JP2010091038A - Radial-thrust combination bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a radial-thrust combination bearing continuously rotating with high accuracy over a long period of time. <P>SOLUTION: The radial-thrust combination bearing includes a radial bearing part 2 including a radial inner race 22, a radial outer race 24, a plurality of radial rolling elements 26 and a radial retainer 28, and a thrust bearing part 4 including a thrust first race 42, a thrust second race 44, a plurality of thrust rolling elements 46 and a thrust retainer 48 in an integral combination. An inner circumferential end surface (radial race guide surface 42s) of the thrust first race is brought into contact with an outer circumferential surface (thrust race contact surface 22s) of the radial inner race, whereby each of the radial inner race and the thrust first race is relatively positioned while guiding the position of the other. The radial race guide surface is chamfered to form a chamfered part 42r, whereby the radial race guide surface and the thrust race contact surface are regularly in face contact with each other. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a type of bearing (radial / thrust combination bearing) in which a radial bearing and a thrust bearing are combined integrally, for example, in a transmission part of an automobile, a sliding hinge part for opening and closing a door, or an industrial machine.

  2. Description of the Related Art Conventionally, various rolling bearings that rotatably support a predetermined rotating shaft are known, and the bearing type of the rolling bearing can be roughly classified into a radial bearing and a thrust bearing depending on the direction of a load to be applied. In general, thrust bearings can carry loads in the axial direction (axial loads), whereas radial bearings can carry not only axial loads but also loads in the radial direction (radial loads). However, since a radial load and an axial load are simultaneously applied, a radial bearing and a thrust bearing may be used together in some places. In this case, it is possible to use a radial bearing and a thrust bearing separately, but in order to apply a radial load and an axial load simultaneously and more efficiently, a type in which the radial bearing portion and the thrust bearing portion are combined together. Bearings (radial / thrust combined bearings) are also used depending on the application of the bearing mounting device (see Patent Document 1).

  FIG. 7A shows an example of the configuration of such a radial / thrust combination bearing (hereinafter also simply referred to as a bearing). In this case, the bearing has a configuration in which the radial bearing portion 6 and the thrust bearing portion 8 are integrally combined, and the radial bearing portion 6 is a pair of races 62 and 64 disposed so as to be relatively rotatable. (Radial inner race 62 and radial outer race 64), a plurality of rolling elements (radial rollers) 66 incorporated so as to be able to roll between the races 62, 64, and the rolling elements 66 are rotatably held, A retainer (radial retainer) 68 for disposing at regular intervals along the circumferential direction is provided. On the other hand, the thrust bearing portion 8 is capable of rolling between a pair of races 82 and 84 (a thrust first race 82 and a thrust second race 84) arranged to face each other so as to be relatively rotatable, and the races 82 and 84. A plurality of incorporated rolling elements (thrust rollers) 86 and a retainer (thrust retainer) 88 for rotatably holding the rolling elements 86 and arranging them at regular intervals along the circumferential direction are provided. .

In FIG. 7A, the radial outer race 64 and the thrust second race 84 are integrated to form one member (radial thrust race 30). The radial thrust trace 30 is an annular member in which a disk portion is continuous on one end side of a cylindrical portion. By forming a raceway surface for rolling the radial roller 66 on the cylindrical portion, the cylindrical portion is formed. Is configured as a radial outer race 64. On the other hand, by forming a raceway surface for rolling the thrust roller 86 on the disc portion of the radial thrust trace 30, the disc portion is configured as a thrust second race 64.
The radial inner race 62 has a radial small-diameter cylindrical portion 62a having a raceway surface for rolling the radial rollers 66, and a radial large portion continuously extending in the diameter-enlarging direction at one end of the radial small-diameter cylindrical portion 62a. The radial cylindrical part 62b and the radial protrusion part 62c which made the front-end | tip periphery of the said radial large diameter cylindrical part 62b protrude in the diameter expansion direction over the perimeter are provided. On the other hand, the thrust first race 82 has a thrust outer disk portion 82a having a raceway surface for rolling the thrust roller 86, and extends in the diameter reducing direction continuously to the inner peripheral end of the thrust outer disk portion 82a. A provided thrust inner disc portion 82b is provided.

  As shown in FIG. 7 (b), the radial inner race 62 and the thrust first race 82 have an inner peripheral end surface (radial race guide surface) 82s of the thrust inner disk portion 82b as an outer peripheral surface (the radial large diameter cylindrical portion 62b). By making the contact state (surface contact state) with the thrust trace contact surface (62s), the positions are guided to each other and relatively positioned. Thus, the radial inner race 62 and the first thrust race 82 can be positioned with respect to the radial thrust race 30 (the radial outer race 64 and the second thrust race 84). In this state, the radial bearing portion 6 and the thrust bearing portion 8 are integrally combined to form a radial / thrust combination bearing.

  In the radial bearing portion 6 and the thrust bearing portion 8 that are integrally combined in this way, the radial inner race 62 and the radial outer race 64 (the cylindrical portion of the radial / thrust trace 30) are rotated relative to each other via the radial roller 66. The thrust first race 82 and the thrust second race 84 (the disk portion of the radial thrust race 30) can be relatively rotated via the thrust roller 86. .

By the way, when the radial / thrust combination bearing (the radial bearing portion 6 and the thrust bearing portion 8) rotates, specifically, the radial inner race 62 and the first thrust race 82 have the radial thrust race 30 (the radial outer race 64 and the radial outer race 64 and the thrust outer race 64). When rotating with respect to the second thrust race 84), the radial bearing portion 6 and the thrust bearing portion 8 may be relatively inclined due to variations in the direction and magnitude of the load applied to the bearing.
For example, when the thrust bearing portion 8 is inclined with respect to the radial bearing portion 6, the thrust race contact surface 62s of the radial inner race 62 (radial large-diameter cylindrical portion 62b) and the first thrust race 82 (thrust inner disc portion 82b). ) Changes in the contact state with the radial race guide surface 82s. That is, the contact state between the thrust trace contact surface 62s and the radial race guide surface 82s changes from the surface contact state shown in FIG. 7 (b) to the line contact state as shown in FIG. 7 (c) and (d). The radial bearing portion 6 and the thrust bearing portion 8 are rotated while the thrust trace contact surface 62s and the radial race guide surface 82s are in line contact with each other.

  If the radial bearing portion 6 and the thrust bearing portion 8 continue to rotate while the thrust trace contact surface 62s and the radial race guide surface 82s remain in a line contact state, the line contact portion of the thrust trace contact surface 62s and the radial race guide surface 62s. Internal stress concentrates on the surface, and damage such as breakage or wear may occur from the line contact portion. If damage is caused to the thrust trace contact surface 62s or the radial race guide surface 82s, the combined radial and thrust bearings (the radial bearing portion 6 and the thrust bearing portion 8) do not rotate smoothly, and such a bearing is kept high for a long time. It may become impossible to continue rotating with high accuracy.

Further, as shown in FIG. 7A, when the radial bearing portion 6 of the combined radial and thrust bearing has a configuration including a radial inner race 62 (so-called inner ring), the flange diameter (radial) of the radial inner race 62 is increased. The outer diameter dimension of the protrusion 62c (distance d shown in FIG. 8A) is such that the radial inner race 62 and the thrust bearing portion 8 (specifically, the first thrust race 82) are engaged with each other. Generally, it is set larger than the circumscribed circle diameter (contact diameter between the radial roller 66 and the radial outer race 64 (distance Dw shown in the figure)).
The dimension management of the circumscribed circle diameter Dw is very important for smoothly rotating the radial / thrust combined bearing. As a pre-operation for combining the radial bearing portion 6 with the thrust bearing portion 8, a predetermined measuring instrument is used. It must be done strictly. In that case, various measuring instruments are arbitrarily selected and used. Among them, a ring gauge is used as an instrument that can measure most stably and does not require measuring time. Not a few.

  However, when the flange diameter d is set to be larger than the circumscribed circle diameter Dw, if the dimension management of the circumscribed circle diameter Dw is performed using the ring gauge 12, the ring gauge 12 is radial as shown in FIG. The ring gauge 12 interferes with the radial protrusion 62c of the inner race 62 (see the dotted circle in the figure) and cannot pass the ring gauge 12. For this reason, when the flange diameter d is set larger than the circumscribed circle diameter Dw, it is difficult to use the ring gauge 12 as a dimension measuring instrument for the circumscribed circle diameter Dw. Therefore, the measurement work such as measuring the circumscribed circle diameter Dw using a measuring instrument other than the ring gauge 12 becomes complicated, and the dimension of the circumscribed circle diameter Dw such as extension of the measurement time and inspection time, reduction of reliability, etc. This is one of the factors that cause deterioration of management accuracy.

Further, in the radial / thrust combination bearing, as shown in FIG. 9A, the radial cage 68 of the radial bearing portion 6 has a so-called roller in order to prevent the radial roller 66 inserted into the pocket 68p from falling off. It is common to provide protrusions 68a and 68b for preventing looseness on both the inner diameter side peripheral portion and the outer diameter side peripheral portion of the pocket 68p.
On the other hand, in order to provide the protrusion 68a on the inner peripheral edge of the radial retainer 68 (pocket 68p), the radial retainer 68 is avoided in order to avoid excessive restraint of the radial roller 66 inserted into the pocket 68p. In other words, the sectional height of the radial cage 68 (the half value of the difference in the outside diameter of the radial cage 68 (distance T shown in FIG. 9A)) is reduced. It is necessary to enlarge it.

However, when the inner diameter dimension of the radial cage 68 is reduced (the sectional height T is increased), as shown in FIG. 9B, the distance between the radial cage 68 and the radial inner race 62 (see FIG. 9B). The gap L) shown in FIG. 5 is narrowed, and the flow path of a lubricant (for example, grease or lubricating oil) enclosed in the bearing for lubrication is also narrowed. Therefore, reducing the inner diameter dimension of the radial cage 68 (increasing its cross-sectional height T) causes a decrease in the fluidity of the lubricant and becomes one of the factors that deteriorate the lubrication performance of the bearing.
Further, for example, when the radial cage 68 is made of resin, the inner diameter of the radial cage 68 made of resin is reduced (the sectional height T is increased), and the inner diameter side of the radial cage 68 (pocket 68p) If the protrusion 68a is provided on the peripheral edge portion, the radial roller 66 is excessively restrained by the expansion and contraction of the resin accompanying the change in the bearing temperature, and there is a possibility that the radial roller 66 cannot be smoothly rotated (rolled). .
Japanese Utility Model Publication No. 4-48417

  The present invention has been made to solve such problems, and the object thereof is a radial / thrust combination bearing capable of continuing to rotate with high accuracy over a long period of time, and in particular, a radial bearing portion constituting the same. Is to provide a combined radial and thrust bearing having a so-called inner ring.

In order to achieve such an object, the radial / thrust combination bearing according to the first embodiment of the present invention is formed by integrally combining a radial bearing portion and a thrust bearing portion, and the radial bearing portion has a relative rotation. A radially inner race and a radially outer race that are arranged so as to face each other, a plurality of radial rolling elements that are rotatably integrated between the races, and the radial rolling elements that are rotatably held and circumferentially arranged. A radial retainer arranged at a predetermined interval along the thrust bearing portion, and the thrust bearing portion is capable of rolling between the first and second races, which are disposed to face each other so as to be relatively rotatable. A plurality of incorporated thrust rolling elements and the thrust rolling elements are rotatably held and arranged at predetermined intervals along the circumferential direction. And a thrust cage. The radial inner race and the thrust first race are both annular, and the inner peripheral end surface of the thrust first race is brought into contact with the outer peripheral surface of the radial inner race, so that one of them guides the position of the other. And the inner peripheral end surface of the first thrust race has a convex curved portion that is convex toward the contact side with the outer peripheral surface of the radial inner race. .
In this case, the first thrust race is formed by a process including at least a punching process.

  In order to achieve the above-described object, the radial / thrust combination bearing according to the second embodiment of the present invention is formed by integrally combining a radial bearing portion and a thrust bearing portion. A radially inner race and a radially outer race that are rotatably opposed to each other, a plurality of radial rolling elements that are rotatably incorporated between the races, and the radial rolling elements that are rotatably held and circumferentially The thrust bearing portion includes a first thrust thrust race and a second thrust race disposed opposite to each other so as to be relatively rotatable, and can roll between the races. A plurality of thrust rolling elements incorporated in the cylinder, and the thrust rolling elements are rotatably held and arranged at predetermined intervals along the circumferential direction. And a thrust retainer fit. The radial inner race, the radial outer race, and the thrust first race all have an annular shape, and the radial inner race has one peripheral edge of the outer peripheral end portion protruding in the diameter increasing direction over the entire circumference. A flange portion is provided, and by engaging the flange portion with an inner peripheral end portion of the thrust first race, the thrust first race and the radial inner race are relatively positioned, and the flange portion Where d is the outer diameter dimension and Dw is the contact diameter dimension between the radial rolling element of the radial bearing portion and the radial outer race, d <Dw.

In order to achieve the above-described object, the radial / thrust combination bearing according to the third embodiment of the present invention is formed by integrally combining a radial bearing portion and a thrust bearing portion, and the radial bearing portion is A radially inner race and a radially outer race that are rotatably opposed to each other, a plurality of radial rolling elements that are rotatably incorporated between the races, and the radial rolling elements that are rotatably held and circumferentially The thrust bearing portion includes a first thrust thrust race and a second thrust race disposed opposite to each other so as to be relatively rotatable, and can roll between the races. A plurality of thrust rolling elements incorporated in the cylinder, and the thrust rolling elements are rotatably held and arranged at predetermined intervals along the circumferential direction. And a thrust cage for. In the radial holder, in order to insert and hold the radial rolling elements one by one, a plurality of pockets having openings on both the outer diameter side and the inner diameter side of the radial holder are provided along the circumferential direction. Each pocket is formed with a predetermined interval, and each pocket is provided with a protruding portion at the periphery of the outer diameter side opening so as to narrow the outer diameter side opening in order to prevent the inserted radial roller from falling off. On the other hand, the peripheral edge of the inner diameter side opening is not provided with a protrusion that narrows the inner diameter side opening.
In such a radial-thrust combined bearing, the half value of the outer diameter difference of the radial cage is T, the diameter dimension of the radial rolling element is Dr, the inner diameter dimension of the radial outer race and the outer diameter dimension of the radial cage. When the half value of the difference dimension is H, the relationship Dr / 2 <T <Dr-H is set.
In addition, what is necessary is just to comprise the said radial holder | retainer with various synthetic resin materials.

  According to the present invention, the combined radial and thrust bearing can be rotated with high accuracy over a long period of time. In particular, even when the radial bearing portion has a so-called inner ring configuration, it is possible to continue rotating the radial / thrust combined bearing with high accuracy over a long period of time.

  Hereinafter, the radial / thrust combination bearing of the present invention will be described with reference to the accompanying drawings. The radial / thrust combined bearing of the present invention is a type of bearing in which a radial bearing portion and a thrust bearing portion are integrally combined. For example, a transmission portion of an automobile, a slide hinge portion for opening and closing a door, an industrial machine, etc. It can be assumed that the rotary shaft is incorporated and used to support the rotating shaft, but the application is not limited to this.

“First Embodiment”
FIG. 1 (a) shows a configuration example of a radial / thrust combination bearing (hereinafter also simply referred to as a bearing) according to the first embodiment of the present invention. A radial inner race 22 and a radial outer race 24 that are rotatably arranged in the radial direction (vertical direction in the figure), and a plurality of radial rolling elements that are rotatably incorporated between the races 22 and 24 ( As an example, a cylindrical roller 26 and a radial holder 28 for rotatably holding the radial rolling element 26 and for arranging the radial rolling element 26 at a predetermined interval (as an example, a constant interval) along the circumferential direction are provided.
In this case, the radial bearing portion 2 is configured as a stationary wheel in which the radial outer race 24 is always kept stationary, and the radial inner race 22 is configured as a rotating wheel that can rotate with respect to the radial outer race 24. The case is assumed as an example. However, the radial inner race 22 may be configured as a stationary wheel that is always kept stationary, and the radial outer race 24 may be configured as a rotating wheel that can rotate with respect to the radial inner race 22. It is also possible to configure both the 22 and the radial outer race 24 as rotating wheels.

On the other hand, the thrust bearing portion 4 includes a thrust first race 42 and a thrust second race 44 that are disposed to face each other in the thrust direction (the left-right direction in FIG. 1A) so as to be relatively rotatable, and between the races 42, 44. A plurality of thrust rolling elements (cylindrical rollers, for example) 46 incorporated so as to be able to roll, and the thrust rolling elements 46 are rotatably held, and at predetermined intervals along the circumferential direction (as an example, constant intervals) A thrust cage 48 is provided.
In this case, the thrust bearing portion 4 is configured as a stationary wheel in which the thrust second race 44 is always kept stationary, and the thrust first race 42 is configured as a rotating wheel that can rotate with respect to the thrust second race 44. The case where it is done is assumed as an example. However, it is also possible to configure the thrust first race 42 as a stationary wheel that is always kept stationary, and to configure the thrust second race 44 as a rotating wheel that can rotate with respect to the thrust first race 42. Both the first thrust race 42 and the second thrust race 44 can be configured as rotating wheels.

  FIG. 1 (a) shows a bearing structure in which cylindrical rollers 26 and 46 are incorporated as rolling elements in the radial bearing portion 2 and the thrust bearing portion 4, respectively. Depending on the above, it is possible to replace the rolling element with a cylindrical roller and use a tapered roller, a spherical roller, or a ball bearing configuration. In the following description, a rolling element (cylindrical roller) incorporated between the radial inner race 22 and the radial outer race 24 of the radial bearing portion 2 is referred to as a radial roller 26, and the thrust first race 42 and the thrust of the thrust bearing portion 4 are thrust. A rolling element (cylindrical roller) incorporated between the second races 44 is referred to as a thrust roller 46.

  Moreover, what is necessary is just to apply arbitrary types as a holder | retainer according to the kind of rolling element. For example, when rolling elements are various types of rollers, types such as machined, comb and basket types can be applied, and when rolling elements are balls, crown and corrugated matching types are applied. can do.

  In the present embodiment, as shown in FIG. 1A, the radial outer race 24 and the thrust second race 44 are integrated to form a single member (radial thrust race 10). The radial thrust trace 10 is an annular member in which a disc portion is continuous on one end side (the left end side in the figure) of a cylindrical portion, and the cylindrical portion is configured as a radial outer race 24, and a disc The portion is configured as a thrust second race 44. In this case, a raceway surface 24t for rolling the radial roller 26 is formed in the cylindrical portion (radial outer race 24) of the radial thrust race 10, and the circular plate portion (thrust second race 44) is formed on the disc portion. Is formed with a raceway surface 44t for rolling the thrust roller 46.

  The radial inner race 22 includes a radial small-diameter cylindrical portion 22a. In the radial small-diameter cylindrical portion 22a, a raceway surface 22t for rolling the radial roller 26 can face the raceway surface 24t of the radial outer race 24. Is formed. At one end of the radial small diameter cylindrical portion 22a (as an example, the left end of FIG. 1A), a radial connecting portion 22e extending in a disk shape from the end in the diameter increasing direction is continuous. Further, a radial large-diameter cylindrical portion 22b extending in a cylindrical shape (that is, concentric) in parallel with the radial small-diameter cylindrical portion 22a is continuous from the extending end of the radial coupling portion 22e. And the radial large diameter protrusion part (flange part) 22c extended in the disk shape from the extended end part of the said radial large diameter cylindrical part 22b to the diameter expansion direction is continuing. On the other hand, a radial small-diameter protruding portion extending in a disk shape from the end portion in the diameter increasing direction is provided at the other end portion (as an example, the right end portion in FIG. 1A) of the radial small-diameter cylindrical portion 22a. 22d is continuous.

  That is, the radial inner race 22 has a structure in which a radial large-diameter protruding portion 22c, a radial large-diameter cylindrical portion 22b, a radial connecting portion 22e, a radial small-diameter cylindrical portion 22a, and a radial small-diameter protruding portion 22d are extended in a series. Is made. In this case, the outer diameter dimension of the radial small diameter cylindrical portion 22a is set smaller than the outer diameter dimension of the radial large diameter cylindrical portion 22b, and the outer diameter dimension of the radial small diameter protruding portion 22d is the radial large diameter protruding portion. It is set to be smaller than 22c.

  On the other hand, the thrust first race 42 is provided with a thrust outer disc portion 42a, and a raceway surface 42t for rolling the thrust roller 46 is provided on the thrust outer disc portion 42a. It is formed to be able to face 44t. At one end portion of the thrust outer disk portion 42a (for example, the lower end portion in FIG. 1A), a cylindrical shape extends from the end portion in a direction (inward direction) close to the thrust second race 44. The thrust connecting portion 42c is continuous, and further, the thrust inner circle extends in a disk shape in the reduced diameter direction in parallel with the thrust outer disc portion 42a from the extending end portion of the thrust connecting portion 42c. The plate part 42b is continuous. On the other hand, at the other end portion of the thrust outer disk portion 42a (as an example, the upper end portion in FIG. 1A), there is a thrust protrusion portion 42d extending in a cylindrical shape inward from the end portion. It is continuous.

  That is, the first thrust race 42 has a structure in which a thrust inner disk portion 42b, a thrust coupling portion 42c, a thrust outer disk portion 42a, and a thrust protrusion 42d are extended in a series. In this case, the inner diameter dimension of the thrust outer disk part 42a is set larger than the inner diameter dimension of the thrust inner disk part 42b.

  As shown in FIG. 1 (b), the radial inner race 22 and the thrust first race 42 having such a structure have an inner diameter surface (radial surface) of a thrust inner disk portion 42b which is an inner peripheral end surface of the thrust first race 42. The race guide surface) 42s is brought into contact with the outer diameter surface (thrust trace contact surface) 22s of the radial large-diameter cylindrical portion 22b, which is the outer peripheral surface of the radial inner race 22, so that one of the two guides the position of the other. Is positioned. That is, the radial inner race 22 and the first thrust race 42 are set so that the inner diameter dimension of the thrust inner disk section 42b and the outer diameter dimension of the radial large-diameter cylindrical section 22b are set to substantially the same dimension. The radial race guide surface 42s of 42b and the thrust trace contact surface 22s of the radial large-diameter cylindrical portion 22b are brought into contact with each other, and are positioned relative to each other and relatively positioned.

  Thus, the radial inner race 22 and the first thrust race 42 can be positioned with respect to the radial thrust race 10 (the radial outer race 24 and the second thrust race 44). In this state, the radial bearing portion 2 and the thrust bearing are provided. The parts 4 are integrally combined to form a radial / thrust combination bearing.

  In this case, the outer diameter dimension of the radial large-diameter protruding portion 22c of the radial inner race 22 is set smaller than the inner diameter dimension of the thrust outer disk portion 42a (thrust connecting portion 42c) of the thrust first race 42. ing. As a result, the radial inner race 22 and the thrust first race 42 are in contact with the radial race guide surface 42s and the thrust trace contact surface 22s, and the radial large-diameter protruding portion 22c and the thrust outer disk portion 42a (thrust connecting portion). 42c) are opposed to each other with a predetermined interval, and are structured in a non-contact state.

  Further, the outer diameter dimension of the radial small-diameter protruding portion 22d of the radial inner race 22 is set smaller than the inner diameter dimension of the radial thrust race 10 (the radial outer race 24 and the thrust second race 44). Thus, in the state in which the radial race guide surface 42s and the thrust race contact surface 22s are in contact with each other, the radial inner race 22 has the radial small diameter protruding portion 22d with the radial thrust race 10 (specifically, the radial outer race 24). And facing each other with a predetermined interval, and a structure that is kept in a non-contact state is formed. Similarly, the thrust protrusion 42d of the first thrust race 42 has a structure that is maintained in a non-contact state with the radial thrust race 10 (specifically, the thrust second race 44).

  As a result, the radial inner race 22 can be rotated with respect to the radial outer race 24 (the cylindrical portion of the radial thrust race 10), and the thrust first race 42 can be the thrust second race 44 (radial thrust). The structure is rotatable with respect to the disk portion of the race 10.

  In the present embodiment, the radial race guide surface 42s of the thrust inner disc portion 42b has a convex curved portion that forms a convex shape toward the contact side with the thrust trace contact surface 22s (lower side in FIG. 1A). is doing. As an example, in the configuration shown in FIGS. 1A and 1B, chamfering is performed over the entire circumference of the outer peripheral edge and the inner peripheral edge (the left peripheral edge and the right peripheral edge in FIG. 1B) of the radial race guide surface 42s. The chamfered portion 42r is formed as a convex curved portion with respect to the outer peripheral edge and the inner peripheral edge. That is, the outer peripheral edge and the inner peripheral edge of the radial race guide surface 42s of the thrust inner disk part 42b are both so-called R-shaped.

  Thus, by forming the chamfered portion 42r with respect to the radial race guide surface 42s, when the bearings (the radial bearing portion 2 and the thrust bearing portion 4) rotate, specifically, the radial inner race 22 and the thrust first When one race 42 rotates with respect to the radial thrust trace 10 (the radial outer race 24 and the thrust second race 44), the radial bearing portion 2 and the thrust bearing are changed depending on variations in the direction and magnitude of the load applied to the bearing. When the portion 4 is relatively inclined, for example, as shown in FIGS. 1C and 1D, the thrust first race 42 (thrust inner disc portion 42b) is replaced with the radial inner race 22 (radial large diameter cylindrical portion 22b). ), The chamfered portion 42r of the radial race guide surface 42s can be brought into contact with the thrust trace contact surface 22s. That is, the radial race guide surface 42s and the thrust trace contact surface 22s can be brought into surface contact with each other, and the radial race guide surface 42s and the thrust trace contact surface 22s can be reliably prevented from making line contact. Therefore, during the rotation of the bearings (the radial bearing portion 2 and the thrust bearing portion 4), the radial race guide surface 42s and the thrust trace contact surface 22s are not in line contact with each other, and the bearing is always rotated in a state of surface contact. It becomes possible to make it.

As a result, the occurrence of damage (breakage, wear, etc.) to the radial race guide surface 42s and the thrust trace contact surface 22s is remarkably reduced, and the bearings (radial bearing portion 2 and thrust bearing portion 4) can always rotate smoothly. it can.
As a result, it is possible to continue rotating such bearings (radial bearing portion 2 and thrust bearing portion 4) with high accuracy over a long period of time. In particular, even in the case where the radial bearing portion 2 has a so-called inner ring (radial inner race 22) as in this embodiment (FIG. 1 (a)), the radial / thrust combination bearing is used for a long time. The effect of being able to continue rotating with high accuracy can be obtained.

  Note that the shape (size, curvature, etc.) of the chamfered portion 42r is such that the radial race guide surface 42s and the thrust trace contact surface 22s are always in surface contact during the rotation of the bearings (radial bearing portion 2 and thrust bearing portion 4). For example, it may be arbitrarily set according to the size of the first thrust race 42 (thrust inner disc portion 42b), and so on, and is not particularly limited here.

  Further, the method for forming the radial inner race 22, the first thrust race 42, and the radial thrust race 10 (the radial outer race 24 and the second thrust race 44) is not particularly limited, and any method can be applied. In this embodiment, the case where these members are formed by punching and surface pressing is assumed as an example. Therefore, as the material (material) of the radial inner race 22, the first thrust race 42 and the radial thrust race 10 (the radial outer race 24 and the second thrust race 44), various metal materials (bearing steel plates, etc.) can be used. Good.

  For example, when the thrust first race 42 is formed by such a forming method, the formed body after the punching process has a sag portion (one circumference) with respect to the radial race guide surface 42s as shown in FIG. A chamfered portion 42r) on the edge side and a shear surface are formed, and a fracture surface and a burr are formed. Then, as shown in FIG. 2 (b), the radial race guide surface 42s (molded body after punching) is subjected to a surface pressing process from the fractured surface side, so that the chamfered portion 42r is also formed on the fractured surface side. Can be formed. Accordingly, the thrust first race 42 can be formed in a short process, and the chamfered portion 42r can be easily formed on the radial race guide surface 42s. As a result, the radial / thrust combined bearing (radial bearing portion 2 and thrust bearing portion 4) can be manufactured at low cost and in a short time.

  Here, in the first embodiment described above, the chamfered portion 42r is formed on the radial race guide surface 42s of the first thrust race 42 so that the bearings (the radial bearing portion 2 and the thrust bearing portion 4) are rotating. The radial race guide surface 42s and the thrust trace contact surface 22s are always kept in a surface contact state. However, the radial race guide surface 42s and the thrust trace contact surface 22s are in a surface contact state during rotation of the bearing. The structure is not particularly limited as long as the structure is maintained (a structure in which the radial race guide surface 42s has a curved portion that is convex toward the contact side with the thrust trace contact surface 22s).

  For example, as in the modification of the present embodiment shown in FIG. 3A, a thrust return portion 42e formed by folding the extending end in the reverse direction with respect to the thrust inner disk portion 42b of the first thrust race 42. And the thrust return portion 42e can be protruded in a convex shape toward the thrust trace contact surface 22s of the radial inner race 2 with a predetermined curvature. Thereby, as shown in FIG. 3 (b), the inner diameter surface (radial race guide surface 42s) of the thrust inner disc portion 42b, which is the inner peripheral end surface of the thrust first race 42, can be formed into a so-called R shape. A configuration similar to that when the chamfered portion 42r is formed on the radial race guide surface 42s (the first embodiment shown in FIG. 1A) can be adopted.

  The thrust return portion 42e has a form (size, curvature, etc.) in which the radial race guide surface 42s and the thrust trace contact surface 22s are always in surface contact during rotation of the bearings (radial bearing portion 2 and thrust bearing portion 4). For example, it may be arbitrarily set according to the size of the first thrust race 42 (thrust inner disc portion 42b), and so on, and is not particularly limited here.

“Second Embodiment”
FIG. 4 shows a configuration example of a radial / thrust combination bearing according to the second embodiment of the present invention. In such a bearing, the basic configuration is assumed to be the same as that of the radial / thrust combination bearing (FIG. 1A) according to the first embodiment described above. Only the structure of the radial bearing part 2 provided with the structure peculiar to the bearing which concerns on embodiment is shown. The configuration of the radial / thrust combination bearing according to the second embodiment will be described below. At that time, the same or similar components as those in the radial / thrust combination bearing (FIG. 1A) according to the first embodiment described above are denoted by the same reference numerals in the drawing, and the description thereof is omitted. Only the configuration specific to the bearing according to the second embodiment will be described.

In the present embodiment, as shown in FIG. 4, the radial large-diameter protruding portion 22c, which is the flange portion of the radial inner race 22, is replaced with the thrust, which is the inner peripheral end portion of the first thrust race 42 (FIG. 1A). By engaging with the inner disc portion 42b (the same figure), the thrust first race 42 and the radial inner race 22 are relatively positioned.
In this case, when the outer diameter dimension of the radial large-diameter protrusion 22c is d and the contact diameter dimension between the radial roller 26 of the radial bearing portion 2 and the radial outer race 24 (the circumscribed circle diameter of the radial roller 26) is Dw, The relation d <Dw is set. That is, the radial large-diameter protruding portion 22c has an outer diameter dimension d set smaller than the contact diameter dimension (the circumscribed circle diameter of the radial roller 26) Dw between the radial roller 26 of the radial bearing portion 2 and the radial outer race 24. ing.

  As a result, even when the ring gage 12 is used to manage the dimension of the circumscribed circle diameter Dw of the radial roller 26, the ring gauge 12 is provided with the radial large-diameter protruding portion 22c of the radial inner race 22 as shown in FIG. The ring gauge 12 can be easily passed through without interfering with. Therefore, it is possible to measure the circumscribed circle diameter Dw by using the ring gauge 12 as a measuring instrument, and the measurement operation can be performed smoothly and stably, and it is possible to perform smoothly without unnecessary measurement time. Measurement can be performed, and it is possible to improve the dimension management accuracy of the circumscribed circle diameter Dw, such as shortening the measurement time and inspection time, and improving reliability.

  As a result, the bearing (particularly, the radial bearing portion 2) can always be smoothly rotated, and the bearing can be continuously rotated with high accuracy over a long period of time. In particular, even in the case where the radial bearing portion 2 has a so-called inner ring (radial inner race 22) as in the present embodiment (FIG. 4), the radial / thrust combination bearing can be highly accurate over a long period of time. The effect of being able to continue the rotation can be obtained.

“Third Embodiment”
FIGS. 5A and 5B show a configuration example of a radial / thrust combination bearing according to a third embodiment of the present invention. In such a bearing, the basic configuration is assumed to be the same as that of the radial / thrust combination bearing (FIG. 1A) according to the first embodiment described above. The configuration of the radial / thrust combination bearing according to the third embodiment will be described below. At that time, the same or similar components as those in the radial / thrust combined bearing according to the first embodiment described above (FIG. 1 (a)) are denoted by the same reference numerals in the drawing, and the description thereof is omitted. Only the configuration specific to the bearing according to the third embodiment will be described.

  In this embodiment, in order to insert and hold the radial rollers 26 one by one in the radial cage 28 as shown in FIG. 5B, both the outer diameter side and the inner diameter side of the radial cage 28 are provided. A plurality of pockets 28p having openings pb and pa are formed at a predetermined interval (as an example, a constant interval) along the circumferential direction. In such a radial cage 28, each pocket 28p has a protrusion protruding so as to narrow the outer diameter side opening pb with respect to the peripheral edge of the outer diameter side opening pb in order to prevent the inserted radial roller 26 from falling off. A portion 28b is provided. On the other hand, a protrusion that narrows the inner diameter side opening pa is not provided on the periphery of the inner diameter side opening pa of each pocket 28p.

  As described above, since the radial cage 28 has a structure in which the protrusion 28b is provided only at the periphery of the outer diameter side opening pb of each pocket 28p, the periphery of the inner diameter side opening pa of each pocket 28p. In addition, the inner diameter side of the radial cage 28 can be made thinner. That is, if the outer diameter dimension of the radial cage 28 is maintained and only the inner diameter dimension is increased, or another way of understanding, the cage cross-sectional height that is half the difference between the outer diameter dimensions of the radial cage 28 is obtained. Thus, the distance (distance T shown in FIG. 5B) can be reduced.

  Thereby, the opposing distance between the radial retainer 28 and the radial inner race 22, that is, the half value of the difference between the inner diameter dimension of the radial retainer 28 and the track diameter dimension of the radial inner race 22 (gap L shown in FIG. 6A). As a result, the flow path of the lubricant (for example, grease or lubricating oil) enclosed in the bearing for lubrication (for example, the passage volume of the lubricant) can be expanded. it can.

  Accordingly, the fluidity of the lubricant is activated (see the arrow in FIG. 6A), the bearings (radial bearing portion 2 and thrust bearing portion 4) can be kept in a good lubrication state, and the bearing is always smooth. And can continue to rotate with high accuracy over a long period of time. In particular, even in the case where the radial bearing portion 2 has a so-called inner ring (radial inner race 22) as in the present embodiment (FIG. 5A), the radial / thrust combined bearing is used for a long time. The effect of being able to continue rotating with high accuracy can be obtained.

As described above, even when the protrusion 28b is provided only at the periphery of the outer diameter side opening pb of each pocket 28p, the radial cage 28 can reliably serve as an outer ring guide, Since the inner diameter side is in a free state (see FIG. 5A), the radial roller 26 inserted into the pocket 28p is not excessively restrained.
The shape (size, shape, etc.) of the protrusion 28b is such that the radial roller 26 inserted into the pocket 28p does not fall off (separate) and is not excessively restrained. As long as it is set according to the above, it is not particularly limited, and any configuration can be adopted. For example, it is good also as a structure which provided the series of protrusion part 28p continuous over the perimeter to the periphery of the outer diameter side opening pb of each pocket 28p, and it is good also as a some protrusion part 28p so that it may interrupt in the circumferential direction. May be provided.

  Further, when the radial roller 26 is inserted into each pocket 28p of the radial cage 28, first, only the radial cage 28 is assembled into the radial inner race 22, and then the projection 28b of the radial cage 28 is placed on the outer diameter side. It is inserted into the pocket 28p by pushing the radial roller 26 from the outer diameter side of the radial retainer 28 while elastically deforming so that the opening pb expands. A radial inner race 22 is disposed on the inner diameter side of the pocket 28p, and a protrusion 28b is disposed on the outer diameter side of the pocket 28p. Therefore, the radial roller 26 inserted into each pocket 28p is attached to the pocket 28p. It can be rotated without falling (separating) from the pocket 28p.

  Here, when only the inner diameter dimension is increased (the sectional height T is decreased) while maintaining the outer diameter dimension of the radial cage 28, the flow path of the lubricant (for example, grease or lubricating oil) ( The gap L) can be sufficiently secured, the cage strength according to the material of the radial cage 28 is sufficiently secured, and the function of holding and guiding the radial roller 26 in the pocket 28p is impaired. What is necessary is just to set cross-sectional height T to an appropriate dimension in the range which does not exist.

  In this embodiment, as shown in FIG. 6B, the diameter dimension of the radial roller 26 is Dr, and the half value of the difference between the inner diameter dimension of the radial outer race 24 and the outer diameter dimension of the radial cage 28 (so-called guide). Assuming that the clearance is H, the cross-sectional height T is set so as to satisfy the relationship Dr / 2 <T <Dr-H. That is, in the radial cage 28, the sectional height T is set to be larger than the radial dimension (Dr / 2) of the radial roller 26 and smaller than the difference between the diameter dimension Dr of the radial roller 26 and the guide clearance H. It is configured.

  In the present embodiment, it is assumed as an example that the radial cage 28 is made of various synthetic resins. As described above, the radial cage 28 has a structure in which the protrusions 28b are provided only at the periphery of the outer diameter side opening pb of each pocket 28p, and the protrusions are not provided at the periphery of the inner diameter side opening pa. Since the inner diameter side opening pa of the roller has a free structure, the radial rollers 26 are not contained in the pockets 28p even when various synthetic resin radial cages 28 expand and contract with temperature changes of the bearings. Is not overly restrained.

  Therefore, even if the radial cage 28 expands and contracts as the bearing temperature changes, the radial roller 26 rotates smoothly in the pocket 28p, and the radial inner race 22 and the radial outer race 24 (track). Rolls smoothly between the surfaces 22t and 24t). That is, the bearings (radial bearing portion 2 and thrust bearing portion 4) can always be rotated smoothly, and such bearings can be continuously rotated with high accuracy over a long period of time.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the structure of the radial / thrust combination bearing which concerns on 1st Embodiment of this invention, Comprising: (a) is sectional drawing which shows the state which combined the radial bearing part and the thrust bearing part, (b) is the same. The figure which expands the inside of the dotted line circle of Drawing (a), and shows the contact state of a radial race guide surface and a thrust trace contact surface, (c) and (d) are a radial bearing part and a thrust bearing part inclined relatively The figure which shows the contact state of the radial race guide surface in this case, and a thrust trace contact surface. It is a figure for demonstrating the processing method of a thrust 1st race, Comprising: (a) is a figure which shows the state of the molded object after stamping, (b) is surface pressing with respect to the molded object after stamping The figure which shows the state which processes. It is a figure which shows the structure of the radial and thrust combination bearing which concerns on the modification of this invention (1st Embodiment), Comprising: (a) is sectional drawing which shows the state which combined the radial bearing part and the thrust bearing part, (b) FIG. 4B is an enlarged view of a dotted circle in FIG. 4A and shows a contact state between the radial race guide surface and the thrust trace contact surface. The figure for demonstrating the structure of the radial and thrust combination bearing which concerns on 2nd Embodiment of this invention. It is a figure for demonstrating the structure of the radial / thrust combination bearing which concerns on 3rd Embodiment of this invention, Comprising: (a) is sectional drawing which shows the state which combined the radial bearing part and the thrust bearing part, (b) These are principal part sectional drawings of the radial retainer for demonstrating the structure of a projection part. (a) is a diagram showing the spacing between the radial cage and the radial inner race and the state of the flow path of the lubricant. (b) is the sectional height of the radial cage, the radial dimension of the radial roller, and the guide clearance. The figure for demonstrating a relationship. It is a figure which shows the structural example of the conventional radial and thrust combined bearing, Comprising: (a) is sectional drawing which shows the state which combined the radial bearing part and the thrust bearing part, (b) is a radial race guide surface and a thrust trace. The figure which shows the contact state of a contact surface, (c), (d) is a figure which shows the contact state of a radial race guide surface and a thrust trace contact surface in case a radial bearing part and a thrust bearing part incline relatively. It is a figure for demonstrating the dimension management of a circumscribed circle diameter, Comprising: (a) is a figure for demonstrating the relationship between the flange diameter of a radial inner race, and the circumscribed circle diameter of a radial roller, (b) is a circumscribed circle. The figure which shows the state in the case of performing dimension management of a diameter using a ring gauge. (a) is principal part sectional drawing of the radial holder for demonstrating the structure of protrusion, (b) is a figure which shows the state of the opposing space | interval of a radial holder and a radial inner race, and the flow path of a lubricant.

Explanation of symbols

2 Radial bearing portion 4 Thrust bearing portion 22 Radial inner race 22s Thrust trace contact surface 24 Radial outer race 26 Radial rolling element 28 Radial cage 42 Thrust first race 42s Radial race guide surface 42r Chamfer 44 Thrust second race 46 Thrust roll Moving body 48 Thrust cage

Claims (6)

In radial / thrust combination bearings in which a radial bearing and a thrust bearing are combined together,
The radial bearing portion includes a radial inner race and a radial outer race that are arranged to face each other so as to be relatively rotatable, a plurality of radial rolling elements that are rotatably integrated between the races, and the radial rolling elements are rotatable. A radial holder for holding at a predetermined interval along the circumferential direction,
The thrust bearing portion includes a thrust first race and a thrust second race that are arranged to face each other so as to be relatively rotatable, a plurality of thrust rolling elements that are rotatably incorporated between the races, and the thrust rolling elements. A thrust retainer is provided for holding it rotatably and arranging it at predetermined intervals along the circumferential direction.
The radial inner race and the thrust first race are both annular, and the inner peripheral end surface of the thrust first race is brought into contact with the outer peripheral surface of the radial inner race, so that one of them guides the position of the other. And has a relatively positioned structure,
The radial / thrust combined bearing is characterized in that an inner peripheral end surface of the first thrust race has a convex curved portion that is convex toward the contact side with the outer peripheral surface of the radial inner race.   The radial thrust combined bearing according to claim 1, wherein the first thrust race is formed by a process including at least a punching process. In radial / thrust combination bearings in which a radial bearing and a thrust bearing are combined together,
The radial bearing portion includes a radial inner race and a radial outer race that are arranged to face each other so as to be relatively rotatable, a plurality of radial rolling elements that are rotatably integrated between the races, and the radial rolling elements are rotatable. A radial holder for holding at a predetermined interval along the circumferential direction,
The thrust bearing portion includes a thrust first race and a thrust second race that are arranged to face each other so as to be relatively rotatable, a plurality of thrust rolling elements that are rotatably incorporated between the races, and the thrust rolling elements. A thrust retainer is provided for holding it rotatably and arranging it at predetermined intervals along the circumferential direction.
The radial inner race, the radial outer race, and the thrust first race all have an annular shape, and the radial inner race has one peripheral edge of the outer peripheral end portion protruding in the diameter increasing direction over the entire circumference. The thrust first race and the radial inner race are relatively positioned by engaging the flange portion with the inner peripheral end of the thrust first race.
When the outer diameter dimension of the flange portion is d and the contact diameter dimension between the radial rolling element and the radial outer race of the radial bearing portion is Dw, a relationship of d <Dw is set. Thrust combination bearing. In radial / thrust combination bearings in which a radial bearing and a thrust bearing are combined together,
The radial bearing portion includes a radial inner race and a radial outer race that are arranged to face each other so as to be relatively rotatable, a plurality of radial rolling elements that are rotatably integrated between the races, and the radial rolling elements are rotatable. A radial holder for holding at a predetermined interval along the circumferential direction,
The thrust bearing portion includes a thrust first race and a thrust second race that are arranged to face each other so as to be relatively rotatable, a plurality of thrust rolling elements that are rotatably incorporated between the races, and the thrust rolling elements. A thrust retainer is provided for holding it rotatably and arranging it at predetermined intervals along the circumferential direction.
In the radial holder, in order to insert and hold the radial rolling elements one by one, a plurality of pockets having openings on both the outer diameter side and the inner diameter side of the radial holder are provided along the circumferential direction. Each pocket is formed with a predetermined interval, and each pocket is provided with a protruding portion at the periphery of the outer diameter side opening so as to narrow the outer diameter side opening in order to prevent the inserted radial roller from falling off. On the other hand, a radial / thrust combined bearing is characterized in that no protrusion is provided on the periphery of the inner diameter side opening to narrow the inner diameter side opening.   The half value of the outer diameter difference of the radial cage is T, the diameter size of the radial rolling element is Dr, and the half value of the difference between the inner diameter size of the radial outer race and the outer diameter size of the radial cage is H. The radial / thrust combined bearing according to claim 4, wherein a relationship of Dr / 2 <T <Dr−H is set.   The radial / thrust combined bearing according to claim 4, wherein the radial cage is made of various synthetic resin materials.

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