radius from the circumferential portion cage center of the inner diameter of between pockets, low torque, resistance to grease leakage , Dust resistance and space saving can be achieved at the same time and at a low cost.

  An embodiment of the present invention will be described with reference to FIGS. This rolling bearing includes an inner ring 1, an outer ring 2, a plurality of balls 3 provided so as to freely roll between the inner ring 1 and the outer ring 2, a cage 4 that holds these balls 3, an inner ring 1, and And an annular seal member SL fitted to both axial end surfaces of the outer ring 2. An inner ring raceway 5 on which the balls 3 roll is provided on the outer diameter surface of the inner ring 1, and an outer ring raceway 6 facing the inner ring raceway 5 is provided on the inner diameter surface of the outer ring 2. Circumferential seal grooves 9 and 9 are formed on both sides of the inner ring raceway 5, and seal member locking grooves 8 and 8 are formed on the inner diameter surface of the outer ring 2 facing the seal grooves 9. The outer peripheral edge 7 of the seal member SL is locked in the seal member locking groove 8.

  The seal member SL is obtained by reinforcing an elastic body 11 made of synthetic rubber or the like with a metal core 10, and a seal lip 12 extending inward in the radial direction is formed on the elastic body 11. As a synthetic rubber used for the elastic body 11, hydrogenated nitrile rubber or ester-resistant acrylic rubber can be employed. Hydrogenated nitrile rubber is superior to nitrile rubber generally used as a sealing member and has no problem in chemical resistance, so it maintains stable properties and can be used at higher temperatures. it can. Ester-resistant acrylic rubber, like hydrogenated nitrile rubber, is superior in heat resistance compared to nitrile rubber and has improved chemical resistance against chemicals such as acrylic rubber ester oil and air conditioner compressor oil. Therefore, stable properties can be maintained and use at higher temperatures is possible.

  The seal lip 12 includes a waist portion 13 in which the thickness of the elastic body 11 is reduced, a dust lip 14 extending axially outward from an end portion of the waist portion 13, and an inward direction from the end portion of the waist portion 13. And a main lip 15 whose tip is in sliding contact with the inner surface 16 of the seal groove 9 is formed. As shown in FIG. 2, the main lip 15 has a protrusion 17 protruding toward the inner surface 16 on a surface facing the inner surface 16 of the seal groove 9. The protrusion 17 is provided on the inner side of the main lip 15 at one or a plurality of locations along the tip, that is, the inner peripheral edge of the seal member SL.

  When the sealing member SL configured as described above is locked in the sealing member locking groove 8 of the outer ring 2, as shown in FIG. 3A, the tip of the main lip 15 is the inner surface of the sealing groove 9. 16 is brought into contact. In this state, the protrusion 17 does not contact the inner surface 16 of the seal groove 9 in a state where there is no pressure difference between the inside and the outside of the bearing, so that the sealing performance is not impaired.

  When the bearing is cooled after the temperature change during the transportation of the rolling bearing or the generation of frictional heat due to the rotation of the rolling bearing, a pressure difference between the inside and outside of the bearing is generated, and the seal lip 12 is placed inside. When pushed in, as shown in FIG. 3B, the protrusion 17 provided on the main lip 15 contacts the inner side surface 16 of the seal groove 9. As a result, the tip of the main lip 15 in the vicinity of the protrusion 17 is elastically deformed outward and is separated from the inner surface 16 of the seal groove 9.

  In this state, an air passage 18 that communicates between the inside and outside of the bearing is formed around the protrusion 17, and the pressure difference between the inside and outside of the bearing is eliminated, thereby preventing the adsorption phenomenon of the bearing. Since the air passage 18 is formed only around the protrusion 17, the tip of the main lip 15 where the protrusion 17 does not exist is kept in contact with the inner surface 16 of the seal groove 9, and the sealing performance is Secured. Further, as soon as the pressure difference between the inside and outside of the bearing is eliminated, the seal lip 12 returns to the normal state, and the deterioration of the sealing performance is minimized.

  If the pressure difference between the inside and outside of the bearing is large and the protrusion 17 is crushed due to contact with the inner surface 16 of the seal groove 9 or the pressure difference inside and outside the bearing is very small, as shown in FIG. Both the tip portions of the lip 15 are in a suction state in contact with the inner side surface 16 of the seal groove 9. In the suction state in this case, the contact pressure of the tip of the protrusion 17 that contacts the inner surface 16 of the seal groove 9 is larger than the tip of the main lip 15 that contacts the inner surface 16 of the seal groove 9.

  Due to the difference in contact pressure, the sliding resistance of the tip of the projection 17 becomes larger than the sliding resistance of the tip of the main lip 15, and when the bearing is rotated in this attracted state, FIG. As shown, the protrusion 17 maintains a state in contact with the inner surface 16 of the seal groove 9 and tries to rotate together with the inner surface 16. At this time, since the front end portion of the main lip 15 slides, as shown in FIG. 5B, the front end portion of the main lip 15 and the inner peripheral edge of the seal member SL are elastic so as to undulate. Deformed. An air passage 19 is formed when the tip of the main lip 15 is elastically deformed, and suction is released.

  Further, in the rolling bearing according to this embodiment, by using the cage 4 shown below, it is difficult for grease to adhere to the seal groove 9 of the inner ring 1, and grease leakage can be reliably prevented. The cage 4 will be described with reference to FIGS.

  As shown in a perspective view in FIG. 6, the retainer 4 has pockets 50 for holding the balls 3 (FIG. 1) at a plurality of locations in the circumferential direction, and the inner surface of each pocket 50 has a concave spherical shape. It is ring-shaped. The retainer 4 is formed by joining two annular retainer halves 51 shown in a perspective view in FIG. 7 so as to face each other in the axial direction and joining them together by a rivet 53 inserted through a rivet hole 52. Composed. These cage halves 51 have a plurality of spherical shell-shaped plate portions 50A whose inner surfaces form half of the pockets 50, and a flat plate portion 51a serving as a portion between adjacent pockets 50; The spherical shell plate portions 50A are alternately arranged in the circumferential direction. The spherical shell-shaped plate portion 50A is a part that becomes a part of the spherical shell, in other words, a counter-sink-shaped bulged portion in which both the inner and outer surfaces are spherical. The projected shape in the axial direction of the cage half 51 is a ring shape having a constant radial width over the entire circumference.

  A part of the cage half 51 is enlarged and shown in a perspective view in FIG. FIG. 8 is a diagram in the case where the pocket inner surface is a monotonous spherical surface in a portion corresponding to FIG. 9. In FIG. 8, a portion A indicated by a two-dot chain line indicates a circumferential band in which the flat plate portions 51a of the cage half 51 are arranged in the circumferential direction. The spherical shell plate portion 50A, which is a half of the pocket 50, is formed at a portion of the circumferential band A that is not the flat plate portion 51a. One side portion of the spherical shell plate portion 50 </ b> A in the drawing is an inner diameter side portion 50 </ b> Ai of the cage 4, and the other side portion of the spherical shell plate portion 50 </ b> A is an outer diameter side portion 50 </ b> Ao of the cage 4.

  As shown in FIG. 9, the inner surface of the pocket 50 (spherical shell plate portion 50 </ b> A) of the cage 4 according to this embodiment is formed on the inner diameter side portion 50 </ b> Ai of the cage 4 from the opening edge on the cage inner diameter side. A recess 54 extending toward the outer diameter side is provided, and a cross-sectional shape of the inner surface of the recess 54 along the circumferential direction of the cage (that is, a cross-sectional shape taken along a plane perpendicular to the cage central axis) is defined as the inner surface of the pocket 50. An arc shape having a radius of curvature Rb smaller than the radius of curvature Ra of the concave spherical surface.

The recessed portion 54 is provided at one location so as to spread from the center OW50 in the cage circumferential direction at the opening edge of the pocket 50 to one side, and the width W54 of the recessed portion 54 is the width W50 in the cage circumferential direction of the pocket 50. The width is almost the whole. Width W54 of the recessed portion 54, than half the width W50 of the pocket 50 has become greatly, and more preferably 2/3 or more, or 3/4 or more.

  The inner surface shape of the recessed portion 54 is a cylindrical surface shape substantially along the surface of the virtual cylinder V centered on the straight line L in the radial direction of the cage 4 as shown in FIG. The virtual cylinder V may be the surface of a grindstone that processes the recess 54. The concave portion 54 extends from the opening edge on the inner diameter side of the cage to the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases, that is, gradually, from the inner diameter edge of the cage to the ball arrangement pitch circle PCD. The shape is shallow and narrow. In this embodiment, the dent 54 extends to the ball arrangement pitch circle PCD. However, the dent 54 may extend slightly to the outer diameter side of the cage from the ball arrangement pitch circle PCD, or slightly to the ball arrangement pitch circle PCD. You may not reach it. The ball arrangement pitch circle PCD is also called a pocket PCD.

  The depth of the concave portion 54 is such that the distance Rc from the center O50 of the concave spherical surface of the pocket inner surface to the deepest position of the concave portion 54 is 1.05 times or more the radius of the ball 8 (just 1.05 times). Preferably). The radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 50 is slightly larger than the radius of the ball 8 and is less than 1.05 of the radius of the ball 8.

  FIG. 10 shows another example of the shape of the inner surface of the pocket 50 (spherical shell plate portion 50A) of the cage 4. In this example, two recessed portions 54A provided in the inner diameter side portion 50Ai of the inner surface of the pocket 50 (spherical shell-shaped plate portion 50A) are positioned on both sides of the center OW50 in the cage circumferential direction at the opening edge of the pocket 50. It is said. The inner surface shape of each recess 54A is such that the cross-sectional shape along the circumferential direction of the cage (that is, the cross-sectional shape taken along the plane perpendicular to the central axis of the cage) is larger than the radius of curvature Ra of the concave spherical surface serving as the inner surface of the pocket 50. It has an arc shape with a small radius of curvature RAb, and more specifically, as shown in FIG. is there. The recessed portion 54A extends from the opening edge on the inner diameter side of the cage to the vicinity of the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases from the inner diameter edge of the cage to the ball arrangement pitch circle PCD. The shape gradually becomes shallower and narrower.

The positions of the two recessed portions 54A are, for example, two symmetrical places where the circumferential orientation angle with respect to the center OW50 in the circumferential direction of the cage at the opening edge of the pocket 50 is 40 ° ± 15 °. Also in this example, the depth of the recessed portion 54A is such that the distance RAc from the center O50 of the concave spherical surface of the pocket inner surface to the deepest position of the recessed portion 54A is 1.05 times or more the radius of the ball 3. Is preferable (it may be just 1.05 times).
In this embodiment, the number of the recessed portions 54A is two, but may be three or more.

  FIG. 11 shows still another example of the shape of the inner surface of the pocket 50 (spherical shell plate portion 50A) of the cage 4 (FIG. 1). In this embodiment, in the embodiment of FIG. 10, the cross-sectional shape (cross-sectional shape along the circumferential direction of the cage) of the recessed portion 54A is a polygonal shape instead of an arc shape. Specifically, as shown in FIG. 5B, a polygonal shape substantially along the surface of each polygonal column (regular decagonal column in the illustrated example) VC centered on the straight line LA in the radial direction of the cage 4. It is. The recessed portion 54C extends from the opening edge on the cage inner diameter side to the vicinity of the ball arrangement pitch circle PCD in the radial direction of the cage, and gradually decreases from the cage inner edge to the ball arrangement pitch circle PCD. The shape gradually becomes shallower and narrower. Other configurations in this embodiment are the same as those in the example of FIG.

  FIG. 12 shows still another example of the shape of the inner surface of the pocket 50 (spherical shell plate portion 50A) of the cage 4. In this example, the recessed portions 54B provided in the inner diameter side portion 50Ai of the inner surface of the pocket 50 (spherical shell-shaped plate portion 50A) are positioned on both sides of the center OW50 in the cage circumferential direction at the opening edge of the pocket 50. Although it is the same as that of embodiment of FIG. 6 by being provided in the location, each recessed part 54B is extended to the cage | basket outer-diameter edge vicinity. The cross-sectional shape along the circumferential direction of the cage of the inner surface of the recessed portion 54B is an arc shape having a curvature radius RBb smaller than the curvature radius Ra of the concave spherical surface serving as the inner surface of the pocket 50. FIG. As shown, the shape is substantially along the surface of one virtual ring VB. The virtual ring VB may be an outer peripheral surface of a grindstone that processes the recess 54B. The virtual ring VB has a ring outer diameter that fits in the pocket 50 and has a donut shape with a circular cross-sectional shape at an arbitrary circumferential position, and the ring center OVB is placed on the cage center axis O as shown in FIG. It has an inclination to it.

In addition, in this invention, the cross-sectional shape along the cage circumferential direction of the recessed portions 54A to 54C is not limited to the shape of each example of FIGS. 8 to 12, but a partial oval shape, a rectangular groove shape, a trapezoidal groove shape, Any other cross-sectional shape may be used. In addition, the cross-sectional shape of the recesses 54A to 54C may be asymmetric with respect to the center of the recess.
The inner surface shape of the pocket 50 is not limited to a spherical shape, and may be any shape as long as the inner diameter side portion of the pocket arrangement pitch circle PCD becomes a smaller diameter as it approaches the cage inner diameter side opening edge, for example, the ball arrangement pitch circle PCD. Further, the outer diameter side portion may be a cylindrical surface shape, and the inner diameter side portion may be a conical surface shape.

  FIG. 14 shows a method for manufacturing the cage 4. This manufacturing method is a method of manufacturing an iron plate punching cage, in which a steel plate is first pressed to punch a ring-shaped metal strip 55. Next, as shown in FIG. 14A, a convex press die 56 for molding the inner surface of the spherical shell plate portion 50A of the cage half 51 and the outer surface of the spherical shell plate portion 50A are molded. A press die set 58 comprising a concave press die 57 is prepared, and the ring-shaped metal strip 55 is sandwiched between the convex press die 56 and the concave press die 57, and FIG. The cage half 51 is press-molded as in B). This press molding may be performed in two stages of rough pressing and finishing pressing, or may be performed once.

Although only one convex press die 56 and one concave press die 57 are shown in the drawing, each of the convex press die 56 and the concave press die 57 is a cage half 51. The same number of the spherical shell plate portions 50A are arranged in the circumferential direction as a single mold, and a plurality of spherical shell plate portions 50A are formed at the same time.
The two retainer halves 51 thus obtained are overlapped as shown in FIG. 14C, and the portion where the flat plate portion 51a of the retainer half 51 is overlapped as shown in FIG. To form a cage 4.

  FIG. 15 shows the convex side press die 56 and the concave side press die 57 used for the finishing pressing step in press molding for molding the cage half 51 of FIG. The hemispherical convex surface of the convex side press die 56 is partially formed with a concave portion molding die portion 56a for molding the inner surface of the concave portion 54A in the pocket 50 (spherical shell plate portion 50A). Further, the concave side press mold 57 is partially formed with a concave portion back surface molding die portion 57a for molding the outer surface of the concave portion 54A in the pocket 50 (spherical shell plate portion 50A). Although a convex part will be formed in the outer surface side of a holder | retainer pocket, if it is non-contact with a seal | sticker, there is no functional problem. In this case, the convex-side press die 56 and the concave-side press die 57 are also provided as a single die corresponding to the number of the spherical shell plate portions 50A of the cage half 51, and have a plurality of spherical shell shapes. The plate portion 50A is formed at the same time.

When the cage half 51 shown in FIG. 10 is formed, the inner surface of the spherical shell-like plate portion 50A has a shape having a concave portion 54A in a part of a simple hemispherical concave surface. If the concave portion 54A is further press-molded into a part of the hemispherical concave surface after forming the concave shape, the manufacturing process is increased by one step as compared with the case of forming a conventional steel punching cage. .
In this embodiment, as described above, for forming a concave portion, the inner surface of the concave portion 54A in the pocket 50 (spherical shell plate portion 50A) is formed on the hemispherical convex surface of the convex press die 56 used in the finishing pressing step. Since the mold portion 56a is partially formed, the recessed portion 54A can be formed at the same time in the finishing pushing process, and the cage 4 can be efficiently manufactured without increasing the manufacturing process.

  Further, the shape and surface roughness of the hemispherical convex surface of the convex press die 56 used in the finishing pressing step are transferred to the inner surface of the cage pocket 50, and the pocket inner surface is inserted into the ball 3 ( In order to come into contact with FIG. 1), it is necessary to reduce the surface roughness of the pocket inner surface. Since the inner surface of the pocket is a simple concave spherical surface in the conventional iron plate punching cage, the surface roughness is reduced by polishing the hemispherical convex surface of the convex press die with a concave grinding stone or the like. However, in the case of this embodiment, as described above, the hemispherical convex surface of the convex-side press die 56 is a part of a simple hemispherical convex surface, and a concave portion molding die portion 56a corresponding to the concave portion 54A of the pocket inner surface. The surface roughness cannot be reduced by polishing with a concave-shaped grindstone or the like as in the conventional example.

  Therefore, in this embodiment, the convex convex spherical surface of the convex press die 56 used in the finishing pressing step is surface-finished by shot blasting, polishing with an electron beam, or lapping by injection of an abrasive. In this case, lapping is generated by obtaining abrasive material having elasticity and adhesiveness by adding moisture to the abrasive grains and sliding the abrasive material on the surface of a mold as a workpiece at high speed. A method of surface finishing by frictional force is preferred. As such wrapping, aero wrapping (Yamashi Towers Co., Ltd.) sold as a mold ultra-mirror finishing device can be employed. As described above, the surface of the convex spherical surface of the convex press die 56 is finished by shot blasting, electron beam, or lapping by jetting an abrasive, so that there is no need for manual polishing, and there is no unevenness and low cost. The surface roughness of the convex convex spherical surface of the side press die 56 can be reduced.

FIGS. 16-18 shows the test result which confirmed the grease adhesion state. In this test, a ball bearing incorporating the cage 4 of this embodiment (the embodiment of FIG. 9 and the embodiment of FIG. 10) and a ball bearing incorporating a general iron plate punched cage are shown in the following table. A comparison was made by driving under the condition of 1.
FIG. 16 and FIG. 17 show the grease adhesion state of the ball bearing using the cage 4 of this embodiment (the embodiment of FIG. 9 and the embodiment of FIG. 10 respectively), and FIG. 18 is a general iron punching cage. The grease adhesion state of the ball bearing using

From the test results shown in FIGS. 16 to 18, in the ball bearing (FIG. 18) incorporating a general steel plate punched cage, grease adheres to the inner ring seal groove, but the ball bearing incorporating the cage 4 of this embodiment. (Examples of FIGS. 16 and 17) show that there is no adhesion of grease.
In the rolling bearing cage 4 according to this embodiment, the shape of the pocket 50 is different from that of the conventional example as described above, so that the adhesion of grease to the shoulder portion of the inner ring can be eliminated. In other words, since a recess is provided at the opening edge on the inner diameter side of the cage, where the grease adheres most to the ball, scraping of the surface of the ball when grease scraping occurs reduces the inner diameter of the cage. The amount of grease that accumulates on the surface is reduced.

  Therefore, grease does not adhere to the inner ring seal groove, and no grease leakage occurs regardless of whether a contact type or non-contact type seal is used. This effect is characteristic especially when the outer ring rotates. Therefore, there is no problem caused by the grease adhering to the seal unlike a general iron plate punched cage. Furthermore, since it is not necessary to add an element for preventing grease leakage to the sealing function, a seal design specialized for muddy water resistance, dust resistance, and low torque is possible. Further, since the ball bearing retainer 4 of this embodiment can be pressed, a high-strength one can be manufactured at a low cost, and the distance from the seal does not change as compared with a general iron punching retainer.

  In each of the above embodiments, the case of the iron plate punched cage is shown, but the present invention can also be applied to the case of the resin cage 59 as shown in FIGS. 19 and 20. The resin cage 59 has two annular bodies 60, 60 made of a resin molded product. A plurality of hemispherical pockets 61A along the outer periphery of the ball are formed at equal intervals in the circumferential direction on one side surface of each annular body 60 that abuts each other. Between the adjacent pockets 61 </ b> A and 61 </ b> A, an engagement hole 62 and an engagement claw 63 serving as a coupling portion are provided, and the engagement claw 63 of one annular body 60 is connected to the engagement hole 62 of the other annular body 60. By inserting, both annular bodies 60 are joined together to form a cage 59.

According to the configuration of the rolling bearing described above, since the protrusion 17 is provided on the inner surface of the seal lip 12, when the adsorption phenomenon occurs, the seal lip 12 is located on the inner side in the bearing axial direction as shown in FIG. The protrusion 17 on the inner surface of the seal lip 12 is pressed against the inner surface 16 of the seal groove 9 at the same time as the seal lip 12 is pressed. At this time, the tip of the main lip 15 near the contact position of the projection 17 and pressed against the inner surface 16 of the seal groove 9 is partially elastic with respect to other portions due to the presence of the projection 17. Deformed. That is, the main lip 15 in the seal lip 12 near the contact position of the protrusion 17 cannot contact the inner surface 16 of the seal groove 9, and an air passage 18 that communicates between the inside of the bearing and the outside of the bearing is formed by non-contact. Is done.
Further, as shown in FIG. 4, when both the protrusion 17 and the tip of the main lip 15 are in contact with the inner surface 16 of the seal groove 9, the difference in the contact pressure between the protrusion 17 and the tip of the main lip 15. Thus, the sliding resistance of the tip 17 a of the protrusion 17 is larger than the sliding resistance of the tip 15 a of the main lip 15. When the bearing is rotated in this state, the tip 15a of the main lip 15 is twisted so as to wave in an uneven shape, and an air passage 19 as shown in FIG. 5B is formed.
For this reason, the pressure balance inside and outside the bearing can be kept instantaneously uniform to prevent the adsorption phenomenon. Further, the air passage 19 for maintaining the pressure balance is immediately closed unless the pressure balance inside and outside the bearing is uniform, that is, no pressure difference occurs, and the seal lip 12 is brought into a normal state as shown in FIG. At this time, the protrusion 17 is not in contact with the inner surface 16 of the seal groove 9. Accordingly, the intrusion of foreign matter from the outside of the bearing can be minimized, and the air passage 19 is narrow, so that grease in the bearing does not leak.

  The cages 4 and 59 have pockets 50 that respectively hold a plurality of balls 8 at a plurality of locations in the circumferential direction, and the inner surfaces of the pockets 50 are held by the inner diameter side of the ball arrangement pitch circle PCD. It is a ring-shaped ring that has a concave curved surface that becomes smaller in diameter as it approaches the opening edge on the inner diameter side of the cage, and has a recess 54 (54A, 54B) that extends from the opening edge on the inner diameter side of the cage to the outer diameter side of the cage. , 54C), it is difficult for grease to adhere to the seal groove 9 of the inner ring 1, and grease leakage can be prevented. Therefore, it is not necessary to change the design of the shape of the seal groove, and it is not necessary to secure a space for providing a slinger or the like in the axial direction of the bearing. Therefore, the number of parts can be made smaller than that described in the aforementioned patent document, and the manufacturing cost can be reduced.

  For example, as shown in FIG. 9, the recessed portion 54 is provided at one position so as to spread from the center in the circumferential direction of the cage at the opening edge of the pocket 50 to a width W50 in the circumferential direction of the cage 50. The inner surface shape of the recess 54 is a cylindrical surface shape substantially along the surface of the virtual cylinder V centered on the straight line L in the radial direction of the cage 4. The recess 54 extends from the opening edge on the inner diameter side of the cage to the vicinity of the ball arrangement pitch circle PCD, and gradually becomes shallower and narrower as it approaches the ball arrangement pitch circle PCD from the inner diameter edge of the cage. Thus, the above-described actions and effects are achieved.

  Further, for example, as shown in FIG. 10, the recessed portions 54A are provided at a plurality of locations on both sides of the center OW50 in the cage circumferential direction at the opening edge of the pocket 50, and the inner surface shape of each recessed portion 54A is The concave portion 54A extends from the opening edge on the inner diameter side of the cage to the ball arrangement pitch circle PCD. The cylindrical surface shape is substantially along the surface of each virtual cylinder VA around the straight line LA in the radial direction of the cage 4. The shape is gradually shallower and narrower as it approaches the ball arrangement pitch circle PCD from the inner diameter edge of the cage, thereby providing the above-described operations and effects.

  Further, as shown in FIGS. 12 and 13, for example, as shown in FIGS. 12 and 13, the recessed portions 54 </ b> B are provided at two locations on both sides of the center OW50 in the circumferential direction of the cage at the opening edge of the pocket 50. The inner surface shape of these two recessed portions 54B extends to the vicinity of the edge, and is substantially along the surface of one virtual ring VB. The virtual ring VB has a ring outer diameter that fits in the pocket 50, and has an arbitrary circumference. The cross-sectional shape of the directional position is circular, and the ring center OVB has an inclination with respect to the cage center axis O, so that the above-described operations and effects are achieved.

21 to 23 show an embodiment corresponding to the second invention. The rolling bearing retainer 4A according to this embodiment is the same as the retainer 4 described above with reference to FIGS.
This retainer 4A is a retainer used for the rolling bearing described above with reference to FIG. 1 and has a ring shape having pockets 50 for retaining the balls 3 in a plurality of positions in the circumferential direction, and retains two annular bodies. The container half 51 is overlapped facing each other in the axial direction. Each of these cage halves 51 has a shape in which spherical shell-shaped plate portions 50A whose inner surfaces form half of the respective pockets and flat plate portions 51a that are portions between adjacent pockets 50 are alternately arranged in the circumferential direction. Is done. Each cage half 51 is a press-formed product of a metal plate (for example, an iron plate punched product), and the two cage halves 51 are mutually connected by a rivet 53 inserted into a rivet hole 52 provided in the flat plate portion 51a. Joined and constructed integrally. The above configuration is the same as that of the embodiment shown in FIGS.

Further, as shown in FIGS. 21 and 23, the retainer 4 </ b> A has a range that overlaps the inner ring outer diameter surface 1 a that is the shoulder height on both sides of the inner ring raceway 5 of the inner ring 1 in the axial direction.
The cage 4A of this embodiment has a thin portion 50Aa in the inner diameter side portion of the ball arrangement pitch circle PCD which is the ball arrangement pitch in the spherical shell plate portion 50A in the above configuration. The thin portion 50Aa is obtained by making the plate thickness t1 of the portion located on the inner ring outer diameter surface 1a, which is the shoulder height on both sides of the inner ring raceway 5 of the inner ring 1, thinner than the plate thickness t0 of the flat plate portion 51a. The inner ring outer diameter surface 1a which becomes the shoulder height is an outer diameter surface portion continuing at the height of the shoulder portion of the inner ring raceway 5 of the inner ring 1, and when the seal groove 9 is formed, the inner ring raceway 5 and the seal are sealed. It is an outer diameter surface portion between the grooves 9. The spherical shell-shaped plate portion 50A reduces the plate thickness t1 of the portion located in the axial range W of the inner ring outer diameter surface 1a. In addition, in FIG. 21, the cross-sectional shape when not reducing the thickness of the spherical shell plate portion 50A is indicated by an imaginary line.

  In the form in which the plate thickness t1 is reduced, the entire range from the portion corresponding to the ball arrangement pitch circle PCD to the inner diameter side in the radial direction of the cage may be reduced. Also, the ball arrangement pitch circle PCD and the inner diameter edge of the cage The range from the midway point to the inner diameter edge may be made thinner. In these cases, the plate thickness t1 may gradually become thinner toward the inner diameter side in the radial direction of the cage so that the inner diameter edge becomes the minimum plate thickness. You may do it. Furthermore, while maintaining the shape of the inner surface of the pocket of the spherical shell-shaped plate portion 50A, even if the plate thickness is reduced so that the shape of the outer surface changes, or while maintaining the shape of the outer surface of the spherical shell-shaped plate portion 50A, The plate thickness may be reduced so that the shape on the inner surface side of the pocket changes.

  Further, in this embodiment, as shown in FIG. 22, both ends are left thin in the arc-shaped range along the inner diameter edge of the spherical shell-like plate portion 50 </ b> A. Depending on the relationship between the inner ring outer diameter surface 1a and the width of the retainer 4A, as shown in FIG. 24, the thin-walled portions 50Aa are formed on both sides except the center of the arc of the inner diameter edge of the spherical shell-like plate portion 50A. It may be divided into two places.

  In this cage 4A, a thin-walled portion 50Aa is formed on the inner diameter portion of the spherical shell-shaped plate portion 50A constituting the pocket 50 in this way, and this thin-walled portion 50Aa is the inner ring outer diameter at the height of the shoulder portion of the inner ring 1. It is a portion that overlaps the surface 1a in the axial direction, and is a portion where the grease adhering to the surface of the ball 3 is scraped off by the cage 4A, or a portion where the scraped grease moves. If the plate thickness t1 of this portion 50Aa is thin, the amount of grease that can be deposited here decreases, and therefore the frequency and amount that can reach the inner ring outer diameter surface 1a of the inner ring 1 decreases, and as a result, the grease goes out of the bearing. Leakage can be prevented. That is, the grease easily moves to the outer diameter side of the cage 4A, and the amount of grease that can stay on the inner diameter side decreases.

However, reducing the overall plate thickness of the cage reduces the strength of the cage alone, so that the cage may be damaged when repeated stress is applied to the cage under misalignment or external vibration. It is difficult to occur.
Therefore, in the inner diameter portion of the cage 4A, the plate thickness is reduced only in the range W that overlaps the inner ring outer diameter surface 1a serving as the shoulder portion of the inner ring 1 in the axial direction, thereby substantially increasing the strength of the cage 4A. The ball bearing retainer 4A that can prevent the grease leakage is formed.

  Therefore, by using the cage in the rolling bearing, the frequency and amount that can reach the inner ring outer diameter surface 1a of the inner ring 1 is reduced, and as a result, leakage of grease to the outside of the bearing can be prevented. That is, the grease easily moves to the outer diameter side of the cage 4A, and the amount of grease that can stay on the inner diameter side can be reduced. Therefore, it is difficult for grease to adhere to the seal groove 9 of the inner ring 1, and grease leakage can be prevented. Further, according to the configuration of this rolling bearing, it is not necessary to change the design of the shape of the seal groove 9 of the inner ring 1, and it is not necessary to secure a space for providing a slinger or the like in the axial direction of the bearing, and the number of parts is also described above. The manufacturing cost can be reduced by reducing the manufacturing cost as described in the literature.

  In order to reduce the plate thickness t1, only the inner diameter side of the flat plate initially punched into the ring may be thinned and press molded. Further, in a press mold when a cage is formed by pressing from a circular plate having a uniform thickness, the clearance distribution between a pair of molds is reduced so that only the thickness of the region shown in FIGS. 22 and 24 is reduced. It may be changed. In this embodiment, the case of a deep groove ball bearing punch made of iron plate is shown. However, the second invention can be applied to the two-part resin cage described above with reference to FIGS. .

25 to 27 show an embodiment corresponding to the third invention . The rolling bearing cage 4B according to this embodiment is a cage used in the rolling bearing described above with reference to FIG. This cage 4B is a ring-shaped member, and the same number of window-like pockets 4Ba for accommodating and holding the balls 3 (FIG. 1) as the balls 3 are formed at equal intervals in the circumferential direction. The inner circumferential surface 4Bb of the circumferential portion with the pocket 4Ba is inclined so as to be recessed toward the outer diameter side, and the radius Rp from the cage center of the inner diameter of the circumferential portion with the pocket 4Ba is between the pockets 4Ba. Is larger than the radius Ri from the center of the cage (Rp> Ri). In this embodiment, the inner peripheral surface 4Bb has a curved surface shape that is a concave curve when viewed from the axial direction, specifically, an arcuate surface.

  The cage 4B is composed of, for example, two annular members 64 manufactured by punching and forming an iron plate by pressing. Each annular member 64 is arranged in the circumferential direction at equal intervals, and a plurality of hemispherical pocket wall portions 64a each constituting the inner wall surface of the pocket 4Ba and a flat plate-like coupling plate that connects adjacent pocket wall portions 64a to each other. The portions 64b are alternately formed. A rivet hole 64c is formed in the coupling plate portion 64b of the annular member 64 made of iron plate. The two annular members 64 are joined by overlapping the respective coupling plate portions 64b with each other, inserting a rivet 65 into the rivet hole 64c, and crimping both ends of the rivet 65. In this way, if the two annular members 64 are coupled to each other to form one cage 4B, the radius from the cage center having the inner diameter as described above is different in each part, but is retained. The processing of the vessel 4B is easy.

  The cage 4B of this embodiment has a shape in which the inner peripheral surface 4Bb of the circumferential direction portion with the pocket 4Ba is recessed toward the outer diameter side, so there is a concern that the overall strength may be lowered. However, most of the damage of the conventional standard shape cage Hr (Rp = Ri) as shown in FIG. 31 is the R portion from the circumferential portion between the pockets Hra to the circumferential portion with the pockets Hra. It is empirically known to occur with Hr7. Since the cage 4B of this embodiment does not change the shape of this portion, it can be said that the overall strength does not decrease.

  In order to investigate the state of grease during operation of this rolling bearing, a test was conducted under the conditions shown in Table 2. FIG. 27 shows the state of adhesion of grease to each part of the bearing after the operation was stopped. For comparison, a test was conducted under the same conditions for a bearing incorporating the conventional cage Hr shown in FIG. The state of adhesion of grease to each part of the bearing after the operation was stopped was as shown in FIG.

  According to this test, the grease G adheres to the inner ring seal groove Hr1a in the case of the bearing incorporating the conventional cage Hr. However, in the rolling bearing incorporating the cage 4 of the present invention, the grease does not adhere to the inner ring seal groove. I understood. For this reason, in a rolling bearing provided with a seal, it is inferred that leakage of the grease G from the portion of the inner ring seal groove due to breathing can be prevented.

  Next, a grease leakage frequency confirmation test was performed using a bearing assembled with a contact-type seal (LU seal manufactured by NTN Corporation). The test conditions were changed from the conditions shown in Table 2 to 15 minutes. When it was confirmed by visual inspection that grease of an amount of about 30 to 100 mg had jumped out of the bearing, grease leakage was assumed. The test results are shown in Table 3.

  Nine out of 10 grease leaks were found in the bearings incorporating the conventional cage Hr, but none of the bearings incorporating the cage 4 of the present invention produced any grease leaks. This proved that the reasoning was correct.

In the above embodiment, the two annular members 64 constituting the cage 4B are made of iron plate, but the annular member 64 may be made of resin. In that case, like the retainer 4C shown in FIGS. 28 and 29, the coupling plate portion 64b is provided with an engaging claw 66 and an engaging hole 67, and the two 66 and 67 are fitted to each other, so that It can be set as the structure which couple | bonds the annular member 64. FIG. Also in this case, the radius Rp from the cage center at the inner diameter of the circumferential portion with the pocket 4Ca is made larger than the radius Ri from the cage center at the inner diameter of the circumferential portion between the pockets 4Ca (Rp> Ri). . Further, two annular members 64 made of resin may be joined with an adhesive or the like.
As the synthetic resin material used for the cage, for example, polyamide resins such as PA66 and PA46 and polyphenyl sulfide resins are suitable, and a reinforcing fiber material such as glass fiber may be mixed as necessary.
Further, the structure is not limited to a structure in which the two annular members 64 are joined to form a single retainer, but may be a machined retainer that cuts out a steel material into a predetermined shape, or a molded retainer that is integrally molded with a resin material. It is good also as a vessel.

  FIG. 30 shows a different embodiment. In the retainer 4D, the shape of the inner peripheral surface 4Db in the circumferential portion with the pocket 4Da is a polygonal shape when viewed from the axial direction. Specifically, the inner peripheral surface 4Db includes a pair of inclined surface portions 4Dba that are inclined toward the outer diameter side with respect to the inner peripheral surface 4Dc in the circumferential portion between the pockets 4Da, and both ends of the outer peripheral surfaces 4Dba are outside the pair of inclined surface portions 4Dba. It has a trapezoidal shape composed of a constant-diameter surface portion 4Dbb that is connected to the radial end and has a constant inner diameter. Similarly to the cages 4B and 4C of the above-described embodiment, the cage 4D is inclined so that the inner circumferential surface 4Db of the circumferential portion with the pocket 4Da is recessed in the outer diameter side, and the pocket 4Da The radius Rp from the cage center of the inner diameter of a certain circumferential portion is larger than the radius Ri from the cage center of the inner diameter of the circumferential portion between the pockets 4Da (Rp> Ri).

  In this way, the cage 4D having a polygonal shape when viewed from the axial direction in the inner circumferential surface 4Db of the circumferential portion having the pocket 4Da is also reduced in overall strength, like the cages 4B and 4C of the above embodiment. When it is incorporated in a rolling bearing as shown in FIG. 1, leakage of grease from the inner ring seal groove portion of the bearing can be prevented.

  In addition, when making inner peripheral surface 4Db of the circumferential direction part with pocket 4Da into the polygonal shape which has a some corner | angular part, the number of the corner | angular part is not specifically limited. Further, the shape may be asymmetric with respect to a straight line in the radial direction. Furthermore, the inner peripheral surface 4Db of the circumferential direction portion with the pocket 4Da may be a combination of a flat surface and a curved surface.

In short, regardless of the material and processing method of the present invention, the radius from the cage center of the inner diameter of the circumferential portion with the pocket is larger than the radius from the cage center of the inner diameter of the circumferential portion between the pockets. It can be applied to a cage having a shape that satisfies the condition of large.
As described above, in the rolling bearing, the cage incorporated in the bearing has a radius from the center of the inner diameter of the circumferential portion having the pocket, and the inner diameter of the circumferential portion between the pockets. By making it larger than the radius from the center, it becomes difficult for grease to adhere to the inner ring shoulder and the inner ring seal groove. This appears particularly when the outer ring rotates. Thereby, leakage of grease can be prevented regardless of whether the seal is a contact type or a non-contact type. Further, since it is not necessary to increase the tightening force of the seal lip 12 (FIG. 1), the torque does not increase. Each of the above-described actions can be obtained in any case where the inner diameter surface of the circumferential portion having the pocket is a curved surface having a concave curve when viewed from the axial direction, or a polygonal shape having a plurality of corners.

  Next, another embodiment of the present invention will be described with reference to FIGS. In the following description, portions corresponding to the matters described in the above-described embodiment shown in FIGS. 1 to 5 are denoted by the same reference numerals, and overlapping description may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

  In the embodiment in this case, as shown in FIG. 33 (a), a ridge 20 projecting over the entire circumference along the tip sliding contact portion is formed on the inner surface of the main lip 15, and the ridge 20 is crossed. This is different from the above-described embodiment in that a notch groove 21 is provided in the direction to be cut. Other configurations are the same as those in the above-described embodiment. As shown in FIG. 33 (b), the protrusion 20 does not contact the inner surface 16 of the seal groove 9 in a state where there is no pressure difference between the inside and outside of the bearing, so that the sealing performance is not impaired. The notch grooves 21 are not limited to those formed by cutting out a part of the ridges 20 but also include those formed by reaching the inner surface of the main lip 15 and dividing the ridges 20.

  A pressure difference between the inside and outside of the bearing occurs, for example, when the bearing is cooled after the temperature change during the transportation of the rolling bearing or the generation of frictional heat accompanying the rotation of the rolling bearing, and the seal lip 12 is placed inside. When pushed in, as shown in FIG. 33 (c), the protrusion 20 provided on the main lip 15 contacts the inner surface 16 of the seal groove 9. As a result, the tip of the main lip 15 in the vicinity of the ridge 20 is elastically deformed outward and is separated from the inner surface 16 of the seal groove 9.

  In this state, an air passage 22 that communicates the inside and outside of the bearing is formed by the notch groove 21 of the protrusion 20, and the pressure difference between the inside and outside of the bearing is eliminated, thereby preventing the bearing adsorption phenomenon. At the same time, since the protrusions 20 projecting all around the tip of the main lip 15 are in contact with the inner surface 16 of the seal groove 9, sealing performance can be ensured. If the pressure difference between the inside and outside of the bearing is large and the ridge 20 is crushed by contact with the inner surface 16 of the seal groove 9 or the pressure difference inside and outside the bearing is very small, as shown in FIG. Both the protrusion 20 and the tip of the main lip 15 are in an adsorbed state in contact with the inner surface 16 of the seal groove 9. In the suction state in this case, the contact pressure of the tip of the ridge 20 that contacts the inner surface 16 of the seal groove 9 is larger than the tip of the main lip 15 that contacts the inner surface 16 of the seal groove 9.

  Due to this difference in contact pressure, the sliding resistance of the tip of the ridge 20 becomes larger than the sliding resistance of the tip of the main lip 15, and when the bearing is rotated in this attracted state, FIG. As shown in FIG. 5, the protrusion 20 maintains a state in contact with the inner surface 16 of the seal groove 9 and tries to rotate together with the inner surface 16. At this time, since the front end portion of the main lip 15 slides, as shown in FIG. 34 (c), the front end portion of the main lip 15 is elastically deformed so that the inner peripheral edge of the seal member SL is undulated. It is done. The air passage 23 is formed at the time of elastic deformation of the front end portion of the main lip 15, and the suction is released. Furthermore, in the rolling bearing according to this embodiment, by applying the retainers 4 and 59, it is difficult for grease to adhere to the seal groove of the inner ring, and grease leakage can be prevented. Therefore, it is not necessary to change the design of the shape of the seal groove, and it is not necessary to secure a space for providing a slinger or the like in the axial direction of the bearing. Therefore, the number of parts can be made smaller than that described in the aforementioned patent document, and the manufacturing cost can be reduced.

FIG. 35 is a cross-sectional view schematically illustrating a state in which the rolling bearing according to the present embodiment is used in the vapor pressure feeding device in the fuel cell system.
By the way, it is necessary to feed water vapor around the fuel cell. In order to increase the efficiency of feeding this water vapor, a compressor is used. The lubrication of the impeller support bearing used in this compressor is often grease lubrication. This is because in the case of oil lubrication, there is a problem that the lubricating oil tends to be mixed into water vapor through the seal portion. When the mixed lubricating oil enters the fuel cell, the electrolyte and electrodes are contaminated, leading to a reduction in battery life. Even with grease lubrication, if the sealing performance is low, the grease itself leaks. Further, if the sealing performance is lowered, when water vapor is mixed into the grease, the grease undergoes alteration such as emulsification, leading to a reduction in bearing life.

  Furthermore, oil separation (separation of grease base oil and thickener) occurs due to an alteration phenomenon, and the same thing occurs when oil lubrication is performed. In order to improve the sealing performance of the seal, a method of increasing the pressing pressure of the contact seal can be considered. However, when the compressor shaft rotates at a high speed, heat generated by sliding of the seal lip becomes a problem. Naturally, the non-contact seal cannot prevent leakage of the lubricating oil.

  Therefore, the present applicant applied seal members SL and SLa that can alleviate the above-described adsorption phenomenon, and cages 4 and 59 in the bearing NB for the fuel cell vapor pressure feeder. In the compressor CPR of the steam pressure feeding device, the pressure of water vapor is applied to the outside of the bearing during operation, so that the pressure is higher outside the bearing than inside the bearing. Therefore, by applying the seal members SL and SLa to the fuel cell vapor pressure feeder bearing NB and the cages 4 and 59, grease leakage resistance, adsorption resistance and space saving can be simultaneously achieved. And it can be achieved at low cost. In this embodiment, the rolling bearing of the present invention is applied to the fuel cell vapor pumping device, but the rolling bearing of the present invention can also be applied to devices other than the fuel cell vapor pumping device.

It is sectional drawing of the rolling bearing which concerns on one Embodiment of this invention. It is a perspective view showing the principal part of the seal lip of the rolling bearing. FIG. 3A is a cross-sectional view of the seal lip in a normal state, and FIG. 3B is a cross-sectional view of the seal lip in an adsorption state. It is sectional drawing showing the state which the main lip and protrusion in the seal lip contacted the seal groove. FIG. 5A is a cross-sectional view taken along the line AA in FIG. 4, and FIG. 5B is a state of the lip tip when the inner ring is rotated. FIG. It is a perspective view of the holder | retainer of this embodiment. It is a perspective view of the retainer half which is a structural member of the retainer. It is a partial expansion perspective view which simplifies and shows a pocket shape about a part of the cage half. (A) is a partial enlarged perspective view highlighting an example of the inner surface of the spherical shell plate portion in the cage half, and (B) is a perspective view showing a state in which a virtual cylinder is added to the perspective view. (A) is a partial enlarged perspective view highlighting another example of the inner surface of the spherical shell plate in the cage half, (B) is a perspective view showing a state in which a virtual cylinder is added to the perspective view. is there. (A) is a partial enlarged perspective view highlighting still another example of the inner surface of the spherical shell plate portion in the cage half, and (B) is a perspective view showing a state in which a virtual polygonal column is added to the perspective view. FIG. (A) is a partial enlarged perspective view highlighting still another example of the inner surface of the spherical shell plate portion in the cage half, (B) is a perspective view showing a state in which a virtual cylinder is added to the perspective view It is. It is explanatory drawing which shows the relationship between the spherical shell-shaped board part and a virtual ring in a cross section. It is explanatory drawing which shows the manufacturing process of the holder | retainer of this embodiment. It is a perspective view of the press die set used for the manufacturing process. It is explanatory drawing of the result of the grease leak test of the rolling bearing incorporating the cage | basket of the structure shown in FIG. It is explanatory drawing of the result of the grease leak test of the rolling bearing incorporating the cage | basket of the structure shown in FIG. It is explanatory drawing of the result of the grease leak test of the ball bearing incorporating the general iron plate punching cage. It is a disassembled perspective view of the resin-made cage to which the cage of this embodiment is applicable. It is sectional drawing of the resin cage. It is a partially broken perspective view of the rolling bearing incorporating the retainer concerning other embodiments of this invention. It is a partial expansion perspective view which shows the spherical shell-shaped board part in the cage half body of the same cage. It is a top view which shows the assembly which integrated the holder | retainer of the same embodiment in the inner ring | wheel. It is a partial expansion perspective view which shows the modification of the spherical shell-shaped board part in the cage half body of the same cage. It is a front view of the holder | retainer integrated in the rolling bearing concerning one Embodiment of this invention. It is AA sectional drawing of FIG. It is a figure which shows the test result performed with respect to the ball bearing incorporating the said holder | retainer. It is a front view of a different holder. It is a disassembled perspective view which shows the principal part of the annular member of the holder. It is a front view of the holder | retainer concerning different embodiment of this invention. It is a front view of the conventional cage | basket. It is a figure which shows the test result performed with respect to the ball bearing incorporating the said holder | retainer. It is a figure showing other embodiment etc. of this invention, and Fig.33 (a) is a perspective view showing the principal part of the seal lip of the rolling bearing which concerns on this embodiment, FIG.33 (b) is a seal | sticker of a normal state FIG. 33C is a cross-sectional view of the seal lip in the suction state. It is sectional drawing of the principal part of the seal lip, FIG.34 (a) is sectional drawing showing the state which the main lip and protrusion contacted the seal groove, FIG.34 (b) is B- of FIG.34 (a). FIG. 34C is a cross-sectional view showing the state of the lip tip when the inner ring is rotated. It is sectional drawing which represents roughly the state which used the rolling bearing concerning this embodiment for the vapor pressure feeder in a fuel cell system.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Inner ring 2 ... Outer ring 3 ... Ball 4 ... Cage 5 ... Inner ring raceway 6 ... Outer ring raceway 9 ... Seal groove 12 ... Seal lip 15 ... Main lip 16 ... Inner side surface 17 ... Projection 18, 19 ... Air passage 50 ... Pocket 54 ... Recesses Rp, Ri ... Radius SL ... Seal member NB ... Fuel cell vapor pressure bearing

Claims (9)

A plurality of balls intervening between the inner and outer rings are held by the cage, and both end surfaces of both raceways of these inner and outer races are closed with seal members, and one peripheral edge portion of the seal members is formed at the end of one raceway. In the rolling bearing in sliding contact with the seal groove and the other peripheral edge fixed to the end of the other raceway,
The periphery of the seal member that is in sliding contact with the seal groove is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside of the bearing partitioned by the seal member and the outside of the bearing. When the seal lip is pushed inward, the projection comes into contact with the inner surface of the seal groove, and the contact of the projection causes the seal lip in the vicinity of the contact to be partially elastically deformed, so that the inside of the bearing and the outside of the bearing And is configured to be displaceable over a state in which an air passage communicating therewith is formed and a state in which the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur,
The cage has pockets for holding a plurality of balls at a plurality of locations in the circumferential direction, and the inner surface of each pocket is closer to the inner diameter side opening edge of the cage than the ball arrangement pitch circle. a ring-shaped retainer having a concave curved surface whose diameter according to the of each pocket, the cage inner surface of the portion along the sealing member, the cage outer diametric side from an opening edge of the cage inner diameter side rolling bearing wherein the recess that set digit and extending. The rolling bearing according to claim 1, wherein a width of the concave portion in the circumferential direction of the cage is larger than half of a width of the pocket in the circumferential direction of the cage. The rolling bearing according to claim 1, wherein the recessed portion has two locations . 4. The rolling bearing according to claim 3 , wherein the position of each of the recesses is a location where the circumferential orientation angle with respect to the center in the circumferential direction of the cage at the opening edge of the pocket is 40 ° ± 15 °. A plurality of balls intervening between the inner and outer rings are held by the cage, and both end surfaces of both raceways of these inner and outer races are closed with seal members, and one peripheral edge portion of the seal members is formed at the end of one raceway. In the rolling bearing in sliding contact with the seal groove and the other peripheral edge fixed to the end of the other raceway,
The periphery of the seal member that is in sliding contact with the seal groove is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside of the bearing partitioned by the seal member and the outside of the bearing. When the seal lip is pushed inward, the projection comes into contact with the inner surface of the seal groove, and the contact of the projection causes the seal lip in the vicinity of the contact to be partially elastically deformed, so that the inside of the bearing and the outside of the bearing And is configured to be displaceable over a state in which an air passage communicating therewith is formed and a state in which the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur
The cage has a shape in which a plurality of spherical shell portions that are formed only in the radial direction of the cage by forming pockets that respectively hold a plurality of balls, and flat plate portions that are portions between adjacent pockets are alternately arranged. The plate thickness of the portion located at the outer diameter surface portion of at least the shoulder height on both sides of the raceway surface of the bearing inner ring in the inner diameter side portion from the ball arrangement pitch circle in the spherical shell-shaped portion, A rolling bearing characterized by being made thinner than the plate thickness. A plurality of balls intervening between the inner and outer rings are held by the cage, and both end surfaces of both raceways of these inner and outer races are closed with seal members, and one peripheral edge portion of the seal members is formed at the end of one raceway. In the rolling bearing in sliding contact with the seal groove and the other peripheral edge fixed to the end of the other raceway,
The periphery of the seal member that is in sliding contact with the seal groove is used as a seal lip, and a protrusion is provided on the inner surface of the seal lip. The protrusion has a pressure difference between the inside of the bearing partitioned by the seal member and the outside of the bearing. When the seal lip is pushed inward, the projection comes into contact with the inner surface of the seal groove, and the contact of the projection causes the seal lip in the vicinity of the contact to be partially elastically deformed, so that the inside of the bearing and the outside of the bearing And is configured to be displaceable over a state in which an air passage communicating therewith is formed and a state in which the protrusion is not in contact with the inner surface of the seal groove when the pressure difference does not occur,
The cage has a shape in which a plurality of spherical shell portions that are formed only in the radial direction of the cage by forming pockets that respectively hold a plurality of balls, and flat plate portions that are portions between adjacent pockets are alternately arranged. a is, the inner peripheral surface of said spherical shell-like portion is a circumferential portion of the pocket, is a shape in which an intermediate portion of the cage circumferential width as viewed in the axial direction is recessed radially outward , the rolling bearing, wherein a radius from the cage center as the inner diameter of the portion becomes the recessed shape, is larger than the radius of the circumferential portions cage center of the inner diameter of between pocket.   The rolling bearing according to claim 6, wherein the position of the portion where the inner diameter of the circumferential portion with the pocket is increased includes a range overlapping in the axial direction with the inner ring outer diameter surface which is the shoulder height of the inner ring.   The rolling bearing according to any one of claims 1 to 7, wherein the protrusions are formed on the inner surface of the seal lip at predetermined intervals along a sliding contact portion thereof.   8. The protrusion according to claim 1, wherein the protrusion is formed on the inner surface of the seal lip by a protrusion that protrudes along the tip sliding contact portion over the entire circumference, and in a direction crossing the protrusion. Rolling bearing with notched grooves.

Images