JP2012211700A - Bearing retainer for conical bearing, and conical baring - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing retainer for a conical bearing that can increase a load capacity by increasing the entire length of a conical bearing, has stable strength and a superior incorporation property, and to provide the conical bearing using the bearing retainer.SOLUTION: A retainer 4a includes a small diameter ring 9, a large diameter ring 10 and a plurality of pillars arranged between them. A hook 15 which is engaged with a large flange 8a provided at a large diameter end in a bearing inner ring 2, is provided in the large diameter ring part 10 where polyphenylene sulfide is filled with a resin reinforcement material, and when a filling ratio of the resin reinforcement material is defined as M, M is made to become 0 wt.%<M<10 wt.%.

Description

  The present invention relates to a tapered roller bearing cage and a tapered roller bearing using the tapered roller bearing cage.

  Engine driving force in an automobile is transmitted to wheels via a power transmission system including any or all of a transmission, a propeller shaft, a differential, and a drive shaft.

  As an example of this transmission (transmission), there is a synchronous mesh transmission shown in FIG. In this transmission, a main shaft 95 and a sub shaft (not shown) arranged in parallel at a predetermined interval are rotatably supported by a transmission case (not shown), and the main shaft 95 is interlocked with an output shaft (drive wheel side). The auxiliary shaft is linked to the input shaft (engine side).

  A countershaft gear 96 is provided integrally (or separately) on the countershaft, and a main shaft gear 91 is rotatably mounted on the main shaft 95 via a tapered roller bearing A. A tooth portion 91a that always meshes with the countershaft gear 96 is integrally provided at a central portion of the outer peripheral surface of the main shaft gear 91, and a clutch gear 97 is engaged and connected to both end portions. The clutch gear 97 is integrally formed with spline teeth 97 a on the outer periphery and a conical cone 97 b on one side, and a synchronization mechanism 98 is disposed in the vicinity of the clutch gear 97.

  The synchronizer 98 includes a sleeve 81 that moves in the axial direction (left and right in the figure) by the operation of a selector (not shown), a synchronizer key 82 that is mounted on the inner periphery of the sleeve 81 so as to be axially movable, A hub 83 engaged and connected to the outer periphery of the main shaft 95, a synchronizer ring 84 slidably mounted on the outer periphery of the cone 7b of the clutch gear 7, and a synchronizer key 82 are elastically attached to the inner periphery of the sleeve 81. A pressing pin 85 and a spring 86 for pressing are provided.

  In the state shown in the figure, the sleeve 81 and the synchronizer key 82 are held in the neutral position by the pressing pin 85. At this time, the main shaft gear 91 rotates idly with respect to the main shaft 95 in response to the rotation of the countershaft gear 96. On the other hand, when the sleeve 81 moves to the left side in the axial direction from the state shown in the figure by the operation of the selector, the synchronizer key 82 moves to the left side in the axial direction following the sleeve 81 and the synchronizer ring 84 is moved to the clutch gear 7. Against the inclined surface of the cone 7b. As a result, the rotational speed on the clutch gear 97 side decreases, and conversely, the rotational speed on the synchro mechanism 98 side increases.

  When the rotational speeds of the two are synchronized, the sleeve 81 further moves to the left in the axial direction, meshes with the spline teeth 97a of the clutch gear 97, and the main shaft gear 1 and the main shaft 5 are connected via the synchro mechanism 98. Is done. Accordingly, the rotation of the countershaft gear 6 is decelerated at a predetermined speed ratio by the main shaft gear 91 and transmitted to the main shaft 95. At this time, the main shaft gear 91 rotates in synchronization with the main shaft 95 and the bearing inner ring 92 of the tapered roller bearing A.

  The tapered roller bearing A used for the main shaft gear mechanism of a synchronous mesh transmission of an automobile has a main shaft gear 91 also used as a bearing outer ring, a raceway surface 92a on the outer peripheral surface, and is fitted on the outer periphery of the main shaft 95. A pair of bearing inner rings 92, a double row tapered roller 93 disposed between the double row raceway surface 91 c of the main shaft gear 91 and the raceway surface 2 a of the pair of bearing inner rings 2, and each row of tapered rollers 93 are respectively provided. It is comprised with a pair of holder | retainer 94 to hold | maintain. A small flange is formed on the raceway surface 92a of the bearing inner ring 92 and a large flange is formed on the large diameter side. In the retainer 94, a plurality of pockets for holding the tapered rollers 93 are arranged at a predetermined pitch along the circumferential direction.

  As shown in FIG. 7, the differential has a drive pinion shaft 42 disposed at the front portion of the differential case 41 and is rotatably supported by a pair of tapered roller bearings 44 and 45. A front end portion of the drive pinion shaft 42 is connected to a propeller shaft (not shown), and a drive pinion gear (reduction small gear) 43 that meshes with a ring gear (reduction large gear) 46 is fixed to the rear end portion or formed integrally. It is.

  The ring gear 46 is attached to a differential gear case 47, and the differential gear case 47 is rotatably supported with respect to the differential case 41 by a pair of tapered roller bearings 48 and 49. In the differential gear case 47, a pair of pinion gears 50 and a pair of side gears 51 that mesh with the pinion gears 50 are respectively arranged. The pinion gear 50 is fixed to the pinion shaft 52, and the side gear 51 is attached to the differential gear case 47 through a thrust washer. Left and right drive shafts (not shown) are coupled to the corresponding side gears 51 so as to be able to transmit torque by serration or the like.

  The drive torque of the propeller shaft is transmitted through a path of drive pinion gear 43 → ring gear 46 → differential gear case 47 → pinion gear 50 → side gear 51 → drive shaft. On the other hand, the driving resistance of the tire is transmitted from the drive shaft → the side gear 51 → the pinion gear 50.

  Each tapered roller bearing shown in FIG. 7 is a so-called single row. As shown in FIG. 8, such a single-row tapered roller bearing includes an inner ring 72 having a tapered raceway surface 75 on the outer peripheral surface, an outer ring 71 having a tapered raceway surface 76 on the inner peripheral surface, and an inner ring. 72, a plurality of tapered rollers 73 interposed between the raceway surface 75 of the outer ring 71 and the raceway surface 76 of the outer ring 71, and a retainer 74 that holds the plurality of tapered rollers 73 at predetermined intervals in the bearing circumferential direction. Are the main components. Further, in the inner ring 72, a small flange 77 is formed on the small diameter side of the raceway surface 75, and a large collar 78 is formed on the large diameter side of the raceway surface 75. The retainer 74 in this case is also provided with a plurality of pockets for holding the tapered rollers 73 at a predetermined pitch along the circumferential direction.

  By the way, with the expansion of the interior space, the engine room is shrinking, the engine output is increased, the transmission is multistaged to improve fuel efficiency, and the usage environment of the tapered roller bearings used therein becomes severe year by year. It is coming. In order to satisfy the life of the bearing in the usage environment, it is necessary to further extend the life of the bearing.

  Therefore, it can be proposed to increase the load capacity with the same dimensions and increase the life of the bearing by increasing the number of tapered rollers or increasing the overall length of the tapered rollers. However, in order to prevent the tapered roller held by the cage from falling off, as shown in FIGS. 6 and 8, a small collar 67 (77) is provided on the outer periphery of the inner ring on the small end side of the tapered roller. For this reason, the full length of the tapered roller 93 (73) cannot be lengthened. Further, between the tapered rollers 93 (73), there is a retainer pillar portion (between adjacent pockets) for holding the tapered rollers 93 (73). For this reason, the number of the tapered rollers 93 (73) cannot be increased. In other words, there was a limit to increasing the load capacity by the gavel 67 (77) and the pillar.

  For this reason, there is one that omits the small flange on the outer periphery of the inner ring on the small end side of the tapered roller (Patent Document 1). That is, an annular large collar is formed only on the outer peripheral large end side of the inner ring, and a collar portion (small collar) is omitted on the small diameter side of the inner ring. Further, by providing a hook portion that can be engaged with the inner ring on the large end side of the cage, the tapered roller 3 is prevented from dropping from the cage 4.

  As described above, iron cages (iron plate cages) are mainly used as the cages in the tapered roller bearings used for transmission and differential. Recently, resin cages are often used.

  The advantages of resin cages are that large quantities can be recovered by injection molding, the productivity is good, and the resin cages molded by injection molding are shaped compared to iron plate cages molded by press processing. There is freedom.

  Tapered roller bearings are often used in differentials that use a lot of oil that is particularly aggressive against resin, so when using a cage made of resin, it has high oil resistance and strength among super engineering plastics. In addition, PPS (poniphenylene sulfide) having excellent toughness is preferable.

  When a PPS resin cage is applied to a tapered roller bearing, short fibers (resin reinforcing material) such as glass fiber and carbon fiber may be mixed as a reinforcing material in order to improve mechanical properties (Patent Document 3 and Patent Document 4).

Japanese Utility Model Publication No. 58-165324 JP 2002-54638 A Japanese Patent No. 2628674 JP 2004-76747 A

  If you eliminate the gavel, you can lengthen the entire length of the tapered roller, but the length of the tapered roller will increase, and the amount of protrusion from the inner ring of the small diameter ring will increase in the cage, causing interference with other parts. Arise. In particular, when such a single-row tapered roller bearing is overlapped to form a double-row tapered roller bearing, opposing cages interfere with each other.

  In addition, in the case where the cage is provided with a hook portion that can be engaged with the large collar of the inner ring, the cage requires flexibility in consideration of assembling workability. However, when a resin filled with a resin reinforcing material is used for the cage, the flexibility is inferior even if the strength can be improved. For this reason, the cage may be damaged during assembly.

  In view of the above-mentioned problems, the present invention can increase the load capacity by increasing the overall length of the tapered roller, and is stable in strength and has excellent ease of incorporation, and A tapered roller bearing using such a cage is provided.

  A tapered roller bearing retainer according to the present invention is a retainer used for a tapered roller bearing that rotatably supports a transmission for a vehicle, and is disposed between a small-diameter ring portion, a large-diameter ring portion, and the like. A large-diameter ring portion having a hook portion that can be engaged with a large flange provided at a large-diameter side end portion of the bearing inner ring, and filling the resin reinforcement with poniphenylene sulfide. Thus, when the filling factor of the resin reinforcing material is M, 0 wt% <M <10 wt%.

  According to the tapered roller bearing retainer of the present invention, poniphenylene sulfide is filled with a resin reinforcing material. Poniphenylene sulfide (PPS) is a high-performance engineering plastic having a molecular structure in which phenyl groups (benzene rings) and sulfur (S) are alternately repeated. It is crystalline and has a continuous use temperature of 200 ° C. to 220 ° C., a high deflection temperature under a high load (1.82 MPa) of 260 ° C. and excellent heat resistance, and has a high tensile strength and bending strength. Since the shrinkage rate during molding is as small as 0.3 to 0.5%, the dimensional stability is good. Excellent in flame retardancy and chemical resistance. PPS can be broadly classified into three types: cross-linked, linear, and semi-cross-linked. The cross-linked type is a high molecular weight product obtained by cross-linking a low molecular weight polymer, and is mainly brittle and reinforced with glass fiber. The straight-chain type has a high toughness and has a high molecular weight without a crosslinking step in the polymerization stage. The semi-cross-linked type has the characteristics of both the cross-linked type and the straight chain type. For this reason, it is most suitable for a differential apparatus and a transfer apparatus in which oil with high aggressiveness to resin is frequently used.

  The reinforcing material is filled with more than 0% by weight and less than 10% by weight, and the strength can be improved. Moreover, since the filling amount of the resin reinforcing material is less than 10% by weight, the fluidity of the resin is not much different from that in which the resin reinforcing material is not filled.

  The resin reinforcing material may be a fiber reinforcing material such as carbon fiber or glass fiber. It may be carbon fiber or glass fiber. Here, the carbon fiber is a fiber made by carbonizing an acrylic fiber or pitch (by-products such as petroleum, coal, coal tar, etc.) at a high temperature. Carbon fibers using the former raw material are classified as PAN (Polyacrylonitrile), and carbon fibers using the latter are classified as PITCH. It is an aggregate of carbon in a broad sense. High strength is obtained by the combination of graphite. Graphite is an elemental mineral consisting of carbon. Carbon fiber is excellent in wear resistance, heat resistance, thermal stretchability, acid resistance, electrical conductivity, tensile resistance, and the like, and has an advantage of being lighter than metals such as aluminum. Further, the glass fiber is a fibrous material made by thinly stretching a molten glass and rapidly solidifying it. They are classified into long fibers and short fibers according to the fiber type, and are roughly classified into alkali glass fibers and alkali-containing glass fibers according to the composition. Glass fiber is excellent in corrosion resistance, heat resistance, moisture resistance, and electrical insulation. For this reason, it becomes a lightweight and strong raw material by mixing carbon fiber and glass fiber with resin.

  In addition, since the large-diameter ring portion has a hook that can be engaged with the large flange provided at the large-diameter end of the bearing inner ring, the tapered roller held in the cage is prevented from falling off, and the bearing inner ring is small. Can eliminate wrinkles. In addition, since the length of the raceway surface and the length of the tapered roller can be increased while suppressing an increase in the axial length of the bearing inner ring, the load capacity of the bearing can be improved.

  The tapered roller bearing of the present invention is a tapered roller bearing using the tapered roller bearing retainer according to claim 1 or 2, and has a roller coefficient γ exceeding 0.94. Here, the roller coefficient γ is defined by the following equation.

Roller coefficient γ = (Z · DA) / (π · PCD)
Here, Z: Number of rollers, DA: Roller average diameter, PCD: Roller pitch circle diameter

  The tapered roller bearing of the present invention is a tapered roller bearing using the tapered roller bearing retainer according to claim 1 or 2, wherein the window angle of the pocket of the retainer is 55 ° or more and 80 ° or less. Is. Here, the window angle of the pocket (between adjacent column portions along the circumferential direction) refers to an angle formed by a surface of the column portion that contacts the rolling surface of the tapered roller.

  The small diameter side end surface of the small diameter ring portion and the outermost diameter portion of the outer peripheral edge of the small end surface of the tapered roller are such that when the small diameter side end surfaces of the pair of inner rings are brought into contact with each other, the small diameter ring portions of the pair of cages are not in contact with each other. However, it is preferable that the end face on the small-diameter side of the small-diameter ring portion is located on the inner side of the plane orthogonal to the bearing central axis. Thereby, interference of a small diameter ring part with other members and cages can be prevented.

  Moreover, it is preferable that the large hook provided at the large diameter side end portion of the inner ring has a circumferential groove in which the hook portion is engaged. By having the circumferential groove in the large collar, it is possible to improve the engagement of the hook portion with the large collar.

  In the tapered roller bearing retainer of the present invention, the large diameter side of the retainer is provided with a hook portion that can be engaged with the large collar of the bearing inner ring, so that the tapered roller held by the retainer is prevented from falling off, and the bearing inner ring Can eliminate the gavel. In addition, since the length of the raceway surface and the length of the tapered roller can be increased while suppressing an increase in the axial length of the bearing inner ring, the load capacity of the bearing can be improved.

  It has the advantages of being made of resin (good productivity, easy application of special shapes, etc.), and the resin to be used is filled with resin reinforcing material, so the strength can be improved and the machine Characteristics can be improved. In particular, poniphenylene sulfide has high oil resistance among super engineering plastics, and is excellent in strength and toughness. For this reason, this cage made of resin-reinforced material filled in Poniphenylene Sulfide is most suitable for tapered roller bearings used in differential devices and transmission devices where oils that are highly attacking the resin are used. Tapered roller bearings using a container can exhibit stable functions over a long period of time.

  Since the filling rate of the resin reinforcement is 0% by weight <M <10% by weight, it has flexibility, and the assembly work where the engaging part (hanging part) gets over the ridge when assembled. Can be performed stably, and the hooking portion or the like is not damaged during the assembly. In other words, if the resin reinforcing material is not filled, the strength of the cage cannot be improved. Conversely, if the filling rate of the resin reinforcing material is 10% by weight or more, the rigidity is high and the flexibility is low, and it is hooked when assembled. There is a risk of damage to parts.

  Since the filling rate of the resin reinforcing material is less than 10% by weight, the fluidity of the resin is not much different from that in which the resin reinforcing material is not filled, and the resin does not flow easily in the cavity for forming the small diameter ring portion. It flows without becoming. For this reason, generation | occurrence | production of the weld part in a small diameter ring part can be suppressed, and the holder | retainer from which a weld part does not arise in the small diameter side can be provided. This can prevent premature breakage due to the weld portion of the cage.

  The resin reinforcing material may be carbon fiber or glass fiber, and these make the resin used light and strong. For this reason, the cage in which such a resin reinforcing material is filled in poniphenylene sulfide can stably improve the strength, and also has heat resistance, flame resistance, oil resistance, chemical resistance, and the like. Excellent. In addition, excellent dimensional stability can be exhibited.

  If the roller coefficient γ exceeds 0.94, the load capacity can be increased to the level of a full roller bearing (bearing not using a cage) without changing the bearing dimensions. Thereby, the contact surface pressure can be reduced, the surface pressure in the stopped state is relaxed, and the fretting resistance is improved. In addition, a good contact state can be secured between the cage and the tapered roller, and the roller can be smoothly rotated.

  Moreover, by setting the cage window angle to 55 ° or more, the pillar width of the cage can be increased, and a good contact state with the tapered roller can be secured. By setting the angle to 80 ° or less, the pressing force in the radial direction does not increase, and smooth rotation can be obtained.

  Other members and double-row combinations are used in the case where the small-diameter side end surface of the small-diameter ring portion and the outermost diameter portion of the outer peripheral edge of the small end surface of the tapered roller are substantially disposed on a plane orthogonal to the bearing central axis. In this case, it is possible to prevent the small-diameter ring portion from interfering with the cages.

  By engaging the hook portion with the circumferential groove, it is possible to improve the engagement of the hook portion with respect to the large flange, and the reliability of preventing the tapered roller from falling off is improved. In addition, the weight can be reduced by forming the circumferential groove.

It is principal part sectional drawing of the tapered roller bearing using the holder | retainer which shows embodiment of this invention. It is a principal part expanded sectional view of the said tapered roller bearing. It is a top view of the said holder | retainer. It is a principal part expanded sectional view of the said tapered roller bearing. It is principal part sectional drawing of the other tapered roller bearing using the holder | retainer which shows embodiment of this invention. It is sectional drawing of a transmission apparatus. It is sectional drawing of a differential apparatus. It is principal part sectional drawing of the conventional tapered roller bearing used for the differential apparatus of the said FIG.

FIG. 1 shows an embodiment of a tapered roller bearing using a cage according to the present invention, and is used particularly in a transmission device as shown in FIG. That is, although not shown in the figure, in the transmission device, the main shaft and the sub shaft arranged in parallel at a predetermined interval are rotatably supported by the transmission case, and the main shaft is interlocked with the output shaft (drive wheel side), The secondary shaft is linked to the input shaft (engine side). The main shaft is supported by a tapered roller bearing according to the present invention (the tapered roller bearing shown in FIG. 1).

The tapered roller bearing shown in FIG. 1 is fixed to inner rings (bearing inner rings) 2a and 2b having conical raceway surfaces 5a and 5b on the outer periphery, a housing (not shown), and the like, and conical raceway surfaces 6a and 6b on the inner periphery. An outer ring (bearing outer ring) 1 having a plurality of teeth, a plurality of tapered rollers 3a, 3b interposed between the raceways of the inner rings 2a, 2b and the outer ring 1, and a plurality of tapered rollers 3a, 3b are held at equal intervals in the circumferential direction. Retainer 4a, 4b. On the large end side of the outer circumference of the inner rings 2a and 2b, annular flanges (large collars) 8a and 8b are formed. In this type of tapered roller bearing, both ends in the axial direction are often sealed with a sealing device, but this sealing device is not shown in the drawings.

  As shown in FIG. 3, the cages 4 a and 4 b include a small-diameter ring portion 9, a large-diameter ring portion 10, and a plurality of column portions 11 disposed therebetween, and a cone between the column portions 11. A pocket 12 for holding the rollers 3a and 3b is formed. Tapered rollers 3 a and 3 b are rotatably accommodated in the pockets 12, respectively. In this embodiment, 25 pockets 12 are formed.

  As shown in FIG. 1, engagement portions (hook portions) 15 that can be engaged with the large collars 8a and 8b of the inner rings 2a and 2b are formed on the large ends of the cages 4a and 4b. The hook 15 extends to the inner diameter side beyond the maximum outer diameter portion of the inner rings 2a, 2b (the outer peripheral surface of the large flanges 8a, 8b). As shown in FIG. 2, the large collars 8a, 8b of the inner rings 2a, 2b are provided with annular circumferential grooves (engagement) to accommodate the hook portions 15 protruding from the outer circumferential surface of the large collars 8a, 8b. Grooves) 17a and 17b are formed. There are slight gaps in the axial direction and the radial direction between the hook portion 15 and the circumferential grooves 17a, 17b, so that the cages 4a, 4b can move slightly in the axial direction and the radial direction. At least one hooking portion 15 is sufficient, but it may be formed at a plurality of locations in the circumferential direction. In this embodiment, six pieces are arranged at a 60 ° pitch along the circumferential direction.

  That is, the hook portion 15 has a hook with which the inner rings 2a and 2b, the tapered rollers 3a and 3b, and the cages 4a and 4b can be kept in an assembled state with respect to the flange portions 8a and 8b of the inner rings 2a and 2b. 4b is in non-contact with the flanges 8a and 8b in a neutral state with respect to the shaft center L, and is not in contact with the flanges 8a and 8b or is in contact with the flanges 8a and 8b during operation. 30 and the bottom surfaces 31 of the circumferential grooves 17a and 17b of the flanges 8a and 8b are in contact with each other.

  The small diameter side end surface 9a of the small diameter ring portion 9 and the outermost diameter portion 21 of the outer peripheral edge of the small end surface 20a of the tapered roller 3a (3b) are substantially disposed on the same plane orthogonal to the bearing center axis L. That is, the wall thickness t of the small diameter ring portion 9 is small. Thereby, as shown in FIG. 1, when the end surfaces on the small diameter side of the inner rings 2a and 2b are brought into contact with each other, the small diameter ring portion 9 of the cages 4a and 4b is set so as not to contact.

  This cage is a resin cage. As this resin, PPS (poniphenylene sulfide) of engineering plastic is used. Here, the engineering plastic is an abbreviation for engineering plastics, which is excellent in heat resistance among synthetic resins and can be used in fields where strength is required. Engineering plastics include general-purpose engineering plastics and super engineering plastics.

  PPS is a high-performance engineering plastic having a molecular structure in which phenyl groups (benzene rings) and sulfur (S) are alternately repeated. It is crystalline and has a continuous use temperature of 200 ° C. to 220 ° C., a high deflection temperature under a high load (1.82 MPa) of 260 ° C. and excellent heat resistance, and has a high tensile strength and bending strength. Since the shrinkage rate during molding is as small as 0.3 to 0.5%, the dimensional stability is good. Excellent in flame retardancy and chemical resistance. PPS can be broadly classified into three types: cross-linked, linear, and semi-cross-linked. The cross-linked type is a high molecular weight product obtained by cross-linking a low molecular weight polymer, and is mainly brittle and reinforced with glass fiber. The straight-chain type has a high toughness and has a high molecular weight without a crosslinking step in the polymerization stage. The semi-cross-linked type has the characteristics of both the cross-linked type and the straight chain type.

  The resin constituting the resin cage is filled with a resin reinforcing material in an amount of more than 0% by weight and less than 10% by weight. That is, when the filling rate of the resin reinforcing material is M, 0 wt% <M <10 wt%. As the reinforcing material, the resin reinforcing material may be a fiber reinforcing material such as carbon fiber (CF) or glass fiber (GF). Here, the carbon fiber is a fiber made by carbonizing an acrylic fiber or pitch (by-products such as petroleum, coal, coal tar, etc.) at a high temperature. Carbon fibers using the former raw material are classified as PAN (Polyacrylonitrile), and carbon fibers using the latter are classified as PITCH. It is an aggregate of carbon in a broad sense. High strength is obtained by the combination of graphite. Graphite is an elemental mineral consisting of carbon. Carbon fiber is excellent in wear resistance, heat resistance, thermal stretchability, acid resistance, electrical conductivity, tensile resistance, and the like, and has an advantage of being lighter than metals such as aluminum. Further, the glass fiber is a fibrous material made by thinly stretching a molten glass and rapidly solidifying it. They are classified into long fibers and short fibers according to the fiber type, and are roughly classified into alkali glass fibers and alkali-containing glass fibers according to the composition. Glass fiber is excellent in corrosion resistance, heat resistance, moisture resistance, and electrical insulation. For this reason, it becomes a lightweight and strong raw material by mixing carbon fiber and glass fiber with resin.

  In the cages 4a and 4b, the window pushing angle (window angle) θ (see FIG. 5) of the column surface 40 of the column part 11 is set to 55 ° or more and 80 ° or less, for example.

  The roller coefficient γ is set to exceed 0.94. Here, the roller coefficient γ is defined by the following equation. Further, the window angle θ of the pocket (between adjacent column portions along the circumferential direction) 12 is an angle formed by a surface of the column portion that contacts the rolling surface of the tapered roller 3a (3b).

Roller coefficient γ = (Z · DA) / (π · PCD)
Here, Z: Number of rollers, DA: Roller average diameter, PCD: Roller pitch circle diameter

  In the present invention, since the hook portion 15 that can be engaged with the large collars 8a and 8b of the inner rings (bearing inner rings) 2a and 2b is provided, the tapered rollers 3a and 3b are prevented from falling off. That is, until the tapered roller bearing is assembled in the machine, the tapered rollers 3a and 3b try to drop to the small end side due to their own weight, and accordingly, the pressing force in the same direction also acts on the cages 4a and 4b. . As a result, the hook 15 engages with the circumferential grooves 17a and 17b provided in the inner rings 2a and 2b, so that further displacement of the cages 4a and 4b toward the smaller end is restricted. In this case, the tapered rollers 3a and 3b are reliably prevented from falling off from the inner rings 2a and 2b of the tapered rollers 3a and 3b because the displacement of the tapered rollers 3a and 3b is restricted by the pocket surface of the pocket 12 on the small end side. It becomes possible to do. For this reason, the small wrinkles of the inner rings 2a and 2b can be eliminated. As a result, the axial dimension of the bearing can be reduced in size and weight, and the load capacity can be improved by extending the tapered roller length. In addition, the length of the raceway surfaces 5a, 5b, 6a, and 6b and the length of the tapered roller can be increased while suppressing an increase in the axial length of the inner rings 2a and 2b, thereby improving the load capacity of the bearing. Can do.

  In addition, the small-diameter side end surface 9a of the small-diameter ring portion 9 and the outermost diameter portion 21 of the outer peripheral edge of the small end surface 20a of the tapered rollers 3a and 3b are substantially disposed on a plane orthogonal to the bearing center axis, In the case of a double-row tapered roller bearing or a single-row tapered roller bearing in the case of using a cage, interference with a mating part such as a housing can be prevented. For this reason, it is excellent in mounting property (incorporation property to other members).

  In particular, the cages 4a and 4b are made of resin and have advantages (good productivity, easy application of special shapes, etc.), and the resin to be used is filled with a resin reinforcing material. Improvement can be achieved and mechanical characteristics can be improved. In particular, poniphenylene sulfide has high oil resistance among super engineering plastics, and is excellent in strength and toughness. For this reason, the cages 4a and 4b formed by filling a resin reinforcing material into the poniphenylene sulfide are optimal for tapered roller bearings used in transmission devices and the like that use a lot of oil that is highly aggressive to the resin. A tapered roller bearing using a cage can exhibit a stable function over a long period of time.

  Further, since the filling rate of the resin reinforcing material is more than 0% by weight and less than 10% by weight, it has flexibility, and the assembling work in which the hooking portion 15 gets over the large fence is stably performed during assembling. In addition, the hook portion 15 and the like are not damaged during the assembly. That is, if the resin reinforcing material is not filled, the strength of the cages 4a and 4b cannot be improved. Conversely, if the filling rate of the resin reinforcing material is 10% by weight or more, the rigidity becomes large and the flexibility is inferior. There is a possibility that the hook 15 or the like may be damaged when assembled. In order to further improve the strength of the cages 4a and 4b, the filling rate of the resin reinforcing material is preferably 5% by weight or more.

  Since the filling rate is less than 10% by weight, the fluidity is not much different from that in which the reinforcing material is not filled, and the resin flows without becoming difficult to flow even in the cavity for forming the small-diameter ring portion. For this reason, generation | occurrence | production of the weld part in the small diameter ring part 9 can be suppressed, and the holder | retainers 4a and 4b which a weld part does not produce on the small diameter side can be provided. This can prevent premature breakage due to the weld portion of the cage.

  As described above, the resin reinforcing material may be carbon fiber or glass fiber, and the resin to be used becomes a lightweight and strong material. For this reason, the cages 4a and 4b in which such a resin reinforcing material is filled in poniphenylene sulfide can stably improve the strength, heat resistance, flame resistance, oil resistance, and chemical resistance. Excellent in properties. In addition, excellent dimensional stability can be exhibited.

If the roller coefficient γ exceeds 0.94, the load capacity can be increased to the level of a full roller bearing (bearing not using a cage) without changing the bearing dimensions. As a result, the contact surface pressure can be reduced, and smooth operation (rotation) can be achieved over a long period.

  Further, by setting the window angle θ of the cages 4a and 4b to 55 ° or more, the column width of the cage can be increased, and a good contact state with the tapered rollers 3a and 3b can be secured, By setting the window angles of the cages 4a and 4b to 80 ° or less, the pressing force in the radial direction is not increased, and smooth rotation can be obtained.

  The tapered roller bearing of the present invention may be a single row as shown in FIG. That is, the tapered roller bearing includes an inner ring 62 having a conical raceway surface 65 on the outer peripheral surface, an outer ring 61 having a conical raceway surface 66 on the inner peripheral surface, a raceway surface 65 of the inner ring 62, and a raceway of the outer ring 61. The main components are a plurality of tapered rollers 63 interposed between the surface 66 so as to be freely rollable, and a retainer 64 that holds the plurality of tapered rollers 63 at a predetermined interval in the bearing circumferential direction. The inner ring 62 is formed with a large collar 18 on the large diameter side of the raceway surface 65. The retainer 64 in this case is also provided with a plurality of pockets for holding the tapered rollers 63 at a predetermined pitch along the circumferential direction.

  The cage 64 includes a small-diameter ring portion 69 and a large-diameter ring portion 70, and the hook portion 15 is provided on the large-diameter ring portion 70. A circumferential groove 17 with which the hook 15 of the retainer 64 is engaged is formed in the large collar 68 of the inner ring 62.

  And the tapered roller bearing comprised in this way can also be used for a differential apparatus as shown in FIG. That is, although not illustrated, the differential device includes a differential case, a differential reduction mechanism disposed in the differential case, a pinion gear that meshes with a ring gear of the differential reduction mechanism, and a pinion shaft that supports the pinion gear. . The pinion shaft is supported by the tapered roller bearing according to the present invention (the tapered roller bearing shown in FIG. 5).

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. For example, the number of pockets 12 of the retainers 4a and 4b is retained. Various changes can be made according to the number of tapered rollers 3a and 3b. Further, the length and thickness of the column portion 11 can be variously changed as long as the tapered rollers 3a and 3b can be held. A single-row tapered roller bearing may be used. As the reinforcing material to be filled, in addition to CF and GF, an aramid fiber that is a resin fiber having high strength may be used. Here, an aramid fiber is a polyamide fiber whose molecular skeleton is composed of an aromatic (benzene ring).

  In the above-described embodiment, the circumferential groove 17 is provided in the large bowl 8. However, such a circumferential groove 17 may not be provided, and instead of the circumferential groove 17, the circumferential groove 17 is provided at a position corresponding to the hook portion 15. Cutout portions may be formed at a predetermined pitch along the circumferential direction.

The oil immersion test was conducted on PPS used in the present invention, and other super engineering plastics PA46 (polyamide 46) and PA66 (polyamide 66), and the results are shown in Tables 1 and 2 below. Table 1 shows the strength reduction rate of tensile strength, and Table 2 shows the strength reduction rate of bending strength.

As the oil, Mitsubishi genuine diamond queen "Super Hypoid Gear Oil SAE90 GL-5" was used. Also, as specimens, BASF Japan Co., Ltd .: Ultramid A3HG5 (PA66 filled with 25% by weight of GF (glass fiber)) and DSMJSR Engineering Plastics Co., Ltd .: TW200F5-70G320 (PA36 to GF) And Dainippon Ink & Chemicals, Inc .: a mixture of Z230 and Z200-5E (PPS filled with GF at 7.5% by weight), and Each produced so-called dumbbell specimens.

  Moreover, as a test, each test piece was immersed in the said oil, and the tensile strength test and bending strength were done after immersion and before immersion. In this case, strength deterioration was confirmed every 500 hours. As can be seen from Tables 1 and 2, when PPS was used, no deterioration was seen in the tensile strength and bending strength even when the immersion time exceeded 2000 hours.

Tests were conducted on the flexibility of the cage, and the results are shown in Table 3 below. As a tapered roller bearing, use “30206U: Inner ring inner diameter 30 mm, outer ring outer diameter 62 mm, axial dimension 17.25 mm” manufactured by NTN Corporation. It was supposed to be equipped with a captain. As an assembling method, a method was adopted in which the rollers were put in the cage pockets and then climbed over the gavel of the inner ring. Also, as a cage, PPS filled with GF (glass fiber) at 30 wt%, PPS filled with GF at 15 wt%, PPS filled with GF at 10 wt%, PPS filled with GF Four types of those filled at 5% by weight were produced.

  As can be seen from Table 3 where the applicability was confirmed on the basis of the radial extension dimension necessary for incorporation, a filling rate of 15% or less is considered to be an applicable range. Thus, it can be seen that when the filling rate exceeds 15%, there is a problem in assemblability.

2 Inner ring 4 Cage 8 Large flange 9 Small diameter ring portion 9a Small diameter side end surface 10 Large diameter ring portion 11 Column portion 15 Hook portion 17 Circumferential groove 20a Small end surface 21 Outermost diameter portion

Claims (7)

A cage used for a tapered roller bearing that rotatably supports a transmission for a vehicle,
Equipped with a small-diameter ring part, a large-diameter ring part, and a plurality of pillars arranged between them, and can be engaged with a large collar provided at the large-diameter side end of the bearing inner ring. Cone characterized by having a hook portion and filling the resin reinforcement with Poniphenylene Sulfide, and assuming that the filling rate of the resin reinforcement is M, 0 wt% <M <10 wt% Roller bearing cage.   2. The tapered roller bearing retainer according to claim 1, wherein the resin reinforcing material is a fiber reinforcing material. A tapered roller bearing using the tapered roller bearing retainer according to claim 1 or 2,
The tapered roller bearing, wherein the roller coefficient γ exceeds 0.94. A tapered roller bearing using the tapered roller bearing retainer according to claim 1 or 2,
A tapered roller bearing wherein the window angle of the pocket of the cage is 55 ° or more and 80 ° or less.   The inner diameter edge of the hook is a flat surface, and the large-diameter side end surface or outer surface of the large collar and the small-diameter side end surface of the cage form parallel surfaces. The tapered roller bearing described.   The small diameter side end surface of the small diameter ring portion and the outermost diameter portion of the outer peripheral edge of the small end surface of the tapered roller are such that when the small diameter side end surfaces of the pair of inner rings are brought into contact with each other, the small diameter ring portions of the pair of cages are not in contact with each other. Is disposed substantially on a plane orthogonal to the bearing central axis, or the small-diameter side end surface of the small-diameter ring portion is on the inner side of the plane orthogonal to the bearing central axis. The tapered roller bearing according to any one of the above.   The tapered roller bearing according to any one of claims 3 to 6, wherein a large groove provided at an end portion on the large diameter side of the inner ring has a circumferential groove with which the hook portion is engaged.

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