WO2012070642A1 - ラジアルニードル軸受用スペーサ - Google Patents
ラジアルニードル軸受用スペーサ Download PDFInfo
- Publication number
- WO2012070642A1 WO2012070642A1 PCT/JP2011/077171 JP2011077171W WO2012070642A1 WO 2012070642 A1 WO2012070642 A1 WO 2012070642A1 JP 2011077171 W JP2011077171 W JP 2011077171W WO 2012070642 A1 WO2012070642 A1 WO 2012070642A1
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- WO
- WIPO (PCT)
- Prior art keywords
- radial
- circumferential
- needle bearing
- rim
- spacer
- Prior art date
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Classifications
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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
- 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
- F16C19/24—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 radial load mainly
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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
- 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
- F16C19/44—Needle bearings
- F16C19/48—Needle bearings with two or more rows of needles
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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
- F16C33/37—Loose spacing bodies
-
- 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
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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
- F16C33/48—Cages for rollers or needles for multiple rows of rollers or needles
- F16C33/485—Cages for rollers or needles for multiple rows of rollers or needles with two or more juxtaposed cages joined together or interacting with each other
-
- 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
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/664—Retaining the liquid in or near the bearing
- F16C33/6651—Retaining the liquid in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
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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
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
-
- 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
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
- F16C19/463—Needle bearings with one row or needles consisting of needle rollers held in a cage, i.e. subunit without race rings
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/085—Bearings for orbital gears
Definitions
- This invention relates to the improvement of the spacer arrange
- a rotational support device for a planetary gear of an automobile transmission uses a radial needle bearing to rotatably support the planetary gear around a planetary shaft supported by a carrier.
- the device is in a state where a moment in a direction in which the central axes of these members are inclined is applied between the planetary gear which is the outer diameter side member provided with the outer ring raceway and the planetary shaft which is the inner diameter side member provided with the inner ring raceway. It is driven by.
- a double-row radial needle bearing is used in which a plurality of needles are arranged at two positions spaced apart in the axial direction to increase the rigidity against the moment.
- FIG. 16 shows a planetary gear rotation support device 1 constituting an automatic transmission for an automobile as an example of a known rotation support device incorporating a double-row radial needle bearing having a spacer.
- the rotation support device 1 rotates a planetary gear 4, which is an outer diameter side member, around a middle portion of a planetary shaft 3, which is an inner diameter side member supported at both ends by a carrier 2, by a double row radial needle bearing 5. Supports freely.
- the planetary gear 4 is a helical gear and meshes with a sun gear and a ring gear (both not shown) in a state where an automatic transmission for an automobile is assembled. Therefore, when the automatic transmission for an automobile is operated, an axial load is applied to the planetary gear 4 in addition to the radial load. As a result, the planetary gear 4 is connected between the planetary gear 4 and the planetary shaft 3 as described above. In addition, a moment in a direction in which these central axes are inclined is applied.
- the double-row radial needle bearing 5 is composed of a pair of radial needle bearings 6 and spacers 7.
- each radial needle bearing 6 includes a plurality of needles 8 and a substantially cylindrical retainer 9 that holds the needles 8 in a rollable manner.
- the rolling surfaces of these needles 8 are respectively rolled into a cylindrical inner ring raceway 10 provided on the outer peripheral surface of the planetary shaft 3 and a cylindrical outer ring raceway 11 provided on the inner peripheral surface of the planetary gear 4.
- the spacer 7 is arrange
- a so-called all-needle type double-row radial needle bearing in which a cage is omitted is also known.
- one end surface in the axial direction of the needle 8 in each row is directly opposed to both end surfaces in the axial direction of the spacer 7.
- the spacer 7 secures the distance between the axes of the radial needle bearings 6 arranged in a double row, so that the rigidity of the double row radial needle bearing 5 with respect to the moment is secured.
- the lubricating oil is supplied to both the radial needle bearings 6 through the oil supply passage 15 provided in the planetary shaft 3.
- a spacer 7 having a structure as shown in FIG. 17 is known as a spacer having such a function.
- the spacer 7 includes a pair of rim portions 12 and a plurality of column portions 13. These rim portions 12 are each annular and are arranged concentrically with respect to the axial direction. Further, these column portions 13 are provided at a plurality of locations in the circumferential direction between both rim portions 12 so as to connect the rim portions 12 to each other.
- a portion surrounded by each of the rim portion 12 and the column portion 13 adjacent in the circumferential direction is a through-hole portion (pocket) 14 that allows the inner and outer peripheral surfaces of the spacer 7 to communicate with each other.
- each through-hole portion 14 reduces the weight of the spacer 7 to reduce the inertial mass, and reduce the centrifugal force acting on the spacer 7 as the planetary shaft 3 revolves, whereby the planetary shaft 3 bends. Plays a function to suppress. Further, each through-hole portion 14 improves the performance of the rotation support device 1 based on the stabilization of the supply of lubricating oil to the rolling contact portions of both needle bearings 6 by securing the lubricating oil flow path, and further the spacer 7. It plays the role of cost reduction by saving material.
- the terms axial direction, radial direction, and circumferential direction mean the axial direction, radial direction, and circumferential direction of the spacer, respectively.
- each of these rubbing portions has an oil film of lubricating oil
- the shear resistance acting on the oil film is reduced by the rotational resistance of the spacer 7. Occupies the majority.
- Such shear resistance increases as the area of the spacer 7 and the adjacent member such as the planetary gear 4, the retainer 9, or the needle 8 abuts or is in close proximity to each other (opposite area) increases.
- Friction resistance based on relative displacement between the spacer 7 and the member adjacent to the spacer 7 causes an increase in dynamic torque (generation of torque loss) of the rotation support device 1, and the rotation support device 1 is incorporated.
- it causes the performance of rotating machinery such as an automatic transmission for automobiles to deteriorate. That is, there are various factors that increase the dynamic torque of the rotation support device 1, such as the rolling resistance and frictional resistance of the radial needle bearing 6 and the stirring resistance of the lubricating oil. It can be said that the frictional resistance including the shearing resistance generated in the above and the stirring resistance of the lubricating oil accompanying the rotation of the spacer 7 are so large that they cannot be ignored. Therefore, in order to improve the performance of the rotary machine device in which the rotation support device 1 is incorporated, it is desired to keep the resistance related to the spacer 7 low.
- the present invention reduces the sliding resistance of a frictional portion between a radial needle bearing spacer and a mating member adjacent to the spacer, and a double row radial in which the spacer is incorporated.
- An object of the present invention is to reduce the rotational resistance (dynamic torque) of the needle bearing, and to reduce power loss in a rotary machine device such as an automatic transmission for automobiles in which the double-row radial needle bearing is incorporated.
- the present invention provides a double-row radial needle bearing in which the area is not excessive and an appropriate amount of oil film is present in a rubbing portion with an adjacent mating member, and wear of these rubbing portions is suppressed.
- An object of the present invention is to provide a spacer for a radial needle bearing that can keep the dynamic torque of the shaft low.
- the radial needle bearing spacer is basically composed of a pair of rim portions that are annular in shape and arranged concentrically with each other in the axial direction, and a plurality of circumferential rim portions between the rim portions.
- a plurality of pillars that connect these rim parts to each other at a location, a cylindrical inner ring raceway provided on the outer peripheral surface of the inner diameter side member, and a cylinder provided on the inner peripheral surface of the outer diameter side member
- a pair of radial needle bearings provided in a state separated from each other in the axial direction between the outer ring raceway.
- a through-hole part that connects the outer peripheral surface and the inner peripheral surface of the spacer is formed between the pillar parts adjacent in the circumferential direction.
- the radial needle bearing spacer according to the present invention is provided on the outer side surface in the radial direction and / or circumferential direction of the column part and / or on the outer side surface in the radial direction and / or axial direction of the rim part. Or a recessed portion that is recessed in a direction away from a mating member adjacent to the rim portion.
- a concave portion recessed in a direction away from the counterpart member is formed by a circumferential concave portion provided on a circumferential outer surface of the column portion and recessed inward in the circumferential direction.
- the circumferential width dimension of the portion of the portion where the circumferential recess is formed is made smaller than the circumferential width direction of the through-hole portion formed between the column portions adjacent in the circumferential direction.
- the circumferential recess can be formed on one or both of the circumferential outer surfaces of the column part, and can also be formed on a part or all of the column part in the axial direction. When it is provided on both the outer circumferential surfaces of the column part, it is preferably provided at a position where they are born. Further, a plurality of the circumferential recesses can be formed in the axial direction of the column part.
- the number of the pillar portions is 3 to 6, and the area of the outer peripheral surface of the through-hole portion formed between the pillar portions adjacent in the circumferential direction is equal to the circumferential outer surface of the pillar portion.
- the recessed part recessed in the direction away from the said counterpart member so that it may become larger than an area can also be comprised by the enlarged part of the said through-hole part.
- the number of the pillars is four or six.
- the column parts adjacent to each other in the circumferential direction are arranged so as to be inclined with respect to the axial direction so as to face opposite directions.
- the concave portion recessed in the direction away from the counterpart member is reduced, the radial thickness of the column portion is reduced, and each outer surface of the column portion is set to be smaller than the outer peripheral surface of the rim portion. It can be formed by being recessed radially inward.
- the recess recessed in the direction away from the mating member may be constituted by an axial recess recessed inward in the axial direction provided on the axially outer surface of the rim portion.
- the axial concave portion can be constituted by a partially conical convex inclined surface portion formed in the outer half portion of the rim portion.
- the axial concave portion may be constituted by a plurality of concave portions formed intermittently in the circumferential direction of the rim portion and over the radial direction.
- the column portion is continuously connected by a plurality of rim elements arranged in a partial arc shape and shifted in phase in the circumferential direction by a half pitch, and the axial recess is adjacent to the circumferential direction. It can also be constituted by discontinuous portions between rim elements.
- the axial recess may be configured by an annular recess formed over the entire circumference in the radial intermediate portion of the axially outer side surface of the rim portion.
- the axial recess may be constituted by a plurality of circular recesses formed on the respective axially outer surfaces of the rim portion.
- the concave portion recessed in the direction away from the counterpart member may be formed by a bottomed radial concave portion provided on the radially outer surface of the column portion and recessed radially inward. it can. In addition, it is not prevented that such a radial direction recessed part is comprised also in the outer peripheral surface of the said rim
- the radial recess can be formed by positioning a portion surrounding the radial recess over the entire circumference on the outer side in the radial direction with respect to these radial recesses. More specifically, the radial recesses are formed on the radially outer surfaces of the column portions in the axial direction, and both circumferential ends of the radial recesses are arranged at both circumferential ends of the column portions. It is also possible to configure such that both ends in the axial direction of these radial recesses are partitioned by the rim portion by the edge portion.
- the radial recess may be constituted by a plurality of circular recesses formed on each radially outer surface of the column portion.
- the present invention it is possible to reduce the area (opposed area) where the radial needle bearing spacer and the mating member abut or face each other and reduce the rotational resistance (friction resistance including shear resistance) of the spacer. It becomes. Therefore, by providing the radial needle bearing spacer of the present invention, it is possible to reduce torque loss during operation of the rotary support device incorporating the double row radial needle bearing. Further, the radial needle bearing spacer can be reduced in weight and cost.
- the lubrication state between the axial end surface of the radial needle bearing spacer and the axial end surface of the cage or needle is also improved. Can be good.
- FIG. 1 is a perspective view showing a first example of a radial needle bearing spacer of the present invention.
- FIG. 2 is also a perspective view showing a second example.
- FIG. 3 is also a perspective view showing a third example.
- FIG. 4 is also a perspective view showing a fourth example.
- FIG. 5 is also a perspective view showing a fifth example.
- FIG. 6 is also a perspective view showing a sixth example.
- FIG. 7 is also a perspective view showing a seventh example.
- FIG. 8 is also a perspective view showing an eighth example.
- FIG. 9 is also a perspective view showing a ninth example.
- FIG. 10 is also a perspective view showing a tenth example.
- FIG. 11 is also a perspective view showing an eleventh example.
- FIG. 10 is also a perspective view showing a tenth example.
- FIG. 11 is also a perspective view showing an eleventh example.
- FIG. 10 is also a perspective view showing a tenth example.
- FIG. 12 is also a perspective view showing a twelfth example.
- FIG. 13 is also a perspective view showing a thirteenth example.
- FIG. 14 is also a perspective view showing a fourteenth example.
- 15 is a cross-sectional view taken along the line XX of FIG.
- FIG. 16 is sectional drawing which shows an example of the rotation support apparatus provided with the double row radial needle bearing incorporating the spacer used as the object of this invention.
- FIG. 17 is a perspective view showing an example of a conventional structure of a radial needle bearing spacer.
- the radial needle bearing spacer includes a cylindrical inner ring raceway 10 provided on the outer peripheral surface of the inner diameter side member 3 such as a planetary shaft, and an outer diameter side such as a planetary gear. Between the cylindrical outer ring raceway 11 provided on the inner peripheral surface of the member 4, a double-row radial needle bearing 5 is configured, and between a pair of radial needle bearings 6 provided in an axially separated state. Installed.
- the basic structure of the radial needle bearing spacer of the present invention is a pair of rim parts 12 each having an annular shape and arranged concentrically with respect to the axial direction.
- a plurality of column portions 13 provided in a state where these rim portions 12 are connected to each other are provided at a plurality of positions in the circumferential direction between the portions 12.
- a through-hole portion 14 that is surrounded by the rim portion 12 and the column portions 13 and communicates with the inner and outer peripheral surfaces of the spacer 7 is formed.
- the spacer 7 is incorporated in a space surrounded by the inner ring raceway 10, the outer ring raceway 11, and a pair of radial needle bearings 6, and the surface thereof is in contact with or in close proximity to the surface of the counterpart member. Thus, it rotates relative to this mating member. More specifically, the spacer 7 is used in a state where the outer peripheral surface of the spacer 7 is in sliding contact with or close to the outer ring raceway 11 and both axial end surfaces are in sliding contact with or close to the axial end surface of the cage 9 or the needle 8. . Since all of the present invention is based on the spacer 7 having the conventional structure shown in FIG. 17 and is improved, in the following description, the description of the improved part is mainly used and the part that is common to this conventional structure. With respect to, the explanation is omitted or simplified.
- the specifications (dimensions, material, surface roughness) of the spacer of the present invention are not particularly limited. For example, the following specifications can be adopted. "Size" Inner diameter: 5-30mm Radial thickness: 0.3-3.0mm Axial width: 2-30mm Circumferential width of the through hole: 1 mm or more Axial width of the radially outer surface of the rim: 1 mm
- Iron-based alloys As iron-based alloys, unheat-treated products such as cold rolled steel plate (SPCC), ultra-low carbon steel (AISI-1010), chromium molybdenum steel (SCM415), or carburizing or carbonitriding Those that have been heat-treated can be used. If these iron-based alloys are used, sufficient strength and rigidity are ensured even in a high temperature environment.
- -Synthetic resin As a synthetic resin, polyacetal resin, polyamide resin (nylon 46, nylon 66), polyphenylene sulfide resin (PPS), etc. can be used. If these synthetic resins are used, the spacer can be easily formed by injection molding, and not only the cost can be reduced, but also the effect of weight reduction can be obtained.
- the outer peripheral surface and the axial end surface that are in contact with or in close proximity to the mating member are preferably smooth surfaces in order to keep the frictional resistance during relative rotation with the mating member low.
- FIG. 1 shows a first example of an embodiment of the present invention.
- the feature of the spacer 7a of this example is that it is recessed inward in the radial direction as a recess recessed in a direction away from the outer diameter side member (planetary gear) 4 which is an adjacent counterpart member on the radially outer surface of the column portion 13a.
- the bottomed radial concave portion 22 is provided so that the relative rotation between the spacer 7a and the outer diameter side member 4 can be performed smoothly.
- the radially inner side surface of the column portion 13a and the inner peripheral surface of the pair of rim portions 12 are formed on a single cylindrical surface, and both circumferential ends and rims of the radially outer surface of these column portions 13a.
- the outer peripheral surface of the part 12 is positioned on a single cylindrical surface.
- the radial direction recessed part 22 is formed in the circumferential direction intermediate part in each of the pillar part 13a. In the case of this example, these radial direction recessed parts 22 are formed over the full length of the column part 13a.
- the cross-sectional shape (the contour of the bottom surface) of the radial recess 22 with respect to a virtual plane orthogonal to the central axis of the spacer 7a is the same composite arc over the entire length.
- This composite arc is composed of a concave arc at the center in the width direction with respect to the circumferential direction and a convex arc at both ends in the width direction with respect to the circumferential direction.
- the ends of these arcs are smoothly continuous, and the circumferential ends of the radial recess 22 and the outer peripheral surfaces of the circumferential ends of the column 13a are also smoothly continuous.
- both circumferential ends of the radial recess 22 are partitioned by both circumferential ends of the column portion 13a, and both axial ends of the radial recess 22 are partitioned by the rim portions 12 on both sides.
- the cross-sectional shape of the radial recess 22 may be a trapezoidal shape or a triangular shape.
- the spacer 7a of this example When the spacer 7a of this example is incorporated in the rotation support device 1 as shown in FIG. 16, the radially outer side surface of the column portion 13a and the outer ring raceway 11 of the outer diameter side member 4 abut or face each other.
- the radial recess 22 is recessed in a direction away from the outer ring raceway 11 of the outer diameter side member 4 which is a counterpart member, and the radial outer surface of the outer ring raceway 11 and the spacer 7a is equal to the area of the radial recess 22.
- the torque loss dynamic torque, frictional resistance
- the volume of the spacer 7a is reduced by the provision of the radial recess 22 and the spacer itself can be reduced in weight and cost.
- lubricating oil that is fed from the oil supply passage 15 to the inner diameter side of the outer ring raceway 11 is stored.
- the lubricating oil stored in the radial recess 22 enters between the outer peripheral surface of the spacer 7a and the outer ring raceway 11, and an oil film is formed on this portion. Form. For this reason, it is possible to prevent the occurrence of significant wear due to oil film breakage at the rubbing portion between the outer peripheral surface of the spacer 7a and the outer ring raceway 11.
- the spacer 7a and the outer ring raceway 11 are relatively relative to each other with respect to the lubricating oil stored in each radial recess 22. Large shear resistance does not occur even when rotating periodically. As a result, the dynamic torque can be kept low while suppressing the abrasion of the outer peripheral surface of the spacer 7a and the friction part of the outer ring raceway 11.
- the radial depth of the radial recess 22 can be reduced within a range that does not affect the rigidity and strength of the spacer 7a including the column portion 13a according to the size of the column portion 13a. It is desirable to ensure a sufficient width.
- the radial depth of the radial recess 22 depends on the specifications of the spacer 7a, it is preferably 0.5 mm or more, more preferably 1 mm or more. Note that the radial thickness of the central portion in the circumferential direction of the column portion 13a is reduced by increasing the radial depth of the radial concave portion 22, but the radial thickness at both ends in the circumferential direction is not reduced.
- the section modulus of the pillar portion 13a can be sufficiently secured, and the strength and rigidity of the spacer 7a including these pillar portions 13a can be sufficiently secured.
- the radial recess 22 instead of forming the radial recess 22 over the entire length of the column portion 13a, one can be provided in a part in the axial direction, or a plurality can be formed in series.
- FIG. 2 shows a second example of the embodiment of the present invention.
- the spacer 7b of this example in the same manner as in the first example, in addition to providing the bottomed radial concave portion 22 recessed radially inward on the radial outer surface of the column portion 13a, both end portions in the axial direction are provided.
- An annular recess 23 is formed over the entire circumference in the radial intermediate portion of the axially outer side surface of each of the provided pair of rim portions 12a. However, it is allowed to form the annular recess 23 in a discontinuous annular shape in the circumferential direction.
- the axial depth and width of the annular recess 23 are not affected by the rigidity and strength of the spacer 7b including the rim portion 12a according to the dimensions of the rim portion 12a. It is desirable to ensure.
- the radial thickness of the rim portion 12a is sufficiently large, a plurality of annular recesses can be formed concentrically on the outer side surface in the axial direction of the rim portion 12a.
- the configuration and operation of the other parts are the same as in the first example.
- FIG. 3 shows a third example of the embodiment of the present invention.
- a plurality of circular recesses 24, each of which is a radial recess are formed on each radially outer surface of each column portion 13b.
- a plurality of circular recesses 25, each of which is an axial recess are formed on each of the rim portions 12b on the outer surface in the axial direction of a pair of rim portions 12b formed at both axial ends of the spacer 7c.
- Each of these circular recesses 24 and 25 is a partially spherical recess.
- Such circular recesses 24 and 25 also function in the same manner as the axial recess 22 and the annular recess 23 in the second example, and suppress the wear of the rubbing portion between the spacer 7c and the counterpart member, and keep the dynamic torque low. It contributes to that.
- circular recesses 24 and 25 rectangular or elliptical recesses can be used.
- the circular recess 24 is within a range that does not affect the rigidity and strength of the spacer 7c including these portions. It is desirable to appropriately regulate the radial depth, diameter and number of the circular recess 25 and the axial depth, diameter and number of the circular recess 25.
- the configuration and operation of other parts are the same as in the second example.
- FIG. 4 shows a fourth example of the embodiment of the present invention.
- the spacer 7d of this example is such that the circumferential width of the axial intermediate portion of each of the plurality of column portions 13c arranged in parallel to each other is narrower than the circumferential width of both axial end portions, and adjacent columns. It is narrower than the circumferential width of the through-hole portion 14a existing between the portions 13c.
- circumferential recesses 16 that are recessed in the circumferential direction are formed in the axial intermediate portions of the circumferential outer surfaces on both sides of the column 13c, one on each circumferential outer surface on both sides of each column 13c.
- the circumferential width W of the column portion 13 is larger than the circumferential width S of the through hole portion 14, whereas the circumferential width w of the axial intermediate portion of these column portions 13c is It is made smaller than the circumferential direction width S of the axial direction intermediate part of the through-hole part 14a (w ⁇ S). Then, the area facing the outer ring raceway 11 is reduced on the outer peripheral surface of the spacer 7d by the radial opening area of the circumferential recess 16. That is, in the structure of this example, the circumferential recessed portion 16 constitutes a recessed portion that is recessed in a direction away from the outer diameter side member 4 that is the counterpart member.
- the circumferential width w of the intermediate portion in the axial direction of the column portion 13c is sufficiently smaller than the circumferential width W of the column portion 13 in the conventional structure shown in FIG.
- the circumferential width of both axial ends of the column portion 13c is substantially the same as the circumferential width W of the column portion in the conventional structure.
- the circumferential width of the both ends in the axial direction is made larger than the circumferential width W of the column portion 13 in the conventional structure. It may be a little wider.
- the shape and size (axial length, circumferential depth) of the circumferential recess 16 is as small as possible so that the area facing the outer ring raceway 11 is as small as possible in consideration of the strength required for the column portion 13c. In order to achieve this, appropriate regulation is made within the scope of the above-mentioned specifications.
- the structure shown in FIG. 4 is trapezoidal, but is not limited to the trapezoidal shape, and ensures the strength and rigidity of the column portion 13 c such as an arc shape, an ellipse shape, and a rectangular shape. Any shape can be adopted as long as possible.
- the circumferential recess 16 is formed on both sides in the circumferential direction of the column portion 13 c, but the circumferential recess 16 may be formed only on one side. In any case, the spacer 7d itself needs only to be able to prevent the pair of radial needle bearings 6 arranged apart from each other in the axial direction from approaching each other.
- the circumferential width S of the through hole 14a is provided in the spacer 7 of the conventional structure shown in FIG. It is made wider than the circumferential width s of the through-hole part 14 (S> s). And the area of the outer peripheral surface of the spacer 7d including the radial outer surface of the column part 13c is made smaller than the area of the outer peripheral surface of the spacer 7 of the conventional structure by the extent that the circumferential width S of the through-hole portion 14a is increased. is doing. Further, the frictional resistance including the shear resistance acting between the outer peripheral surface of the spacer 7d and the outer ring raceway 11 formed on the inner peripheral surface of the outer diameter side member 4 can be reduced by reducing the area of the outer peripheral surface.
- the dynamic torque of the double row radial needle bearing 5 incorporating the spacer 7d can be suppressed to be small, and the performance of the rotary machine device including the double row radial needle bearing unit 5 can be improved.
- the spacer 7d can be reduced in weight and cost by reducing the raw material, because the circumferential recess 16 is formed in the column portion 13c and the circumferential width w of the axial intermediate portion is narrowed.
- weight reduction contributes to suppression of the bending
- a radial recess is provided on the radially outer surface (particularly the axial intermediate portion) of the column portion 13d within a range in which the strength and rigidity of the column portion 13c can be secured, and Alternatively, an axial recess may be provided simultaneously on the axially outer surface of the rim portion 12.
- FIG. 5 shows a fifth example of the embodiment of the present invention.
- circumferential recesses 16a are formed on the outer circumferential surfaces of both ends in the axial direction of the column part 13d, and these column parts are formed.
- the area of the outer surface in the radial direction 13d, and hence the area of the outer peripheral surface of the spacer 7e, is made smaller than that of the conventional structure shown in FIG. That is, in the case of this example, the circumferential width of the intermediate portion in the axial direction of the column portion 13d is set to be approximately the same as the width W of the column portion 13 in the conventional structure shown in FIG. The circumferential width is made narrower than this.
- the shape and size (axial length, circumferential depth) of the circumferential recess 16a are set such that the area facing the outer ring raceway 11 is as small as possible in consideration of the strength required for the column portion 13d.
- the axial length of the circumferential recessed portion 16a is summed up for each circumferential outer surface of each column portion 13d, and within the above-described specifications, Regulate appropriately.
- the configuration and operation of other parts are the same as in the fourth example.
- FIG. 6 shows a sixth example of the embodiment of the present invention.
- the spacer 7f of this example has a structure in which the fourth example and the fifth example are combined. That is, in the case of the structure of this example, the circumferential recessed portion 16b is formed on the circumferential outer surface of the axial intermediate portion of each column portion 13e, and the circumferential recessed portion 16a is disposed on the circumferential outer surface of both axial ends. Forming. And the area of the radial direction outer side surface of the column part 13e and by extension, the area of the outer peripheral surface of the spacer 7f are made small by these recessed parts 16a and 16b.
- the shape and size (axial length, circumferential depth) of the circumferential recesses 16a and 16b are as small as possible so that the area facing the outer ring raceway 11 is as small as possible in consideration of the strength required for the column portion 13e.
- the axial lengths of the circumferential recesses 16a and 16b are totaled for each circumferential outer surface of each column portion 13e, Regulate appropriately.
- the configuration and operation of other parts are the same as in the fourth example.
- FIG. 7 shows a spacer 7g of the seventh example of the embodiment.
- the spacer 7g has circumferential recesses 16b at two positions on the outer circumferential surface of the intermediate portion in the axial direction of the column portion 13f. Then, the area of the radially outer surface of the column portion 13f, and hence the area of the outer peripheral surface of the spacer 7g, is reduced by the amount of these recesses 16b.
- the shape and size (axial length, circumferential depth) of the circumferential recess 16b are set so that the area facing the outer ring raceway 11 is as small as possible in consideration of the strength required for the column portion 13f.
- FIG. 8 shows an eighth example of the embodiment of the present invention.
- each of the pair of rim portions 12b each having an annular shape has a partially conical convex inclined surface portion 17 on the radially outer half portion of the axially outer side surface (the axial side surface opposite to each other).
- the radially outer half is formed as a recess recessed in a direction away from the counterpart member.
- the radially inner half of the outer surface in the axial direction of the rim portion 12b is a flat surface 18 that exists in a direction perpendicular to the central axis of the spacer 7h.
- each inclined surface portion 17 As much as possible within a range in which the strength and rigidity of the rim portion 12b can be secured reduces the area of the rubbing portion with the mating member. This is also preferable from the viewpoint of reducing the weight of the spacer 7h.
- the axial dimension is about 1/2 to 3/4 of the axial width of the rim part 12b
- the radial dimension is about 1/2 to 3/4 of the radial thickness of the rim part 12b. It is preferable to do.
- the inclination angle of the inclined surface portion 17 with respect to the central axis of the spacer 7h is set in a range larger than 0 ° and smaller than 90 °, but is preferably set in a range of 30 to 60 °.
- the flat surface 18 abuts or is close to the axial end surface of the cage 9 or the needle 8 constituting the pair of radial needle bearings 6.
- the area of the flat surface 18 is smaller than the area of the outer surface in the axial direction of the rim portion 12 having the conventional structure shown in FIG. Therefore, in the case of this example, the frictional resistance accompanying the relative rotation between the spacer 7h and the cage 9 or the needle 8 can be reduced.
- the opposing area between the outer peripheral surface of the rim portion 12b and the outer ring raceway 11 can be reduced, and the frictional resistance associated with the relative rotation between the spacer 7h and the outer diameter side member 4 can be reduced accordingly.
- the dynamic torque of the double row radial needle bearing 5 can be reduced.
- the volume of the spacer 7h can be reduced and the weight can be reduced by the amount of the inclined surface portion 17 formed.
- a convex arc surface that is continuous from the radially outer surface of the rim portion 21b to the flat surface 18 can be used instead of the inclined surface portion 17.
- the structure of this example can also be implemented in combination with the structures of the first to seventh examples. The configuration and operation of other parts are the same as in the fourth example.
- FIG. 9 shows a ninth example of the embodiment of the present invention.
- the spacer 7i of this example forms a plurality of axial recesses 19 by intermittently denting the axially outer surfaces of a pair of rim portions 12c each having an annular shape in the axial direction with respect to the circumferential direction.
- these axial recesses 19 have a substantially rectangular shape extending in the radial direction of each rim portion 12c, that is, penetrating from the inner periphery to the outer periphery of the outer surface in the axial direction.
- the axial recesses 19 are arranged at an equal pitch in the circumferential direction, but it is not always necessary to have an equal pitch.
- the size (circumferential width, axial depth) of the axial recess 19 is determined according to the size (diameter, radial thickness, axial width) of the rim portion 12c, for example, and the axial recess 19 is formed. In this state, setting as large as possible within a range that can ensure the strength and rigidity required for the rim portion 12c reduces the torque loss by reducing the area facing the mating surface, and the spacer 7i. This is preferable in terms of weight reduction.
- the circumferential width of the axial recesses 19 is set to about 1 to 2 times the circumferential width of the projections existing between the recesses 19 adjacent to each other in the circumferential direction. It is preferably set to about 1/3 to 2/3 of the axial width of the portion 12c.
- the shape of the axial recess 19 is not limited to the rectangular shape as shown in the figure, and various shapes such as a partial arc shape, an elliptical shape, and a triangular shape can be employed. Further, in this example, the axial recesses 19 and the column portions 13 are made to coincide with each other in terms of the circumferential phase. However, the phases of these recesses 19 and the column portions 13 are shifted by a half pitch. You may make the phase and the phase of the through-hole part 14 correspond. Furthermore, the number of the axial recesses 19 formed on the outer surface in the axial direction of the rim portion 12c may be different from the number of the column portions 13 (through hole portions 14). The structure of this example can also be implemented in combination with the structures of the first to eighth examples. The configuration and operation of other parts are the same as in the fourth example.
- FIG. 10 shows a spacer 7j of the tenth example of the embodiment of the present invention.
- the spacer 7j has a pair of rim portions 12d that are discontinuous in the circumferential direction. That is, the rim portion 12d has a plurality of (six in the illustrated example) rim elements 20 each having a partial arc shape, and the phase in the circumferential direction between the rim portions 12d is divided by a half pitch. They are shifted. Then, both end edges in the circumferential direction of the rim element 20 are made continuous by the column portions 13 to form a spacer 7j that is entirely cylindrical and has a crank shape when unfolded.
- the discontinuous portion 26 between the rim elements 20 adjacent in the circumferential direction becomes an axial concave portion formed intermittently and radially in the circumferential direction of the rim portion, and the counterpart. It becomes a recessed part dented in the direction away from a member (the outer ring track 11 of the outer diameter side member 4 and the axial end surface of the cage 9 or the needle 8).
- the discontinuous portion 26 is preferably formed at the same time as the spacer 7j is integrally formed by injection molding of synthetic resin from the viewpoint of saving material and facilitating processing.
- the spacer 7j is made of a metal material
- a part of the rim portion 12 constituting the spacer 7 having the conventional structure shown in FIG. 17 may be formed by scraping later.
- the outer circumferential surface and the axially outer surface of the rim portion 12d of the spacer 7j and the axial end surface of the outer ring raceway 11 and the cage 9 or each needle 8 are opposed to each other in the spacer 7j. Area to be reduced.
- the structure of this example can also be implemented in combination with the structures of the first to ninth examples. The configuration and operation of other parts are the same as in the fourth example.
- FIG. 11 shows a spacer 7k of an eleventh example according to the embodiment of the present invention.
- the spacer 7k has a smaller number of pillars 13 than the conventional structure shown in FIG. 17 and a larger circumferential pitch, and the opening of the through-hole part 14e existing between the neighboring pillars 13 in the circumferential direction.
- the area (area of the outer peripheral surface) is increased, and the area of the outer peripheral surface of the spacer 7k facing the outer ring raceway 11 is reduced. That is, in the conventional structure, the opening area of each through hole portion 14 is smaller than the area of the radially outer surface of each column portion 13 (the circumferential width s of the through hole portion 14 is the circumferential direction of the column portion 13).
- each through hole 14e is larger than the area of the radially outer surface of each column 13.
- the enlarged portions of both ends in the circumferential direction of the through hole portion 14e as compared with the through hole portion 14 of the conventional structure shown in FIG. 17 are the counterpart members (the outer ring track 11 of the outer diameter side member 4). It becomes a recessed part recessed in the direction away from.
- the number of the column portions 13 constituting the spacer 7k is required to be three or more, but it is preferable that the number is small as long as the strength and rigidity of the spacer 7k can be secured.
- the number is preferably 3-6.
- the circumferential width of each through hole portion 14e is preferably larger than the circumferential width of the column portion 13, but the circumferential width of the through hole portion 14e is more than twice the circumferential width of the column portion 13, Furthermore, it is preferable to secure three times or more.
- the upper limit of the circumferential width of the through-hole portion 14e is defined as a value that can ensure the required rigidity after the number of the column portions 13 is three or more. As long as this condition is satisfied, the circumferential width of the through-hole portion 14e is preferably as large as possible.
- the through holes 14e are preferably formed simultaneously with the spacer 7k by synthetic resin injection molding from the viewpoint of saving material and facilitating processing.
- the spacer 7k is made of a metal material
- the structure of this example can also be implemented in combination with the structures of the first to tenth examples. The configuration and operation of other parts are the same as in the fourth example.
- FIG. 12 shows a twelfth example of the embodiment of the present invention.
- the spacer 7 l in this example is an improvement of the structure of the spacer 7 k in the eleventh example, and has a structure in which a reinforcing rim portion 21 is added to the intermediate portion in the axial direction. That is, the reinforcing rim portion 21 is provided in a state in which the intermediate portions in the axial direction of the column portions 13 are connected so as to partition the wide through hole portion 14f in the axial direction.
- the reinforcing rim portion 21 has the same diameter as the pair of rim portions 12 provided at both ends in the axial direction and is concentric with the rim portions 12.
- FIG. 13 shows a tenth example of the embodiment of the present invention.
- the spacer 7m of this example even-numbered (six in the illustrated example) column portions 13g and 13h arranged between the pair of rim portions 12 are inclined with respect to the axial direction. The inclination direction is opposite to each other between the column portions 13g and 13h adjacent in the circumferential direction. In this way, by tilting these column portions 13g and 13h to make the structure of the spacer 7m a truss shape, the spacer 7m relating to the twisting and axial forces acting between the pair of rim portions 12 is obtained.
- the strength and rigidity are improved compared to the eleventh example. If the structures of the present example and the twelfth example are combined, the strength and rigidity of the spacer 7m can be further improved.
- the configuration and operation of the other parts are the same as in the eleventh example.
- [Fourteenth example of embodiment] 14 to 15 show a fourteenth example of the embodiment of the present invention.
- the thickness in the radial direction of the column portion 13i is made smaller than the spacer 7 having the conventional structure shown in FIG.
- the radially inner side surfaces of these column portions 13i and the inner peripheral surfaces of the pair of rim portions 12 are positioned on a single cylindrical surface.
- the entire radial outer surface of the column portion 13 i is recessed inward in the radial direction from the outer peripheral surface of the rim portion 12.
- the radially outer surface of the pillar portion 13i is a concave portion that is recessed in a direction away from the counterpart member.
- the thickness of the column portion 13i is smaller than the radial thickness of the rim portion 12 as much as possible to ensure the strength and rigidity of the spacer 7n. Is preferred.
- the radially outer surface of the column portion 13i is slightly recessed (for example, 0.5 mm or more, preferably 1 mm or more) from the outer peripheral surface of the rim portion 12. If this is not the case, an oil film is prevented from being formed between the outer ring raceway 11 and the outer peripheral surface of the spacer 7n, and the frictional resistance can be sufficiently reduced.
- the structure of this example is the same as that of the eighth to tenth examples from the viewpoint of reducing the frictional resistance with the cage 9 or the axial end face of the needle 8 and the structure of the eighth to tenth examples and the weight reduction. It can also be implemented in combination with the structure. Furthermore, from the viewpoint of suppressing the wear of the frictional portion with the cage 9 which is the mating surface or the axial end surface of the needle, it may be carried out in combination with the structure having the axial recess in the second example or the third example. it can. The configuration and operation of other parts are the same as in the fourth example.
- the spacer for a radial needle bearing of the present invention can be widely used for a double row radial needle bearing constituting a rotation support portion of various mechanical devices.
- the present invention is preferably applied to a double row radial needle bearing incorporated in a rotation support portion of a planetary gear constituting a planetary gear device of an automatic transmission for an automobile, but is not limited to this, and a rotation support portion of a planetary gear device of various mechanical devices.
- the present invention can also be applied to a double-row radial needle bearing used for a rotation support portion of a rotating member other than a planetary gear.
- Rotation support apparatus Carrier 3 Inner diameter side member (planetary axis) 4 Outer diameter side member (planetary gear) 5 Double-row radial needle bearing 6 Radial needle bearing 7, 7a-7n Spacer 8 Needle 9 Cage 10 Inner ring raceway 11 Outer ring raceway 12, 12a-12d Rim part 13, 13a-13i Column part 14, 14a-14h Through hole part 15 Oil supply passage 16, 16a, 16b Recessed portion 17 Inclined surface portion 18 Flat surface 19 Axial recessed portion 20 Rim element 21 Reinforcing rim portion 22 Radial recessed portion 23 Annular recessed portion 24 Circular recessed portion 25 Circular recessed portion 26 Discontinuous portion
Abstract
Description
「寸法」
内径: 5~30mm
径方向厚さ: 0.3~3.0mm
軸方向幅: 2~30mm
透孔部の周方向幅: 1mm以上
リム部の径方向外側面の軸方向幅: 1mm以上
・鉄系合金
鉄系合金としては、冷間圧延鋼板(SPCC)、超低炭素鋼(AISI-1010)、クロムモリブデン鋼(SCM415)などの未熱処理品、あるいは、これらに浸炭処理、浸炭窒化処理などの熱処理を施したものを使用できる。これらの鉄系合金を使用すれば、高温環境下でも十分な強度および剛性が確保される。
・合成樹脂
合成樹脂としては、ポリアセタール樹脂、ポリアミド樹脂(ナイロン46、ナイロン66)、ポリフェニレンサルファイド樹脂(PPS)などが使用可能である。これらの合成樹脂を使用すれば、スペーサを射出成形することにより容易に形成できて、低コスト化を図れるだけでなく、軽量化による効果が得られる。
スペーサの表面のうち、相手部材に当接もしくは近接対向する外周面および軸方向端面は、この相手部材との相対回転時の摩擦抵抗を低く抑えるために、平滑面とすることが好ましい。具体的には、少なくともこれらの外周面および軸方向端面を、それぞれ中心線平均粗さRaで、6.3μm以下とすることが好ましい。
図1は、本発明の実施の形態の第1例を示している。なお、本例のスペーサ7aの特徴は、柱部13aの径方向外側面に、隣接する相手部材である外径側部材(遊星歯車)4から離れる方向に凹んだ凹部として、径方向内側に凹んだ有底の径方向凹部22を設けて、スペーサ7aと、外径側部材4との相対回転を円滑に行わせる点にある。
図2は、本発明の実施の形態の第2例を示している。本例のスペーサ7bでは、第1例と同様に、柱部13aの径方向外側面に、径方向内側に凹んだ有底の径方向凹部22を設けたことに加えて、軸方向両端部に設けた1対のリム部12aのそれぞれの軸方向外側面の径方向中間部に、環状凹部23を、全周にわたって形成している。ただし、環状凹部23を周方向に関して不連続な欠円環状に形成することも許容される。このような環状凹部23を備えた本例のスペーサ7bを、図16に示すような回転支持装置1に組み込んだ場合、リム部12aの軸方向外側面と保持器9またはニードル8の軸方向端面とが近接対向する。また、この環状凹部23内には、給油通路15から外輪軌道11の内径側に送り込まれる潤滑油が貯溜される。
図3は、本発明の実施の形態の第3例を示している。本例のスペーサ7cの場合には、それぞれの柱部13bの径方向外側面に、それぞれが径方向凹部である円形凹部24を、これらの柱部13bごとに複数形成している。また、スペーサ7cの軸方向両端部に形成した1対のリム部12bの軸方向外側面に、それぞれが軸方向凹部である円形凹部25を、これらのリム部12bごとに複数形成している。これらの円形凹部24、25は、それぞれ部分球状の凹部である。このような円形凹部24、25も、第2例における軸方向凹部22および環状凹部23と同様に機能して、スペーサ7cと相手部材との擦れ合い部の摩耗を抑えつつ、動トルクを低く抑えることに寄与する。なお、これらの円形凹部24、25に代替して、矩形状、楕円形状の凹部とすることも可能である。
図4は、本発明の実施の形態の第4例を示している。本例のスペーサ7dは、互いに平行に配列された複数の柱部13cのそれぞれの軸方向中間部の周方向幅を、軸方向両端部の周方向幅に比べて狭くし、かつ、隣接する柱部13cの間に存在する透孔部14aの周方向幅よりも狭くしている。言い換えれば、柱部13cの両側の周方向外側面の軸方向中間部に、それぞれ周方向に凹んだ周方向凹部16を、それぞれの柱部13cの両側の周方向外側面に1箇所ずつ形成し、従来構造では、柱部13の周方向幅Wが、透孔部14の周方向幅Sよりも大きかったのに対して、これらの柱部13cの軸方向中間部の周方向幅wを、透孔部14aの軸方向中間部の周方向幅Sよりも小さくなるようにしている(w<S)。そして、これらの周方向凹部16の径方向開口面積分だけ、スペーサ7dの外周面で外輪軌道11との対向面積を小さくしている。すなわち、本例の構造では、周方向凹部16が、相手部材である外径側部材4から離れる方向に凹んだ凹部を構成する。
図5は、本発明の実施の形態の第5例を示している。本例のスペーサ7eの場合には、第4例のスペーサ7dとは逆に、柱部13dの軸方向両端部の周方向外側面に、それぞれ周方向凹部16aを形成して、これらの柱部13dの径方向外側面の面積、ひいてはスペーサ7eの外周面の面積を、図17に示した従来構造に比べて小さくしている。すなわち、本例の場合には、柱部13dの軸方向中間部の周方向幅を、図17に示した従来構造における柱部13の幅Wと同程度とし、柱部13dの軸方向両端部の周方向幅をこれよりも狭くしている。
図6は、本発明の実施の形態の第6例を示している。本例のスペーサ7fは、第4例と第5例とを組み合わせたような構造を有する。すなわち、本例の構造の場合には、それぞれの柱部13eの軸方向中間部の周方向外側面に周方向凹部16bを、軸方向両端部の周方向外側面に周方向凹部16aを、それぞれ形成している。そして、これらの凹部16a、16bの分だけ、柱部13eの径方向外側面の面積、ひいては、スペーサ7fの外周面の面積を小さくしている。周方向凹部16a、16bの形状および大きさ(軸方向長さ、周方向深さ)は、柱部13eに必要とされる強度などを考慮して、外輪軌道11との対向面積ができる限り小さくなるように、それぞれの柱部13eの周方向外側面ごとに、周方向凹部16a、16bの軸方向長さを合計するほかは、第4例と同様に、前述した諸元の範囲内で、適切に規制する。その他の部分の構成および作用は、第4例と同様である。
図7は、実施の形態の第7例のスペーサ7gを示している。このスペーサ7gは、柱部13fの軸方向中間部の周方向外側面のそれぞれの2箇所位置ずつに周方向凹部16bを形成している。そして、これらの凹部16bの分だけ、柱部13fの径方向外側面の面積、ひいては、スペーサ7gの外周面の面積を小さくしている。周方向凹部16bの形状および大きさ(軸方向長さ、周方向深さ)は、柱部13fに必要とされる強度などを考慮して、外輪軌道11との対向面積ができる限り小さくなるように、周方向凹部16bの軸方向長さをそれぞれの柱部13fの周方向外側面ごとに、2個分を合計するほかは、第4例と同様に、前述した諸元の範囲内で、適切に規制する。その他の部分の構成および作用は、第4例と同様である。
図8は、本発明の実施の形態の第8例を示している。本例のスペーサ7hは、それぞれが円環状である1対のリム部12bの軸方向外側面(互いに反対側の軸方向側面)の径方向外半部に、それぞれ部分円すい凸面状の傾斜面部17を形成して、この径方向外半部を、相手部材から離れる方向に凹んだ凹部としている。これに対して、リム部12bの軸方向外側面の径方向内半部は、スペーサ7hの中心軸に対し直角方向に存在する平坦面18としている。
図9は、本発明の実施の形態の第9例を示している。本例のスペーサ7iは、それぞれが円環状である1対のリム部12cの軸方向外側面を周方向に関して間欠的に軸方向に凹ませ、複数の軸方向凹部19を形成している。本例では、これらの軸方向凹部19を、それぞれのリム部12cの径方向にわたる、すなわち、軸方向外側面の内周縁から外周縁に貫通する、略矩形状としている。本例では、軸方向凹部19を周方向に関して等ピッチで配列しているが、必ずしも等ピッチである必要はない。
図10は、本発明の実施の形態の第10例のスペーサ7jを示している。このスペーサ7jは、1対のリム部12dを、それぞれ周方向に関して不連続な、欠円環状としている。すなわち、これらのリム部12dは、それぞれが部分円弧状である複数個ずつ(図示の例では6個ずつ)のリム素子20を、リム部12d同士の間で、周方向に関する位相を半ピッチ分ずらせて配置している。そして、リム素子20の周方向両端縁同士を、それぞれ柱部13により連続させて、全体が円筒状で、展開した状態での形状がクランク状となる、スペーサ7jとしている。本例の構造では、周方向に隣り合う、リム素子20の間の不連続部26が、リム部の周方向に間欠的に、かつ、径方向にわたって形成された軸方向凹部となり、かつ、相手部材(外径側部材4の外輪軌道11および保持器9またはニードル8の軸方向端面)から離れる方向に凹んだ凹部となる。
図11は、本発明の実施の形態の第11例のスペーサ7kを示している。このスペーサ7kは、図17に示した従来構造に対して柱部13の数を少なく、周方向ピッチを大きくして、周方向に隣り合う柱部13の間に存在する透孔部14eの開口面積(外周面の面積)を広くし、外輪軌道11と対向するスペーサ7kの外周面の面積を小さくしている。すなわち、従来構造では、それぞれの透孔部14の開口面積が、それぞれの柱部13の径方向外側面の面積よりも小さい(透孔部14の周方向幅sが、柱部13の周方向幅Wよりも小さい)のに対して、それぞれの透孔部14eの外周面の面積が、それぞれの柱部13の径方向外側面の面積よりも大きくなっている。本例の構造では、透孔部14eの周方向両端部で、図17に示した従来構造の透孔部14に比べて拡大された部分が、相手部材(外径側部材4の外輪軌道11)から離れる方向に凹んだ凹部となる。
図12は、本発明の実施の形態の第12例を示している。本例のスペーサ7lは、第11例のスペーサ7kの構造を改良したもので、軸方向中間部に補強用リム部21を追加した構造を有する。すなわち、幅広の透孔部14fを軸方向に仕切るように、柱部13の軸方向中間部同士を連結する状態で、補強用リム部21を設けている。この補強用リム部21は、軸方向両端部に設けた1対のリム部12と同径で、これらのリム部12と同心である。本例の場合、補強用リム部21を設けることにより、透孔部14fの周方向幅を十分に大きくしても、スペーサ7lの強度および剛性を十分に確保できるようにしている。その他の部分の構成および作用は、第11例と同様である。
図13は、本発明の実施の形態の第10例を示している。本例のスペーサ7mの場合には、1対のリム部12の間に配置した偶数本(図示の例では6本)の柱部13g、13hを、軸方向に対し傾斜させている。また、傾斜方向は、周方向に隣り合う柱部13g、13hの間で、互いに逆方向としている。このように、これらの柱部13g、13hを傾斜させて、スペーサ7mの構造をトラス状とすることにより、1対のリム部12の間に作用する捻り方向および軸方向の力に関する、スペーサ7mの強度および剛性を、第11例に比べて向上させている。なお、本例と第12例の構造を組み合わせれば、スペーサ7mの強度および剛性を、より一層向上させることができる。その他の部分の構成および作用は、第11例と同様である。
図14~図15は、本発明の実施の形態の第14例を示している。本例のスペーサ7nの場合、図17に示した従来構造のスペーサ7に対して、柱部13iの径方向厚さを小さくしている。また、これらの柱部13iの径方向内側面と、1対のリム部12の内周面とを単一円筒面上に位置させている。そして、柱部13iの径方向外側面の全体を、リム部12の外周面よりも径方向内方に凹ませている。本例の構造では、柱部13iの径方向外側面が、相手部材から離れる方向に凹んだ凹部となる。
2 キャリア
3 内径側部材(遊星軸)
4 外径側部材(遊星歯車)
5 複列ラジアルニードル軸受
6 ラジアルニードル軸受
7、7a~7n スペーサ
8 ニードル
9 保持器
10 内輪軌道
11 外輪軌道
12、12a~12d リム部
13、13a~13i 柱部
14、14a~14h 透孔部
15 給油通路
16、16a、16b 凹部
17 傾斜面部
18 平坦面
19 軸方向凹部
20 リム素子
21 補強用リム部
22 径方向凹部
23 環状凹部
24 円形凹部
25 円形凹部
26 不連続部
Claims (16)
- それぞれが円環状で、軸方向に離隔した状態で互いに同心に配置された1対のリム部と、これらのリム部の間の周方向複数箇所に、これらのリム部同士を連結する複数本の柱部とを備え、
内径側部材の外周面に設けられた円筒状の内輪軌道と、外径側部材の内周面に設けられた円筒状の外輪軌道との間に、軸方向に離隔した状態で設けられた1対のラジアルニードル軸受の間に設置される、
ラジアルニードル軸受用スペーサであって、
前記柱部の径方向および/または周方向の外側面に、および/または、前記リム部の径方向および/または軸方向の外側面に、前記柱部または前記リム部に隣接する相手部材から離れる方向に凹んだ凹部が形成されていることを特徴とする、
ラジアルニードル軸受用スペーサ。 - 前記相手部材から離れる方向に凹んだ凹部が、前記柱部の周方向外側面に設けられた、周方向内側に凹んだ周方向凹部からなり、前記柱部のこの周方向凹部が形成された部分の周方向幅寸法が、周方向に隣接する柱部間に形成される透孔部の周方向幅方向よりも小さくなっている、請求項1に記載のラジアルニードル軸受用スペーサ。
- 前記周方向凹部が、前記柱部の周方向外側面の両方の互いに整合する位置に設けられている、請求項2に記載のラジアルニードル軸受用スペーサ。
- 前記周方向凹部が、前記柱部の軸方向に複数設けられている、請求項2に記載のラジアルニードル軸受用スペーサ。
- 前記柱部の数を3~6本とし、周方向に隣接する柱部間に形成される透孔部の外周面の面積が、前記柱部の周方向外側面の面積よりも大きくなるようになっており、前記相手部材から離れる方向に凹んだ凹部が、前記透孔部のうちの拡大された部分からなる、請求項1に記載のラジアルニードル軸受用スペーサ。
- 前記柱部の数が4本または6本であり、周方向に隣接する柱部が、互いに逆方向を向くように、軸方向に対して傾斜して配置されている、請求項5に記載のラジアルニードル軸受用スペーサ。
- 前記相手部材から離れる方向に凹んだ凹部が、前記柱部の径方向厚さを小さくして、前記柱部のそれぞれの外側面を、前記リム部の外周面よりも径方向内側に凹ませることにより形成されている、請求項1に記載のラジアルニードル軸受用スペーサ。
- 前記相手部材から離れる方向に凹んだ凹部が、前記リム部の軸方向外側面に設けられた、軸方向内側に凹んだ軸方向凹部からなる、請求項1に記載したラジアルニードル軸受用スペーサ。
- 前記軸方向凹部が、前記リム部の外半部に形成された、部分円すい凸面状の傾斜面部からなる、請求項8に記載したラジアルニードル軸受用スペーサ。
- 前記軸方向凹部が、前記リム部の周方向に間欠的に、かつ、径方向にわたって、形成された複数の凹部からなる、請求項8に記載したラジアルニードル軸受用スペーサ。
- 前記柱部が、部分円弧状で、周方向に関する位相を半ピッチずつずらせて配置された、複数のリム素子により連続的に連結されており、前記軸方向凹部が、周方向に隣接する前記リム素子間の不連続部からなる、請求項8に記載したラジアルニードル軸受用スペーサ。
- 前記軸方向凹部が、前記リム部の軸方向外側面の径方向中間部に、全周にわたって形成された環状凹部である、請求項8に記載したラジアルニードル軸受用スペーサ。
- 前記軸方向凹部が、前記リム部のそれぞれの軸方向外側面に形成された複数の円形凹部からなる、請求項8に記載したラジアルニードル軸受用スペーサ。
- 前記相手部材から離れる方向に凹んだ凹部が、前記柱部の径方向外側面に設けられた、径方向内側に凹んだ有底の径方向凹部からなる、請求項1に記載のラジアルニードル軸受用スペーサ。
- 前記径方向凹部が、前記柱部のそれぞれの径方向外側面に、軸方向に形成されており、これらの径方向凹部の周方向両端部が前記柱部のそれぞれの周方向両端縁部により、これらの径方向凹部の軸方向両端部が前記リム部により、それぞれ仕切られている、請求項2に記載したラジアルニードル軸受用スペーサ。
- 前記径方向凹部が、前記柱部のそれぞれの径方向外側面に形成された複数の円形凹部からなる、請求項2に記載したラジアルニードル軸受用スペーサ。
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EP11826107.2A EP2660486A4 (en) | 2010-11-26 | 2011-11-25 | SPACER FOR RADIAL BEARING WITH NEEDLES |
US13/498,065 US20130004111A1 (en) | 2010-11-26 | 2011-11-25 | Spacer for Radial Needle Roller Bearing |
KR1020127007682A KR101389164B1 (ko) | 2010-11-26 | 2011-11-25 | 래디얼 니들 베어링용 스페이서 |
CN2011800034943A CN102639885A (zh) | 2010-11-26 | 2011-11-25 | 径向滚针轴承用隔离件 |
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JP2011246179A JP5821548B2 (ja) | 2011-11-10 | 2011-11-10 | ラジアルニードル軸受用スペーサ |
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Publication number | Priority date | Publication date | Assignee | Title |
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CN112240347A (zh) * | 2019-07-17 | 2021-01-19 | 斯凯孚公司 | 轴承保持架及其应用 |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013122257A (ja) * | 2011-12-09 | 2013-06-20 | Ntn Corp | ころ軸受 |
KR101302644B1 (ko) * | 2012-07-13 | 2013-09-03 | 한국원자력연구원 | 캠락용 이종재질 슬리브 |
DE102013212962A1 (de) * | 2013-07-03 | 2015-01-08 | Aktiebolaget Skf | Lagerkäfig für verlängerte Fettgebrauchsdauer |
US10556980B2 (en) * | 2014-03-03 | 2020-02-11 | University Of South Carolina | Poly alkyl (meth)acrylates grafted nanoparticles and their methods of manufacture and use |
DE102014219311A1 (de) * | 2014-09-24 | 2016-03-24 | Aktiebolaget Skf | Wälzlagerkäfig |
DE102015119584A1 (de) * | 2015-11-12 | 2017-05-18 | Wittenstein Se | Getriebe |
DE102016112520A1 (de) * | 2016-07-07 | 2018-01-11 | Ihi Charging Systems International Germany Gmbh | Lagervorrichtung für einen Abgasturbolader und Abgasturbolader |
US10378586B2 (en) * | 2017-08-21 | 2019-08-13 | Schaeffler Technologies AG & Co. KG | Bearing cage with lubrication channel |
US11732750B2 (en) | 2021-03-04 | 2023-08-22 | General Electric Company | Bearing system with independent adaptive stifness support |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS568925U (ja) * | 1979-07-03 | 1981-01-26 | ||
JPS5654323U (ja) * | 1979-10-03 | 1981-05-12 | ||
JPS61126146U (ja) * | 1985-01-28 | 1986-08-08 | ||
JP2002081528A (ja) * | 2000-09-05 | 2002-03-22 | Koyo Seiko Co Ltd | 歯車の支持構造 |
JP2005016710A (ja) | 2003-05-30 | 2005-01-20 | Nsk Ltd | 針状ころ軸受 |
JP2005325991A (ja) | 2004-04-12 | 2005-11-24 | Uchiyama Mfg Corp | ベアリングシール |
JP2005325992A (ja) | 2004-04-16 | 2005-11-24 | Nsk Ltd | ラジアル針状ころ軸受及びピニオンシャフト |
JP2008101725A (ja) | 2006-10-20 | 2008-05-01 | Nsk Ltd | 遊星歯車回転支持装置 |
JP2008303992A (ja) | 2007-06-08 | 2008-12-18 | Nsk Ltd | ラジアル針状ころ軸受 |
JP2009115323A (ja) | 2004-04-16 | 2009-05-28 | Nsk Ltd | ラジアル針状ころ軸受及びピニオンシャフト |
JP2009287772A (ja) * | 2008-05-01 | 2009-12-10 | Nsk Ltd | 針状ころ軸受 |
JP2010002029A (ja) | 2008-06-23 | 2010-01-07 | Nsk Ltd | ラジアル針状ころ軸受 |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0689781B2 (ja) * | 1989-06-28 | 1994-11-14 | エヌティエヌ株式会社 | 自動調心ころ軸受用の合成樹脂製保持器 |
DE8914265U1 (ja) * | 1989-12-04 | 1990-01-18 | Fag Kugelfischer Georg Schaefer Kgaa, 8720 Schweinfurt, De | |
IT1245292B (it) * | 1991-03-26 | 1994-09-13 | Skf Ind Spa | Gabbia di trattenimento per rulli conici |
DE9306686U1 (ja) * | 1993-05-04 | 1993-07-01 | Ina Waelzlager Schaeffler Kg, 8522 Herzogenaurach, De | |
AU2003223662A1 (en) * | 2002-04-12 | 2003-10-27 | The Torrington Company | Lubrication metering bearing retainer |
JP2004346980A (ja) * | 2003-05-20 | 2004-12-09 | Nsk Ltd | ラジアルニードル軸受と遊星歯車の回転支持装置と変速装置 |
JP4581542B2 (ja) * | 2004-08-02 | 2010-11-17 | 日本精工株式会社 | 回転支持装置 |
JP2006144839A (ja) * | 2004-11-17 | 2006-06-08 | Ntn Corp | ころ軸受 |
JP2006283933A (ja) * | 2005-04-04 | 2006-10-19 | Nsk Ltd | ラジアルニードル軸受 |
JP2007040334A (ja) * | 2005-08-01 | 2007-02-15 | Nsk Ltd | 針状ころ軸受 |
US7952837B1 (en) * | 2005-11-03 | 2011-05-31 | Seagate Technology Llc | Stiffened shaft bearing cartridge |
DE102005055618A1 (de) * | 2005-11-22 | 2007-05-24 | Schaeffler Kg | Käfig für Wälzkörper |
JP4848964B2 (ja) * | 2007-01-19 | 2011-12-28 | 株式会社ジェイテクト | 転がり軸受用保持器 |
JP2008215605A (ja) * | 2007-02-05 | 2008-09-18 | Nsk Ltd | ラジアルニードル軸受用保持器及びその製造方法とラジアルニードル軸受 |
JP2009019766A (ja) * | 2007-06-11 | 2009-01-29 | Nsk Ltd | 転がり軸受用保持器及び転がり軸受 |
DE102008035691B4 (de) * | 2008-07-30 | 2014-10-23 | Schaeffler Technologies Gmbh & Co. Kg | Radiallager |
-
2011
- 2011-11-25 US US13/498,065 patent/US20130004111A1/en not_active Abandoned
- 2011-11-25 EP EP11826107.2A patent/EP2660486A4/en not_active Withdrawn
- 2011-11-25 CN CN2011800034943A patent/CN102639885A/zh active Pending
- 2011-11-25 KR KR1020127007682A patent/KR101389164B1/ko active IP Right Grant
- 2011-11-25 WO PCT/JP2011/077171 patent/WO2012070642A1/ja active Application Filing
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS568925U (ja) * | 1979-07-03 | 1981-01-26 | ||
JPS5654323U (ja) * | 1979-10-03 | 1981-05-12 | ||
JPS61126146U (ja) * | 1985-01-28 | 1986-08-08 | ||
JP2002081528A (ja) * | 2000-09-05 | 2002-03-22 | Koyo Seiko Co Ltd | 歯車の支持構造 |
JP2005016710A (ja) | 2003-05-30 | 2005-01-20 | Nsk Ltd | 針状ころ軸受 |
JP2005325991A (ja) | 2004-04-12 | 2005-11-24 | Uchiyama Mfg Corp | ベアリングシール |
JP2005325992A (ja) | 2004-04-16 | 2005-11-24 | Nsk Ltd | ラジアル針状ころ軸受及びピニオンシャフト |
JP2009115323A (ja) | 2004-04-16 | 2009-05-28 | Nsk Ltd | ラジアル針状ころ軸受及びピニオンシャフト |
JP2008101725A (ja) | 2006-10-20 | 2008-05-01 | Nsk Ltd | 遊星歯車回転支持装置 |
JP2008303992A (ja) | 2007-06-08 | 2008-12-18 | Nsk Ltd | ラジアル針状ころ軸受 |
JP2009287772A (ja) * | 2008-05-01 | 2009-12-10 | Nsk Ltd | 針状ころ軸受 |
JP2010002029A (ja) | 2008-06-23 | 2010-01-07 | Nsk Ltd | ラジアル針状ころ軸受 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2660486A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112240347A (zh) * | 2019-07-17 | 2021-01-19 | 斯凯孚公司 | 轴承保持架及其应用 |
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US20130004111A1 (en) | 2013-01-03 |
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