WO2006013756A1 - 回転支持装置 - Google Patents
回転支持装置 Download PDFInfo
- Publication number
- WO2006013756A1 WO2006013756A1 PCT/JP2005/013694 JP2005013694W WO2006013756A1 WO 2006013756 A1 WO2006013756 A1 WO 2006013756A1 JP 2005013694 W JP2005013694 W JP 2005013694W WO 2006013756 A1 WO2006013756 A1 WO 2006013756A1
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- WO
- WIPO (PCT)
- Prior art keywords
- portions
- diameter side
- cage
- support device
- inner diameter
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/62—Selection of substances
-
- 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
-
- 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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
-
- 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
- F16C33/541—Details of individual pockets, e.g. shape or roller retaining means
-
- 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
- F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
- F16C33/546—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part with a M- or W-shaped cross section
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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
Definitions
- a rotation support device is used to rotatably support, for example, a planetary gear incorporated in a planetary gear mechanism constituting an automatic transmission for an automobile around a planetary shaft provided on a carrier.
- the present invention realizes a structure in which a cage is provided in order to achieve high-speed rotation, and the durability of the cage can be sufficiently secured.
- FIG. 9 shows an example of a planetary gear rotation support device that rotatably supports the planetary gear with respect to such a carrier.
- both ends of the planetary shaft 3 are supported and fixed at a plurality of positions in the circumferential direction of a pair of support plates 2a and 2b that are parallel to each other and that constitute the carrier 1.
- a planetary gear 4 is rotatably supported by a radial-one dollar bearing 5 around an intermediate portion of the planetary shaft 3.
- This radial single dollar bearing 5 holds a plurality of single dollars 6 by a cage 7 so that it can roll freely, and the intermediate outer peripheral surface of the planetary shaft 3 is formed as a cylindrical inner ring raceway 8.
- the inner peripheral surface of the planetary gear 4 is a cylindrical outer ring raceway 9, and the rolling surfaces of the needles 6 are in rolling contact with the inner ring raceway 8 and the outer ring raceway 9.
- floating washer 1 Oa and 10b are arranged between the axial end faces of the planetary gear 4 and the inner side faces of the support plates 2a and 2b, respectively. And the frictional force acting between the two support plates 2a and 2b are reduced.
- Patent Document 1 As a radial needle bearing for supporting a planetary gear incorporated in a planetary gear mechanism that constitutes an automatic transmission for automobiles, as described in Patent Document 1, for example, a total of one dollar without a cage is conventionally known. The type was common. In contrast, in recent years, in order to achieve high-speed rotation of planetary gears In order to avoid contact (rubbing) between dollars adjacent to each other in the circumferential direction, for example, as described in Patent Document 2 (Japanese Patent Laid-Open No. 8-270658), a cage 7 is provided. Radial needle bearings are often used.
- the retainer 7 constituting the radial-dollar bearing 5 is spaced apart from each other in the axial direction (left-right direction in FIGS. 9 to 11), for example, as shown in FIG. And a pair of rim portions 11 each having a ring shape and a plurality of column portions 12.
- Each of these column portions 12 is intermittently arranged in the circumferential direction, and both end portions thereof are connected to the outer diameter portions of the inner side surfaces of the rim portions 11 facing each other.
- Each of the column parts 12 has a shape in which the axially intermediate part is bent in a trapezoidal shape inward in the radial direction.
- each of the column portions 12 includes a pair of outer diameter side straight portions 13, a pair of inclined portions 14, and one inner diameter side straight portion 15.
- both outer diameter side straight portions 13 are arranged in parallel with the center axis of the cage 7 with the respective base end portions being continuous with the inner surface outer diameter portions of the two rim portions 11.
- the both inclined portions 14 are formed by connecting the base end portions of the both outer diameter side straight portions 13 and the axial direction central portion of the retainer 7 in the radial direction of the retainer 7. Inwardly inclined in the direction of force.
- the inner diameter side straight portion 15 is arranged in parallel with the central axis of the cage 7 with both end portions being continuous with the tip portions of the both inclined portions 14.
- Space portions surrounded by both circumferential side surfaces of the pillar portions 12 adjacent to each other in the circumferential direction and inner surfaces facing each other of the rim portions 11 are defined as pockets 16, respectively.
- Each of the above-mentioned dollars 6 is held in 16 so that it can roll freely.
- the cage 7 is provided with locking projections 17 at positions that are aligned with each other with respect to the circumferential direction on both side surfaces of the both end portions of the pillars 12 so that these side forces protrude in the circumferential direction. ing.
- Each of the locking projections 17 is for preventing each of the dollars 6 that are rotatably held in the pockets 16 from coming out of the pockets 16 outward in the radial direction.
- each of the locking projections 17 is provided on the portion so as to face each other, and the distance D (FIG. 10) between the leading edges of the locking projections 17 is
- the inner end edge in the radial direction of the cage 7 is positioned on the inner diameter side of the pitch circle of each of the above-mentioned dollars 6 and the distance D ( Fig 10
- each one-dollar 6 is Rather than abutting only on one of the circumferential side surfaces of each inner diameter side straight portion 15, they are alternately abutted on both sides in the circumferential direction in accordance with the revolving motion of each dollar 6.
- moment loads in different directions are alternately applied to the respective column portions 12, and it becomes difficult to ensure the durability of the continuous portions between the both end portions of the respective column portions 12 and the rim portions 11.
- the reason for this will be described with reference to FIG.
- the planetary gear 4 incorporated in the planetary gear mechanism revolves around the sun gear (not shown) as the carrier 1 rotates, and based on the combination of the sun gear and the ring gear (not shown), Rotates around 3.
- each of the dollars 6 constituting the radial-dollar bearing 5 that rotatably supports the planetary gear 4 around the planetary shaft 3 is caused by the rotation of the planetary gear 4. Revolving around the planetary axis 3 while rotating. In this case, each of the dollars 6 receives the centrifugal force of the revolving motion around the sun gear, and is displaced outward in the radial direction of the carrier 1. Pressed against.
- the magnitude of the force with which each of these dollars 6 is pressed against the circumferential side surface of each of the pillars 12 differs depending on the position of each of the needles 6 with respect to the planetary axis 3.
- the needle 6 present in the direction perpendicular to the radial direction of the carrier 1 (the left and right ends in FIG. 12) is pressed against the side surface of each column 12 that is the strongest.
- the dollars 6 are strongly pressed alternately from the opposite direction each time the cage 7 makes one rotation.
- circumferential force is alternately applied to each of the pillars 12, and the continuous part between the both ends of the pillars 12 and the rims 11 is easily fatigued. The security is impaired.
- Structures for restricting the radial position of the cage 7 incorporated in the radial needle bearing 5 include a so-called needle guide, a so-called outer ring guide, and a so-called inner ring guide.
- the two dollar guide regulates the radial position of the cage 7 by engaging the pocket 16 of the cage 7 with the rolling surface of each of the dollars 6.
- the outer ring guide regulates the radial direction position of the cage 7 by making the outer peripheral surface of the cage 7 and the outer ring raceway 9 close to each other.
- the inner ring guide regulates the radial position of the cage 7 by causing the inner circumferential surface of the cage 7 and the inner ring raceway 8 to face each other in close proximity.
- each of the dollars 6 is formed on the both sides of the circumferential direction of each column portion 12 based on the centrifugal force accompanying the rotation of the carrier 1. Accordingly, the continuous portions of the both end portions of the column portions 12 and the rim portions 11 are easily fatigued. [0013] However, if the outer ring guide or the inner ring guide is employed, and the entire column portion 12 is shifted to the outer diameter side or the inner diameter side of the pitch circle of each needle 6, each of these one dollars. The component force in the radial direction is generated in the force by which 6 presses each of the column parts 12.
- Patent Document 1 Japanese Utility Model Publication No. 5-62729
- Patent Document 2 JP-A-8-270658
- the rotary support device of the present invention has a support shaft having a cylindrical inner ring raceway on the outer peripheral surface and a cylindrical outer ring raceway on the inner peripheral surface, and is concentric with the support shaft around the support shaft.
- the cage includes a pair of rim portions disposed at positions sandwiching each of the dollars from both sides in the axial direction, and a plurality of pillar portions connecting the rim portions. Is.
- Each of the needles is held in a pocket that exists between the rim portions and the column portions adjacent in the circumferential direction.
- the axially central portion and the rolling surfaces of the needles do not come into contact among the circumferential side surfaces of the column portions.
- the axial central portion and the rolling surface of each dollar do not come into contact among the circumferential side surfaces of each column portion.
- the abutting portions between the rolling surfaces of the dollars and the circumferential side surfaces of the column portions are only the portions near the axial ends of the column portions. Therefore, the distance from the force point of the force with which each needle presses each column portion to the continuous portion between the both axial end portions of each column portion and both rim portions is shortened. Since the stress generated in each continuous portion is proportional to the product of the force applied to the force point and the distance, the distance is reduced and the continuous portion is not easily fatigued. The durability of the cage can be improved.
- FIG. 1 is a cross-sectional view showing an overall configuration of Example 1 of the present invention.
- FIG. 2 is an enlarged view of a portion X in FIG.
- FIG. 3 is a view of the retainer column taken out and seen from the side of FIG.
- FIG. 4 is a partially enlarged perspective view of the cage.
- FIG. 5 is a diagram showing two examples of the cross-sectional shape of the inner-diameter linear portion in the middle of the column portion.
- FIG. 6 is a view similar to FIG. 3, showing Example 2 of the present invention.
- FIG. 7 is a view similar to FIG. 3, showing Example 3.
- FIG. 8 is a view showing Example 4 in which FIG. 8 (A) is a view similar to FIG. 3, and FIG. 8 (B) is a view showing the upward force of (A).
- FIG. 9 is a partial cross-sectional view showing an example of a conventionally known rotation support device for a planetary gear.
- FIG. 10 is a perspective view showing an example of a radial-dollar bearing retainer that is an object of the present invention.
- FIG. 11 is a cross-sectional view taken along line AA in FIG.
- FIG. 12 is a schematic diagram for explaining the reason why forces in different directions with respect to the circumferential direction are alternately applied to the pillar portion of the cage.
- positioning in the radial direction of the cage is achieved by outer ring guidance in which the outer peripheral surfaces of both rim portions are opposed to the inner peripheral surface of the rotating member.
- the positioning of the cage in the radial direction is achieved by a one-dollar guide by engaging both circumferential side surfaces of each column and the rolling surfaces of each needle.
- the axial dimension of the central portion in the axial direction that does not come into contact with the rolling surface of each two dollars among both circumferential side surfaces of each column portion is 1Z4 or more (more preferably 1Z3 or more).
- the upper limit of the axial dimension is not particularly restricted for the purpose of the present invention. As long as the function as a cage is not impaired, the larger the better.
- each of the column portions includes a pair of outer diameter side straight portions, a pair of inclined portions, and one inner diameter side straight portion. Shall be.
- both the outer diameter side straight portions are arranged in parallel with the central axis of the cage, with the respective base end portions continuing to the inner surface outer diameter portions of both rim portions.
- both inclined portions have their base end portions connected to the both outer diameter side straight portions, and the inner ends in the radial direction of the retainer as the force toward the axial central portion of the retainer is increased. It is assumed that it is tilted in the direction to face the direction.
- the inner diameter side linear portion is arranged in parallel with the central axis of the cage, with both end portions being continuous with the tip portions of the inclined portions.
- Such a structure can stabilize the posture of each dollar in each of the pockets (squeeze can be suppressed). Therefore, if the present invention is implemented with such a structure, the rotary member It can contribute to improving the performance of various devices equipped with this rotating member, such as stable and low rotational resistance.
- the both circumferential sides of the inner diameter side straight portion are connected to both outer diameter side straight lines. It is made to dent about the width direction of each pillar part rather than the both side surfaces of at least one of a part and both inclination parts.
- the radially outer side portion of the cage on both side surfaces in the circumferential direction of the inner diameter side linear portion is similarly recessed from the inner side portion.
- the thickness dimension of the inner diameter side straight line portion can be made smaller than the thickness dimension of both outer diameter side straight line portions and the thickness dimension of both inclined portions.
- Such a structure has a problem that the cross-sectional area of the inner diameter side linear portion is reduced, and it is difficult to ensure the strength and rigidity of the inner diameter side linear portion, but from the power point to each of the continuous portions. The effect that the stress generated in each of these continuous portions can be sufficiently relaxed by sufficiently shortening the distance is sufficiently obtained.
- the entire inner diameter linear portion is arranged radially inward of the pitch circle of each dollar. You can also.
- the support shaft is a planetary shaft supported by a carrier constituting the planetary gear mechanism
- the rotating member is a planetary gear disposed around the planetary shaft.
- each needle constituting the radial needle bearing for rotatably supporting the planetary gear around the planetary shaft supported by the carrier constituting the planetary gear mechanism is accompanied by the rotation of the carrier.
- a centrifugal force directed radially outward of the carrier is applied. Therefore, it is effective to implement the present invention with such a planetary gear mechanism in order to improve the durability of the radial-dollar bearing, extension and the planetary gear mechanism.
- the planetary shaft is made of steel which is hardened by hardening only the surface layer portion.
- a centrifugal force accompanying a revolving motion and a force generated at a meshed portion with the sun gear and the ring gear are applied as a radial load.
- This radial load is applied as a force in the direction of bending to the planetary shaft through each of the dollars constituting the radial-single dollar bearing, and as a result, the planetary shaft is slightly elastically changed.
- the planetary shaft is generally made of hardened steel, but residual austenite is unavoidably present in the hardened steel. Such retained austenite decomposes when used at a high temperature of 80 ° C or higher, causing volume expansion.
- the temperature of the lubricating oil (ATF) is often used at 80 ° C or more, and the conditions for decomposing residual austenite in the planetary shaft are in place.
- the planetary shaft is elastically deformed based on the radial load in a state where the retained austenite in the planetary shaft is decomposed in this way, plastic deformation in the bending direction of the planetary shaft proceeds. . That is, the decomposition rate of the retained austenite is plastically deformed in an arc shape corresponding to the direction of the radial load because the portion where the tensile stress acts is faster than the portion where the compressive stress acts. In this way, the speed at which the planetary shaft is plastically deformed is supported around the higher the temperature of the planetary shaft, the faster the revolution speed, the smaller the cross-sectional diameter, and the longer the axial dimension. The greater the torque transmitted by the planetary gear, the greater the torque.
- the rolling surfaces of the needles and the column portions are engaged at both axial ends of the needles. It is preferable to combine them. In this case, since both side edges in the circumferential direction of both inclined parts of these column parts and the rolling surfaces of the needles are brought into sliding contact with each other, the axial center part of the column parts is provided. The distance between the inner peripheral side surface of the inner diameter side linear portion and the outer peripheral surface of the planetary shaft becomes shorter.
- the planetary shaft is made of steel that has been hardened and hardened only in the surface layer, thereby securing the amount of retained austenite in the surface layer.
- the nitrogen concentration on the planetary shaft surface is 0.05 to 0.5 wt% (more preferably 0.009 to 0.5 wt%), and carbon The concentration is set to 0.9 to 1.8% by weight.
- steel containing 0.9 to 1.8 wt% Cr is used as the steel constituting the planetary shaft.
- steel containing 0.4 to 0.8 Si is used as the steel constituting the planetary shaft.
- the minimum hardness of the planetary shaft is set to Hv300 or more.
- the minimum hardness of the planetary shaft (generally, the hardness of the central portion in the radial direction of the planetary shaft) is also effective for suppressing the bending of the planetary shaft.
- the minimum hardness is set to Hv300 or higher, preferably Hv350 or higher, more preferably Hv400 or higher.
- Example 1 to 5 show Example 1 of the present invention.
- the feature of the present invention is that the stress generated in the continuous portion between both end portions of each column portion 12a and both rim portions 11 is relieved and damage such as cracks is prevented from occurring in both continuous portions. .
- the shape of both side surfaces in the circumferential direction of each column portion 12a is devised, and the inner diameter side linear portion 15 provided in the middle portion in the axial direction of each column portion 12a is held.
- the position of the vessel 7a in the radial direction is regulated.
- the circumferential side surfaces of both inclined portions 14 and the inner diameter side linear portion 15 of the column portions 12a are made of metal plates constituting the cage 7a.
- a stepped shape having a curved S-curved portion 18 in the middle in the thickness direction is formed, and the portion indicated by the diagonal lattice in FIG. 3 is recessed with respect to the other portions.
- the inner diameter side straight portion 15 with respect to the direction is positioned relatively on the inner diameter side.
- the radial position of each of the bent portions 18 existing in the radial intermediate portion on both sides in the circumferential direction of each of the column portions 12a is set slightly inside the pitch circle P of each of the dollars 6 Is located.
- each of the above-mentioned one-dollar 6 rolling surfaces and each of the column parts 12a The radial position where the both sides of the circumferential surface abut each other is slightly deviated from the pitch circle P of each of these one-dollar 6, but since the deviation is slight, the radial position of each of the bent portions 18 is set as described above. Even if configured in this way, there is no particular problem.
- the circumference of the rolling surface of each needle 6 and the circumference of each column portion 12a is devised by devising the shape of both side surfaces in the circumferential direction and restricting the radial position of each bent portion 18.
- the both side surfaces in the direction come into contact with a part of the both inclined portions 14 shown by thick solid lines (i) in FIG.
- both circumferential side surfaces of the inner diameter side straight portion 15 and the rolling surfaces of the needles 6 that are present in the central portion in the axial direction do not contact each other.
- each of the column parts 12a can be secured. That is, the thickness dimension of each of the column parts 12a can be sufficiently secured including the inner diameter side straight part 15, and the width dimension in the circumferential direction is about the same as the outer diameter side straight part 13 in the circumferential direction. It can be secured.
- the cross-sectional area of the inner diameter side straight portion 15 and each inclined portion 14 can be sufficiently widened, and the strength and rigidity of the inner diameter side straight portion 15 and each inclined portion 14 can be sufficiently secured. Further, the width dimension in the circumferential direction of each outer diameter side straight portion 13 can be sufficiently secured from the inner diameter side to the outer diameter side, and the cross-sectional area of each outer diameter side straight portion 13 can be sufficiently widened. The surface force of stress relaxation generated in each outer diameter side straight portion 13 is also advantageous.
- each column portion 12 can be made desired by using the fracture surface generated at the time of punching as each of the bent portions 18.
- the cross-sectional shape of each of these bent portions 18 is a concave curved surface as shown in FIG. Or a planar shape as shown in (B). The point is that the outer diameter side half of the inner diameter side straight portion 15 is recessed in the circumferential direction so that the portion does not come into contact with the rolling surface of each dollar 6. Good.
- Fig. 6 shows a second embodiment of the present invention.
- the inner diameter side straight portion 15 as a whole is made closer by bringing the inner peripheral side surface of the inner diameter side straight portion 15 constituting the intermediate portion in the axial direction of the column portion 12b closer to the outer peripheral surface of the support shaft 3. It is arranged radially inside the pitch circle of each dollar 6 (see Fig. 1 and 2).
- Fig. 7 shows a third embodiment of the present invention.
- the thickness dimension t of the inner diameter side straight part 15a constituting the intermediate part in the axial direction of the column part 12c is set to the thickness dimension T of both outer diameter side straight parts 13 and It is smaller than the thickness dimension T (t to T).
- the entire inner diameter side linear portion 15a is positioned on the inner diameter side of the pitch circle of each dollar 6 (see FIGS. 1 and 2).
- the outer peripheral surface of the inner diameter side straight portion 15a is positioned on the inner diameter side of the pitch circle of each of the needles 6 in this way.
- the rolling surface and both side surfaces in the circumferential direction of each of the pillar portions 12c are in contact with each other at a part of the inclined portions 14 shown by thick solid lines (i) in FIG. Therefore, from the force point of the force that each of these dollars 6 presses each of the column portions 12c, the continuous portion 19 (see FIG. (Refer to the above), the durability of the cage 7a can be improved.
- the thickness dimension t of the inner diameter side straight portion 15a is made smaller, the outer peripheral surface of the inner diameter side straight portion 15a is made larger than the pitch circle as described above. Even when positioned on the inner diameter side, it is possible to prevent the inner peripheral surface of the inner diameter side linear portion 15a from being too close to the outer peripheral surface of the planetary shaft 3.
- Fig. 8 shows a fourth embodiment of the present invention.
- the width dimension w in the circumferential direction of the inner diameter side straight portion 15b constituting the intermediate portion in the axial direction of the column portion 12d is set to the width dimension W of both outer diameter side straight portions 13 and both inclined portions. It is smaller than the thickness dimension W of 14 (w and W). Therefore, in the case of the present embodiment, both the circumferential side surfaces of the inner diameter side linear portion 15b shown by the oblique lattice in FIG. It is recessed in the width direction of each pillar 12d.
- the inner diameter side straight portion 15b is positioned on the pitch circle of each dollar 6 (see FIGS. 1 and 2).
- the inner diameter side straight portion 15b is positioned on the pitch circle of each dollar 6, so that the inner peripheral surface of the inner diameter side straight portion 15b and the outer peripheral surface of the planetary shaft 3 are arranged. Can be prevented from getting too close.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Heat Treatment Of Articles (AREA)
- General Details Of Gearings (AREA)
- Retarders (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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DE112005001874T DE112005001874B4 (de) | 2004-08-02 | 2005-07-27 | Rotationssupportvorrichtung |
US11/659,217 US8322931B2 (en) | 2004-08-02 | 2005-07-27 | Rotation support apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-225136 | 2004-02-08 | ||
JP2004225136A JP4581542B2 (ja) | 2004-08-02 | 2004-08-02 | 回転支持装置 |
Publications (1)
Publication Number | Publication Date |
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WO2006013756A1 true WO2006013756A1 (ja) | 2006-02-09 |
Family
ID=35787045
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2005/013694 WO2006013756A1 (ja) | 2004-08-02 | 2005-07-27 | 回転支持装置 |
Country Status (4)
Country | Link |
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US (1) | US8322931B2 (ja) |
JP (1) | JP4581542B2 (ja) |
DE (1) | DE112005001874B4 (ja) |
WO (1) | WO2006013756A1 (ja) |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5273996B2 (ja) * | 2007-02-26 | 2013-08-28 | Ntn株式会社 | 保持器付きころ |
DE102007030217A1 (de) * | 2007-06-29 | 2009-01-08 | Schaeffler Kg | Käfig |
US8834035B2 (en) * | 2007-12-27 | 2014-09-16 | Ntn Corporation | Roller bearing retainer and needle roller bearing |
US8602657B2 (en) * | 2009-06-15 | 2013-12-10 | Koyo Bearings Usa Llc | Cage for bearing assembly |
DE102009056354A1 (de) | 2009-11-30 | 2011-06-01 | Schaeffler Technologies Gmbh & Co. Kg | Nadelkranz mit einem W-förmigen Käfig und darin geführten Wälzkörpern für Automobilanwendungen |
DE102010019069A1 (de) | 2010-05-03 | 2011-11-03 | Schaeffler Technologies Gmbh & Co. Kg | Axialkäfig für zylindrische Wälzkörper |
DE102010035797A1 (de) * | 2010-08-30 | 2012-03-01 | Schaeffler Technologies Gmbh & Co. Kg | Wälzkörperkäfig für zylindrische Wälzkörper eines Wälzlagers |
CN102639885A (zh) * | 2010-11-26 | 2012-08-15 | 日本精工株式会社 | 径向滚针轴承用隔离件 |
JP2013068281A (ja) * | 2011-09-22 | 2013-04-18 | Ntn Corp | ころ軸受 |
JP5773823B2 (ja) * | 2011-09-27 | 2015-09-02 | Ntn株式会社 | ころ軸受の保持器 |
JP5773822B2 (ja) * | 2011-09-27 | 2015-09-02 | Ntn株式会社 | ころ軸受の保持器 |
DE102011085716A1 (de) * | 2011-11-03 | 2013-05-08 | Schaeffler Technologies AG & Co. KG | Radialkäfig für zylindrische Wälzkörper, insbesondere Nadelkranzkäfig |
DE102011085713A1 (de) * | 2011-11-03 | 2013-05-08 | Schaeffler Technologies AG & Co. KG | Radialkäfig für zylindrische Wälzkörper, insbesondere Nadelkranzkäfig |
JP6389031B2 (ja) * | 2013-06-10 | 2018-09-12 | Ntn株式会社 | 円錐ころ軸受 |
US20150292557A1 (en) * | 2014-04-11 | 2015-10-15 | Schaeffler Technologies AG & Co. KG | Cage for rolling bearing assembly and rolling element-cage assembly with enhanced lubricating abilities |
DE102014212270A1 (de) * | 2014-06-26 | 2016-01-14 | Schaeffler Technologies AG & Co. KG | Käfig für ein Wälzlager, Wälzlager und Planetenradlagerung |
DE102014214332A1 (de) * | 2014-07-23 | 2016-01-28 | Schaeffler Technologies AG & Co. KG | Käfig für ein Wälzlager, Wälzlager und Planetenradlagerung |
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DE102016211917A1 (de) * | 2016-06-30 | 2018-01-04 | Aktiebolaget Skf | Wälzlagerkäfig oder Wälzlagerkäfigsegment |
JP7089369B2 (ja) | 2018-01-09 | 2022-06-22 | Ntn株式会社 | 保持器付きころおよび遊星歯車支持構造 |
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Also Published As
Publication number | Publication date |
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JP4581542B2 (ja) | 2010-11-17 |
DE112005001874T5 (de) | 2007-07-19 |
JP2006046391A (ja) | 2006-02-16 |
DE112005001874B4 (de) | 2010-07-08 |
US8322931B2 (en) | 2012-12-04 |
US20090215583A1 (en) | 2009-08-27 |
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