WO2009087957A1 - Butée à rouleaux, et dispositif de retenue associé - Google Patents

Butée à rouleaux, et dispositif de retenue associé Download PDF

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Publication number
WO2009087957A1
WO2009087957A1 PCT/JP2009/000007 JP2009000007W WO2009087957A1 WO 2009087957 A1 WO2009087957 A1 WO 2009087957A1 JP 2009000007 W JP2009000007 W JP 2009000007W WO 2009087957 A1 WO2009087957 A1 WO 2009087957A1
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WO
WIPO (PCT)
Prior art keywords
cage
diameter side
plate
roller bearing
component plate
Prior art date
Application number
PCT/JP2009/000007
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English (en)
Japanese (ja)
Inventor
Kazuyuki Yamamoto
Original Assignee
Ntn Corporation
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Filing date
Publication date
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2009087957A1 publication Critical patent/WO2009087957A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/547—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from two parts, e.g. two discs or rings joined together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly

Definitions

  • the present invention relates to a thrust roller bearing used in an automobile transmission, a torque converter, a car air-conditioning compressor, and the like, and a cage for the same.
  • Thrust roller bearings used in torque converters are susceptible to eccentric rotation between the engine and transmission. Further, in thrust roller bearings for transmissions, misalignment occurs in the bearing mounting portion due to accumulation of tolerances of peripheral parts.
  • Patent Document 1 has a description that a conventional thrust roller bearing which is a two-piece type (box-shaped) cage has insufficient prevention of slippage
  • Patent Document 3 has a conventional W
  • a short roller is dropped in a thrust roller bearing as a shape cage (M-type cage).
  • M-type cage shape cage
  • a three-position integrated thrust roller bearing used in a torque converter or transmission that is, two L-shaped hooked race rings 32 and 33 and rollers with cages (cage as shown in FIGS. 11 and 12).
  • the cages 40 and 40A may be sandwiched between the flanges 32b and 33b of the both race rings 32 and 33, and the cages 40 and 40A may have a short life.
  • thrust roller bearings for transmissions there are many types with only a cage and roller that do not require a race ring with the other part as a direct rolling surface in addition to those with a race ring as shown in FIGS. Although used, these bearings are required to have oil permeability in order to supply lubricating oil to peripheral parts through the bearings. Furthermore, since thrust roller bearings used in car air conditioner compressors are used under lean lubrication, there is a need for improved wear resistance and lubrication conditions. As a specific example, in order to obtain oil permeability for feeding lubricating oil to peripheral parts and cooling performance of roller contact portions (roller rolling surface, roller pair cage), the roller surface is exposed more from the cage. Is required.
  • Patent Document 7 describes an example of damage in a thrust roller bearing used as a conventional two-piece type (tuftride treated product) cage
  • Patent Document 11 describes a conventional two-piece type (box Type) Thrust roller bearings used as cages have a description of poor lubricity.
  • Patent Literature A structure in which a cage is prevented from being pinched against eccentricity.
  • Patent Document 4 A structure that absorbs a radial load with an elastic ring against eccentricity.
  • Patent Document 5 A structure in which the guide surface with the raceway of the cage is a convex curved surface to improve lubricity.
  • Patent Document 6 A structure that prevents the roller chamfered portion from entering the end face of the cage pocket.
  • Patent Document 8 A measure for improving the lubricity of the pocket removal surface.
  • Patent Document 9 Structure having improved lubricity by using a W-shaped cage as a rolling element guide.
  • Japanese Patent No. 3900843 Japanese Patent No. 3692585 Japanese Patent No. 3661133 Japanese Patent No. 3632262 JP 2007-187207 A Japanese Patent Laid-Open No. 2007-100775 JP 2006-189133 A JP 2005-83449 A JP 2003-106336 A JP 2002-339984 A JP 2002-70872 A
  • the thrust roller bearing retainer includes a two-piece (box-shaped) retainer 40 as shown in FIG. 11 and a W-shaped retainer 40A as shown in FIG. Since it is difficult to incorporate the rollers 34 by elastically deforming the conventional two-sheet type (box-type) cage 40, processing is performed in the order of heat treatment of the steel plate ⁇ roller assembly ⁇ bending (caulking). It is. 12 has a structure in which the rollers 34 are more exposed from the cage 40A than the box-type cage 40 of FIG. 11, and thus has a high cooling effect.
  • the conventional two-piece type (box type) cage 40 and W-type cage 40A have advantages and disadvantages as listed below.
  • Two-sheet type (box type) cage 40 (Advantages) -Since the cross-sectional shape is substantially quadrilateral, it is strong against radial loads (clamped by cages 32, 33). -Since the cross-sectional shape is approximately square, even short rollers can be held. (Cons) -Since the rolls are crimped after heat treatment, cracks are likely to occur and the prevention of loosening is insufficient. (In Patent Document 1, there is a description that raw materials before quenching are easier to bend) -For this reason, it is not suitable for improving wear resistance by carburizing and hardening and increasing the number of hardened layers.
  • An object of the present invention is to provide a thrust roller bearing that can avoid the influence of eccentric rotation and that is oil-permeable and can ensure the cooling performance of the contact portion, and a cage for the same.
  • the rollers are held in pockets provided at a plurality of locations in the circumferential direction in a cage including at least a first cage component plate and a second cage component plate that are axially overlapped with each other.
  • the first cage component plate is a flat plate-shaped portion that is positioned on the inner diameter side and the outer diameter side and facing each other in the axial direction, and the outer diameter side flat portion and the outer diameter side flat portion, respectively.
  • a central flat portion that is in the middle in the radial direction with respect to the inner diameter side flat portion and the outer diameter side flat portion and is axially offset, and an inner diameter side continuous from the outer peripheral edge of the inner diameter side flat portion to the inner peripheral edge of the central flat portion
  • the second retainer component plate is a first retainer component plate having a cross-sectional shape having an outer diameter side continuous portion continuing from the inner periphery of the outer diameter side flat portion to the outer periphery of the central flat portion.
  • the inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate are respectively disposed between the inner diameter side folded portion and the flat plate portion and between the outer diameter side folded portion and the flat plate portion. It is sandwiched.
  • the second cage component plate is formed in a flat shape, and the first cage component plate is held by the inner diameter side folded portion and the outer diameter side folded portion.
  • stress on the bent first retainer component plate is reduced.
  • the second cage component plate since the second cage component plate does not have a bent portion like the first cage component plate, the second cage component plate is strong against a radial force. Because of the strong second cage component plate, the stress on the bent portion of the first cage component plate can be reduced, thereby avoiding a short life of the cage.
  • the cage in a so-called three-piece integral type thrust roller bearing having two L-shaped raceways, the cage is held between inner and outer rings under rotational conditions with a unit eccentricity larger than the radial clearance inside the bearing. Although a radial load acts on the cage, as described above, the stress on the bent portion of the cage can be reduced without increasing the size of the bearing, so that the cage can be prevented from being damaged.
  • the bent portion of the first cage component plate is not a complicated shape like the W-type cage in the conventional example, and the bending process by the press does not require a plurality of steps and only needs to be performed once. Therefore, the thickness of the bent portion hardly decreases with respect to the original plate thickness, and the stress on the bent portion can be further reduced.
  • the box-type cage and the W-type cage in the conventional thrust roller bearing have a substantially rectangular cross section, whereas the cross section of the cage in the thrust roller bearing has a substantially triangular shape. It is also possible to ensure a good oil permeability.
  • the inner diameter side folded portion and the outer diameter side folded portion of the second cage component plate can be formed into an arcuate curved surface
  • the cage and the inner and outer rings The inflow property of the lubricant to the contact surface is improved.
  • the thrust roller bearing is configured only by the cage that holds the roller, the inflow of the lubricant to the contact surface of the guide portion of the mating member that becomes the cage and the rolling surface is improved.
  • a three-piece integrated thrust roller bearing which is a bearing with two bearing rings, is configured by making the inner diameter side folded portion and the outer diameter side folded portion of the second cage component plate into an arcuate curved surface.
  • the frictional resistance is reduced by reducing the contact area between the inner and outer diameter surfaces of the cage and the inner and outer rings, and the torque can be reduced.
  • Even when a thrust roller bearing is configured with only a cage that holds the roller the contact area between the cage and the guide portion of the mating member that becomes the rolling surface is reduced, so that frictional resistance is reduced and low torque is achieved. can do.
  • the structure of the cage can expose most of the surface of the roller from the cage as compared with the conventional box-type cage, so that the cooling effect of the roller contact portion is increased.
  • the oil permeability and the lubrication performance such as the cooling effect of the contact portion can also prevent the life from being reduced due to wear or heat generation even under severe conditions such as lean lubrication. By the above effects, the influence of eccentric rotation can be avoided, and the oil permeability can be ensured for the cooling performance of the contact portion.
  • the first cage component plate and the second cage component plate are heat-treated products of steel plates, and the inner diameter side folded portion and the outer diameter side folded portion are subjected to crimping in an unheat treated state.
  • the formed part may be sufficient.
  • it is easy to perform the caulking process a large tightening force can be obtained, and sufficient loosening can be prevented.
  • heat treatment is performed after caulking, a wide range of wear resistance technologies such as carburizing and quenching, hardening layer upgrade, and surface treatment can be adopted as heat treatment, expanding the range of functions, costs, and productivity.
  • the crimping process plastic processing
  • the processing time by the press crimping can be shortened.
  • the first cage component plate and the second cage component plate are heat-treated products of steel plates, and each roller is incorporated into the heat-treated cage. good. That is, the cage is heat-treated before assembling the rollers. With this configuration, it is not necessary to crimp the cage while securing the appropriate gap between the rollers and the cage pocket while holding the rollers, so that high parts accuracy and assembly accuracy are not required, and assembly costs Can be prevented.
  • the pocket of the cage is formed by a pocket hole punched and formed in the first cage component plate by pressing and a pocket hole punched and formed in the second cage component plate by pressing.
  • the return portions generated by the punching may be on the non-overlapping surface side. In the case of this configuration, it is possible to obtain a certain pocket gap without being affected by the return portion due to punching, and to stabilize the behavior of the cage.
  • the width dimension in the cage radial direction of the pocket hole of the second cage component plate is longer than the width dimension in the cage radial direction of the pocket hole of the first cage component plate constituting the pocket. You may do it.
  • a large amount of lubrication to the end face of the roller can be ensured.
  • the cage since the cage is structured to receive the end surface of the roller at the end surface along the circumferential direction of the cage of the pocket hole of the first cage component plate located near the roller axis, the inclination of the roller Therefore, even short rollers can be held.
  • the width dimension in the cage circumferential direction of the pocket hole of the first cage component plate is larger than the width dimension in the cage circumferential direction of the pocket hole of the second cage component plate constituting the pocket. May be lengthened.
  • the oil passage opening which is a part where the width dimension of the pocket hole in the circumferential direction of the pocket hole is locally increased at the edge portion along the radial direction of the pocket hole of the pocket hole of the second cage component plate May be provided.
  • oil permeability can be improved by providing an oil passage port at the edge portion along the cage radial direction of the pocket hole of the second cage component plate.
  • a flat raceway plate portion and an inner ring having a cylindrical portion extending from the inner peripheral edge of the raceway plate portion, a flat raceway plate portion facing the raceway plate portion of the inner race, and an outer peripheral edge of the raceway plate portion
  • An outer ring having a cylindrical portion extending from the inner ring to the inner ring side, the retainer, and the rollers, and each roller held by the retainer is interposed between the inner ring and the raceway plate portion of the outer ring, and is eccentric with each other.
  • the cage In a three-piece integral type thrust roller bearing having two L-shaped raceways, the cage is held in the radial direction by being sandwiched between inner and outer rings under rotational conditions with a unit eccentricity larger than the radial clearance inside the bearing. Load acts.
  • the thrust roller bearing retainer of the present invention is used for the above-described thrust roller bearing.
  • FIG. 3 is a plan view of a cage pocket viewed from the direction of arrow A in FIG. 2.
  • FIG. 3 is a plan view of a cage pocket viewed from the direction of arrow B in FIG. 2. It is sectional drawing which cut the roller holding
  • FIG. 1 shows a cross-sectional view of the thrust roller bearing of this embodiment.
  • the thrust roller bearing 1 includes an annular inner ring 2 that is one of the race rings, an annular outer ring 3 that is the other race ring disposed concentrically with the inner ring 2, an annular cage 10, and rollers 4. Is provided.
  • the inner ring 2 has an L-shaped cross section having a flat track plate portion 2a and a cylindrical portion 2b extending from the inner periphery of the track plate portion 2a.
  • the outer ring 3 has an inverted L-shaped cross section including a flat plate-like track plate portion 3a facing the track plate portion 2a of the inner ring 2 and a cylindrical portion 3b extending from the outer peripheral edge of the track plate portion 3a to the inner ring 2 side. ing. Between the raceway plate portions 2 a and 3 a of the inner ring 2 and the outer ring 3, the rollers 4 held by the cage 10 are interposed. The roller 4 is prevented from falling off the cage 10 as will be described later, and the cage 10 and each roller 4 constitute a roller 20 with a cage.
  • the inner ring 2 and the outer ring 3 are provided with engaging projections 2ba and 3ba projecting toward the roller arrangement portion at a plurality of locations in the circumferential direction at the tips of the cylindrical portions 2b and 3b.
  • engaging 2ba and 3ba with the cage 10 By engaging 2ba and 3ba with the cage 10, the three-way integral thrust bearing 1 in which the roller with cage 20 and the inner and outer rings 2 and 3 are not separated is formed.
  • the inner ring 2 and the outer ring 3 are supported on the opposing surfaces of a pair of bearing ring support members 5 and 6 that rotate eccentrically with each other.
  • bearing ring support member 5 is fixed, and the other bearing ring support member 6 performs an eccentric rotation in which the center O2 is eccentric by an eccentric amount e with respect to the rotation center O1.
  • bearing ring support members 5 and 6 include a fixed scroll member and an eccentric rotation scroll member in a scroll pump.
  • FIG. 2 is an enlarged cross-sectional view of a portion where the pocket 13 is formed in the cage 10
  • FIG. 3 is a cross-sectional view of the cage 10 holding the rollers 4.
  • the cage 10 is composed of at least an annular first cage component plate 11 and a second cage component plate 12 that are axially overlapped with each other, and each roller 13 is inserted into each pocket 13 provided at a plurality of locations in the circumferential direction. Is retained.
  • the first cage component plate 11 has a cross-sectional shape including an inner diameter side flat portion 11a, an outer diameter side flat portion 11b, a central flat portion 11c, an inner diameter side continuous portion 11d, and an outer diameter side continuous portion 11e.
  • the inner diameter side flat portion 11a and the outer diameter side flat portion 11b are flat plate portions that are located on the inner diameter side and the outer diameter side, respectively, and that face in the axial direction.
  • the central flat part 11c is a flat plate-like part located in the middle of the radial direction with respect to the inner diameter side flat part 11a and the outer diameter side flat part 11b and being offset in the axial direction.
  • the inner diameter side continuous portion 11d is an inclined portion that continues from the outer peripheral edge of the inner diameter side flat portion 11a to the inner peripheral edge of the central flat portion 11c.
  • the outer diameter side continuous portion 11e is an inclined portion that continues from the outer peripheral edge of the central flat portion 11c to the inner peripheral edge of the outer flat side portion 11b.
  • the second cage component plate 12 has a cross-sectional shape including a flat plate portion 12a, an inner diameter side folded portion 12b, and an outer diameter side folded portion 12c.
  • the flat plate portion 12a is a surface opposite to the biasing direction of the central flat portion 11c of the first retainer constituting plate 11, and extends over the inner diameter side flat portion 11a and the outer diameter side flat portion 11b of the first retainer constituting plate 11. It is an overlapping part.
  • the inner diameter side folded portion 12b is a portion having a shape folded from the inner peripheral edge of the flat plate portion 12a.
  • the outer diameter side folded portion 12c is a portion having a shape folded from the outer peripheral edge of the flat plate portion 12a.
  • the inner diameter side flat portion 11a of the first cage constituting plate 11 is sandwiched between the inner diameter side folded portion 12b and the flat plate portion 12a. Further, the outer diameter side flat portion 11b of the first cage constituting plate 11 is sandwiched between the outer diameter side folded portion 12c and the flat plate portion 12a.
  • the corners of the inner diameter side folded portion 12b and the outer diameter side folded portion 12c are arcuate, but the entire inner diameter side folded portion 12b and outer diameter side folded portion 12c are semicircular as shown in FIG. 7, for example. You may make it become.
  • the first cage component plate 11 and the second cage component plate 12 are heat-treated products of steel plates, and the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 are not yet formed. It is a portion formed by caulking in a heat treatment state.
  • the rollers 4 are incorporated into the cage 10 that has been heat-treated in this manner.
  • FIG. 6 shows a cross-sectional view of the cage 10 holding the rollers 4 in the circumferential direction of the cage.
  • the pockets 13 of the cage 10 that holds the rollers 4 are formed in a pocket hole 14 formed by stamping the first cage component plate 11 and the second cage component plate 12. It consists of pocket holes 15 formed by stamping.
  • the pocket holes 14 and 15 of the first and second cage constituting plates 11 and 12 are formed by punching by press working using a punching die (not shown).
  • the processed surface is from the insertion side of the press die, the drooping portion a, the shearing surface portion b, the fracture surface portion c, and the return portion d. Occurs.
  • the pocket holes 14 and 15 are punched from the overlapping surface side to the non-overlapping surface side so that the return portions d are on the non-overlapping surface side.
  • the roller 4 forms the first cage.
  • a roller drop prevention portion 14 a that prevents the plate 11 from falling off is formed in the pocket hole 14 so as to protrude.
  • FIG. 4 shows a plan view of the pocket 13 seen from the direction of arrow A in FIG. 2
  • FIG. 5 shows a plan view of the pocket 13 seen from the direction of arrow B in FIG.
  • the width dimension L2 in the cage radial direction of the pocket hole 15 of the second cage component plate 12 constituting the pocket 13 is larger than the width dimension L1 in the cage radial direction of the pocket hole 14 of the first cage component plate 11.
  • the width dimension P1 in the cage circumferential direction of the pocket hole 14 of the first cage component plate 11 is larger than the width dimension P2 in the cage circumferential direction of the pocket hole 15 of the second cage component plate 12.
  • an oil passage port 15a that is a portion in which the width of the pocket hole 15 in the cage circumferential direction is locally increased may be provided. Further, the oil passage port 15a may be plural as shown in FIG. Thus, by providing the oil passage port 15a at the edge of the pocket hole 15 along the radial direction of the cage, the oil permeability can be improved.
  • a three-position integral type thrust roller bearing 1 including the cage 10 holding the roller 4, the inner ring 2, and the outer ring 3 is configured.
  • a cage and roller type thrust roller bearing may be configured only by the held cage 10, that is, by only the roller with cage 20.
  • both members 7, 8 are arranged such that a pair of mating members 7, 8 that are arranged opposite to each other in the axial direction and rotate relative to each other become rolling surfaces that the rollers 4 contact.
  • the cage 10 is disposed between them.
  • the second cage component plate 12 is formed in a flat shape, and the first cage component plate 11 is held by the inner diameter side folded portion 12b and the outer diameter side folded portion 12c. Therefore, the stress on the bent first retainer constituting plate 11 is reduced with respect to the load in the radial direction. That is, since the second cage component plate 12 does not have a bent portion like the first cage component plate 11, it is strong against a radial force. This strong second cage component plate 12 can reduce the stress on the bent portion of the first cage component plate 11, thereby avoiding a short life of the cage.
  • the thrust roller bearing 1 with a bearing ring configured as shown in FIG. 1 it is sandwiched between the cylindrical portions 2 b and 3 b of the inner and outer rings 2 and 3 under a rotational condition with a unit eccentric amount larger than the radial clearance inside the bearing.
  • a radial load is applied to the cage 10.
  • the stress on the bent portion of the cage 10 can be reduced without increasing the size of the bearing. Can be prevented.
  • the bent portion of the first cage constituting plate 11 is not a complicated shape like the W-type cage 40A in the conventional example shown in FIG. 12, for example, and a plurality of steps are required for bending by press. Since the bending step is small, the bending thickness is hardly reduced with respect to the original thickness (90% of the thickness before pressing) as illustrated in FIG. more than). As a result, the stress on the bent portion can be further reduced.
  • box type cage 40 and the W type cage 40A in the conventional thrust roller bearing illustrated in FIGS. 11 and 12 have a substantially rectangular cross section, whereas the cross section of the cage 10 in the thrust roller bearing 1 is shown. Since it has a substantially triangular shape, sufficient oil permeability can be secured.
  • the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 can be formed into an arcuate curved surface as shown in FIG. 2 and FIG.
  • the thrust roller bearing 1 When the thrust roller bearing 1 is configured, the flowability of the lubricant into the contact surface between the cage 10 and the inner and outer rings 2 and 3 is improved. As shown by the phantom line in FIG. 2, even when the thrust roller bearing is configured only by the cage 10 that holds the roller 4, The inflow property of the lubricant to the contact surface is improved.
  • the three-piece integrated thrust roller bearing 1 is configured as shown in FIG. 1 by making the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 into an arcuate curved surface
  • the frictional resistance is reduced by reducing the contact area between the inner and outer diameter surfaces of the cage 10 and the inner and outer rings 2 and 3, and the torque can be reduced.
  • FIG. 2 even when a thrust roller bearing is configured by only the cage 10 holding the roller 4, the contact area between the cage 10 and the guide portions 7a and 8a of the mating members 7 and 8 serving as rolling surfaces is reduced. By reducing the frictional resistance, the torque can be reduced.
  • the three-piece integrated thrust roller bearing 1 is configured as shown in FIG. 1 by making the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 into an arcuate curved surface,
  • the built-in force in the engagement utilizing the elastic displacement of the cage 10 with the inner and outer rings 2, 3 can be reduced, and deformation and cracking can be prevented.
  • the structure of the cage 10 can expose most of the surface of the roller 4 from the cage 10 as compared with the conventional box-type cage, so that the cooling effect of the roller contact portion is increased.
  • the oil permeability and the lubrication performance such as the cooling effect of the contact portion can also prevent the life from being reduced due to wear or heat generation even under severe conditions such as lean lubrication.
  • the 1st and 2nd cage component plates 11 and 12 of the cage 10 are made of heat-treated products of steel plates, and the inner diameter side folded portion 12b and the outer diameter side of the second cage component plate 12 are used.
  • the folded portion 12c is a portion formed by crimping in an unheated state (uncured state)
  • heat treatment is performed after caulking, a wide range of wear resistance technologies such as carburizing and quenching, hardening layer upgrade, and surface treatment can be adopted as heat treatment, expanding the range of functions, costs, and productivity.
  • the crimping process plastic processing
  • the processing time by the press crimping can be shortened.
  • the cage 4 is secured while securing an appropriate gap between the roller 4 and the pocket 13 of the cage 10 with the roller 4 being sandwiched. It is not necessary to perform 10 caulking, so that high component accuracy and assembly accuracy are not required, and an increase in assembly cost can be suppressed.
  • the pocket 13 of the cage 10 is composed of pocket holes 14 and 15 formed by stamping the first and second cage component plates 11 and 12, and each of these pocket holes. Nos. 14 and 15 are not affected by the return part due to shearing, because the return parts caused by shearing by punching are pressed from the side where the rollers 4 come into contact with each other so that the return parts are non-overlapping surfaces. Pocket space can be obtained, and the behavior of the cage 10 can be stabilized.
  • the width dimension L2 in the cage radial direction of the pocket hole 15 of the second cage component plate 12 constituting the pocket 13 of the cage 10 is set to the pocket hole of the first cage component plate 11. 14 is longer than the width dimension L1 in the radial direction of the cage, so that a large amount of lubrication to the end face of the roller 4 can be secured.
  • the cage 10 has a structure that receives the end surface of the roller 4 at the end surface along the circumferential direction of the cage of the pocket hole 14 of the first retainer constituting plate 11 at a position close to the axis O of the roller 4. Therefore, the inclination of the roller 4 can be suppressed, and even a short roller can be held.
  • FIG. 10 shows a second embodiment of the present invention.
  • the thrust roller bearing 1 of this embodiment is a three-piece integral type thrust roller bearing 1 shown in FIG. 1, and an outer diameter side gap g1 that is a gap between the outer peripheral surface of the cage 10 and the cylindrical portion 3b of the outer ring 3.
  • at least one of the inner diameter side gap g2 that is a gap between the inner peripheral surface of the cage 10 and the cylindrical portion 2b of the inner ring 2 is used as an eccentricity amount e of the pair of bearing ring support members 5 and 6. Is larger than Other configurations are the same as those of the first embodiment of FIG.
  • a three-piece integrated thrust roller bearing having inner and outer rings 2 and 3 is sandwiched between the cylindrical portions 2b and 3b of the inner and outer rings 2 and 3 under a rotational condition with a unit eccentricity e larger than the radial clearance inside the bearing.
  • a radial load acts on the cage 10.
  • the cage 10 since the radial clearance in the bearing is larger than the unit eccentric amount (the eccentric amount e of the pair of bearing ring support members 5 and 6), the cage 10 has the inner and outer rings 2 and 3 in the above configuration. It is possible to prevent occurrence of a radial load on the cage 10 due to eccentricity without being sandwiched between the cylindrical portions 2b and 3b.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Cette invention se rapporte à une butée à rouleaux, qui permet d'empêcher les influences des rotations excentriques et permet de retenir l'écoulement d'huile et de maintenir la performance de refroidissement d'une partie de contact de rouleau, et à un dispositif de retenue destiné à la butée à rouleaux. La butée à rouleaux comprend un dispositif de retenue (10) comprenant une première et une deuxième plaque constitutive du dispositif de retenue (11 et 12) et des rouleaux (4) sont retenus dans des poches (13) agencées dans la direction circonférentielle du dispositif de retenue (10). La première plaque constitutive du dispositif de retenue (11) a une forme en coupe comprenant des parties plates (11a et 11b) de côtés radialement intérieur et extérieur, une partie plate centrale (11c) axialement décalée par rapport aux parties plates individuelles (11a et 11b), et des parties continues (11d et 11e) s'étendant des parties plates individuelles (11a et 11b) à la partie plate centrale (11c). La deuxième plaque constitutive du dispositif de retenue (12) comprend une partie de plaque (12a) chevauchant les parties plates individuelles (11a et 11b), et des parties pliées (12b et 12c) repliées à partir des côtés radialement intérieur et extérieur de la partie de plaque (12a). Les parties plates individuelles (11a et 11b) de la première plaque constitutive du dispositif de retenue (11) sont intercalées entre les parties pliées individuelles (12b et 12c) et la partie de plaque (12a).
PCT/JP2009/000007 2008-01-10 2009-01-06 Butée à rouleaux, et dispositif de retenue associé WO2009087957A1 (fr)

Applications Claiming Priority (2)

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JP2008002767A JP2009162360A (ja) 2008-01-10 2008-01-10 スラストころ軸受およびその保持器
JP2008-002767 2008-01-10

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WO2009087957A1 true WO2009087957A1 (fr) 2009-07-16

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Cited By (2)

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WO2009127191A1 (fr) * 2008-04-15 2009-10-22 Schaeffler Kg Cage pour palier à roulement
WO2019089058A1 (fr) * 2017-11-06 2019-05-09 Koyo Bearings North America Llc Cage de maintien de rouleau en deux parties pour une butée à rouleaux

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Publication number Priority date Publication date Assignee Title
JP5955192B2 (ja) * 2012-10-10 2016-07-20 Ntn株式会社 スラスト軸受用保持器および保持器付きころ、ならびに、スラスト軸受

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JPS63219914A (ja) * 1987-03-09 1988-09-13 Ntn Toyo Bearing Co Ltd スラストころ軸受用保持器の製造方法
JP2004218655A (ja) * 2003-01-09 2004-08-05 Ntn Corp 無段変速機用の支持構造およびその製造方法
JP2007100775A (ja) * 2005-10-03 2007-04-19 Nsk Ltd スラスト円筒ころ軸受

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JPS63219914A (ja) * 1987-03-09 1988-09-13 Ntn Toyo Bearing Co Ltd スラストころ軸受用保持器の製造方法
JP2004218655A (ja) * 2003-01-09 2004-08-05 Ntn Corp 無段変速機用の支持構造およびその製造方法
JP2007100775A (ja) * 2005-10-03 2007-04-19 Nsk Ltd スラスト円筒ころ軸受

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009127191A1 (fr) * 2008-04-15 2009-10-22 Schaeffler Kg Cage pour palier à roulement
WO2019089058A1 (fr) * 2017-11-06 2019-05-09 Koyo Bearings North America Llc Cage de maintien de rouleau en deux parties pour une butée à rouleaux
CN111492147A (zh) * 2017-11-06 2020-08-04 光洋轴承北美有限责任公司 用于滚子推力轴承的两件式滚子保持架
US11353060B2 (en) 2017-11-06 2022-06-07 Koyo Bearings North America Llc Two-piece roller retainer cage for a roller thrust bearing
US11732754B2 (en) 2017-11-06 2023-08-22 Jtekt Bearings North America Llc Two-piece roller retainer cage for a roller thrust bearing

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