WO2006041184A1 - 転がり、摺動部材、これを用いたトロイダル型無段変速機および転がり、摺動部材の製造方法 - Google Patents
転がり、摺動部材、これを用いたトロイダル型無段変速機および転がり、摺動部材の製造方法 Download PDFInfo
- Publication number
- WO2006041184A1 WO2006041184A1 PCT/JP2005/019036 JP2005019036W WO2006041184A1 WO 2006041184 A1 WO2006041184 A1 WO 2006041184A1 JP 2005019036 W JP2005019036 W JP 2005019036W WO 2006041184 A1 WO2006041184 A1 WO 2006041184A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rolling
- continuously variable
- disk
- roll
- variable transmission
- Prior art date
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Classifications
-
- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
- C22C38/22—Ferrous alloys, e.g. steel alloys containing chromium with molybdenum or tungsten
-
- C—CHEMISTRY; METALLURGY
- C21—METALLURGY OF IRON
- C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
- C21D1/00—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering
- C21D1/18—Hardening; Quenching with or without subsequent tempering
-
- C—CHEMISTRY; METALLURGY
- C21—METALLURGY OF IRON
- C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
- C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
-
- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/04—Ferrous alloys, e.g. steel alloys containing manganese
-
- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
- C22C38/34—Ferrous alloys, e.g. steel alloys containing chromium with more than 1.5% by weight of silicon
-
- 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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
Definitions
- Rolling and sliding member toroidal continuously variable transmission using the same, and method for manufacturing rolling and sliding member
- the present invention relates to a rolling and sliding member, a toroidal continuously variable transmission using the same, and a rolling
- the present invention relates to a method for manufacturing a sliding member.
- a rolling and sliding part refers to a part that makes pure rolling contact, pure sliding contact, and a mixture of rolling contact and sliding contact.
- a force that is known as a full toroidal type nyanoft toroidal type is used.
- the contact area between the I / O disk and the roller is exposed to high temperature (100 ° C or higher) and high surface pressure (several thousand MPa or higher, for example, maximum contact pressure of 4000 MPa or more).
- high temperature 100 ° C or higher
- high surface pressure hundreds or higher, for example, maximum contact pressure of 4000 MPa or more.
- a large vertical stress repeatedly acts from three points, and a large shear stress corresponding to the oil film shear stress repeatedly acts during power transmission.
- a large vertical stress and a large shear stress repeatedly act on the outer peripheral surface of the roller.
- the raceway surface of the input / output disk and the outer peripheral surface of the roller can be said to have special and severe contact conditions compared to the rolling surface of a normal rolling bearing in which only normal stress mainly acts on the surface.
- a white structure (White Etching Area) was generated in addition to a black structure (Dark Etching Area), which is a general rolling fatigue structure, resulting in a short life.
- White yarn and weave is considered to be generated by transformation of retained austenite in the surface layer to martensite due to stress-induced transformation.
- Patent Document 1 Japanese Patent Laid-Open No. 2002-188702
- Rolling and sliding members according to the present invention are: C: 0.9 to 1. lwt%, Si: 0.5 to 3. Owt%, Mn: 0.05 to 0.5 wt%, Cr: 2 0-5.Owt%, Mo: 0.05-0.5wt%, the balance Fe and unavoidable impurities are formed by steel, and the average particle size of spherical carbide is 0.
- the amount of spherical carbide is set to 6.0% or less in terms of area ratio.
- the reasons for limiting the content of each element in the steel used, the average particle size of the spherical carbide, and the amount are as follows.
- the C has the effect of strengthening martensite by solid solution in the base, ensuring the hardness after tempering and improving the rolling fatigue life characteristics, but such an effect is less than 0.9 wt%. If it exceeds 1. lwt%, giant carbides are formed and the rolling fatigue life characteristics deteriorate.
- the C content is preferably 0.995-1.05 wt%.
- Si has the effect of suppressing the precipitation of fine carbides in the martensite structure and suppressing the strength reduction of martensite due to rolling fatigue. If less than 0.5 wt%, the effect of suppressing the strength reduction is small 3 wt% Exceeding toughness decreases and rolling fatigue life decreases. Si The content is preferably 1.0 to 2. Owt%.
- Mn improves the hardenability of the steel to increase the toughness of the base martensite and has the effect of improving the hardness and rolling fatigue life characteristics. However, if it exceeds 0.5 wt%, the machinability is significantly reduced.
- the Mn content is preferably 0.3 to 0.48 wt%.
- Cr promotes carbide formation and has the effect of increasing the calorie (stabilization) of the retained austenite phase by lowering the Mf point at which martensitic transformation is completed.However, if the content is less than Owt%, carbide precipitation occurs. If the amount is less than 5. Owt%, the amount of carbide precipitation increases too much, the hardness after heat treatment decreases, and the rolling fatigue life decreases.
- the Cr content is preferably 2.0 to 3.5 wt%.
- Mo is a force that has the effect of solid solution in the base to secure the hardness after tempering and improve the rolling fatigue life characteristics.If it is less than 0.05 wt%, such an effect cannot be obtained, and 0.5 wt% Above%, the above effect becomes saturated and the cost increases.
- the Mo content is preferably 0.2 to 0.45 wt%.
- the average particle size of the spherical carbide exceeds 0.6 m, it will act as a stress concentration source at the time of rolling contact.
- the lower limit of the average particle size of the spherical carbide is preferably 0.2 m. This is because if it is smaller than this, the wear resistance may be lowered.
- the average particle size of the spherical carbide is preferably 0.4 to 0.6 m.
- the amount of dissolved carbon in the martensite decreases and the martensite hardness decreases, resulting in a decrease in rolling fatigue life.
- the lower limit of the area ratio of the spherical carbide is preferably 0.3%. If the amount is less than this, the solid solution carbon concentration in the matrix becomes high, and there is also a force that may reduce the rolling life.
- the area ratio of the spherical carbide is preferably 4-6%.
- the amount of retained austenite is preferably 10 to 25%. Residual austenite has the effect of relaxing the stress concentration at the time of rolling contact and improving the rolling fatigue life.
- the amount of retained austenite is less than 10%, the effect of reducing the stress concentration is reduced.
- the upper limit of the amount of retained austenite is preferably 25%.
- the amount of retained austenite is preferably 11 to 21%.
- a toroidal continuously variable transmission according to the present invention includes a disk-shaped power transmission member having a concave raceway surface on a side surface, and a roller-shaped power transmission member that rolls on the raceway surface of the disk-shaped power transmission member.
- at least one of the two power transmission members is composed of the rolling and sliding parts according to the present invention described above.
- the rolling and sliding member manufacturing method according to the present invention includes: C: 0.9 to 1. lwt%, Si: 0.5 to 3. Owt%, Mn: 0.05 to 0.5 wt%, Cr : 2. 0 ⁇ 5. Owt%, Mo: 0.05 ⁇ 0.5wt%, 850 ⁇ 950 ° to the processed material formed into a predetermined shape with steel composed of the remainder Fe and inevitable impurities After quenching by heating to C and quenching, tempering by heating to 250 to 350 ° C was performed, so that the average particle size of spherical carbide was less than 0, and the amount of spherical carbide was 6 by area ratio. 0% or less.
- the heating temperature during the quenching treatment was limited to 850 to 950 ° C, and the heating temperature during the tempering treatment was limited to 250 to 350 ° C.
- C 0.9 to 1. lwt%, Si: 0. 5 ⁇ 3.Owt%, Mn: 0.05 ⁇ 0.5wt%, Cr: 2.0 ⁇ 5.Owt%, Mo: 0.05 ⁇ 0.5wt%, balance Fe and inevitable impurities
- the average particle size of the spherical carbide should be 0. or less and the amount of spherical carbide should be 6.0% or less in terms of area ratio. Because you can.
- the heating temperature during the quenching treatment is preferably 860 to 940 ° C, and the heating temperature during the tempering treatment is preferably 260 to 300 ° C.
- the rolling and sliding member of the present invention even when used for a long time, the generation of a white structure can be suppressed and the life can be extended. Moreover, carburizing or carbonitriding Therefore, it is possible to manufacture by simply performing a quenching process and a tempering process without performing shot peening, thereby reducing the manufacturing cost.
- the life of the disk-shaped power transmission member and the roller-shaped power transmission member can be extended.
- FIG. 1 shows a noriator portion of a full toroidal continuously variable transmission as a toroidal continuously variable transmission using a rolling and sliding member as a disk-shaped power transmission member and a roller-shaped power transmission member according to the present invention. Show.
- the variator (1) of the toroidal-type continuously variable transmission is provided with an input shaft (3) that is rotationally driven by a power source (2) of the automobile, and the input shaft (3)
- An input disk (4) (disk-shaped power transmission member) as a power transmission member on the input side is fitted on both ends in the axial direction.
- a spline hole (4a) is formed in the center of each input disk (4), and the axially inner side surface of each input disk (4), that is, the side surface facing the other input disk (4),
- An annular concave raceway surface (4b) is formed concentrically with the input shaft (3).
- the spline shaft (3a) formed on the input shaft (3) is inserted into the spline hole (4a) of the input disk (4), so that the input disk (4) is connected to the input shaft (3). And can move slightly in the length direction of the input shaft (3).
- a locking ring (5) is fixed axially outside the input disk (4) in the input shaft (3), thereby preventing the two input disks (4) from moving away from each other. .
- the cylindrical output shaft (8) is fitted on the outer periphery of the portion between the input disks (4) of the input shaft (3) so as to be concentric with the input shaft (3) and relatively rotatable. Being A predetermined gap is provided between both ends of the output shaft (8) and the input disk (4).
- An output disk (9) (disk-shaped power transmission member) as a power transmission member is fitted on both axial ends of the output shaft (8).
- a spline hole (9a) is formed in the center of each output disk (9), and each output disk (9)
- An annular concave raceway surface (9 b) is formed concentrically with the input shaft (3) and the output shaft (8) on the outer side surface in the axial direction, that is, the side surface facing the input disk (4). Then, the spline shaft portion (8a) formed on the output shaft (8) is inserted into the spline hole (9a) of the output disc (9), so that the output shaft (8) is connected to the output disc (9).
- the output disk (9) can move slightly in the length direction of the output shaft (8) while rotating integrally.
- a toothed belt wheel (8b) is formed on the output shaft (8) on the inner side in the axial direction from both output disks (9). Power is transmitted to the driven side (not shown) via the hooked toothed belt (11).
- a backup plate (13) is disposed on the side surface of each output disk (9) opposite to the raceway surface (9b) via a gap (12).
- the gap (12) is sealed by a casing (14) and a non-illustrated sealing means, and the output disk (9) is connected to the gap (12) by supplying hydraulic pressure from a hydraulic source (15). By energizing to the opposite input disk (4) side, a predetermined terminal load is applied.
- the portions between the raceway surface (4b) of the input disk (4) and the raceway surface (9b) of the output disk (9) that are opposed to each other are configured as toroid-like gaps.
- a plurality of, in this case, three rollers (16) (roller-shaped power transmission members) in rolling contact with both raceway surfaces (4b) and (9b) are arranged at equal intervals in the circumferential direction. Arranged.
- Each roller (16) is rotatably supported by a carriage (17) so that the contact position of each roller (16) with respect to both raceway surfaces (4b) (9b) is changed by the tilt of the carriage (17). It has become.
- each roller (16) in the toroidal gap is moved to both disks (4). Rolling contact with high load on the raceway surface (4b) (9b) of (9) and connecting both discs (4) (9) via the roller (16) ) To the output shaft (8). At this time, the rotational speed of the output disk (9) is changed by changing the contact position of each roller (16) with respect to the raceway surfaces (4b) and (9b) of both disks (4) and (9) by tilting the carriage (16). As a result, the gear ratio becomes variable.
- the force illustrated by the rolling mouth idle type continuously variable transmission using the rolling and sliding member according to the present invention is used.
- the rolling and sliding member according to the present invention is used as a half-toroidal continuously variable transmission.
- the spin component at the contact portion between the disk and the roller is large, the effect of the present invention is enhanced for a full toroidal continuously variable transmission.
- the rolling and sliding member according to the present invention can be applied to various rolling and sliding members such as other rolling bearings and one-way clutches.
- it is suitable for applications with large vibration impact, such as rolling elements for rolling bearings for alternators and bearing rings.
- a disk-shaped test roller (20) and a disk-shaped disk (22) having a diameter of 58 mm and a thickness of 8 mm were manufactured by the following method using six types of steels having the compositions shown in Table 1. That is, the steel is turned to form a predetermined shape, and then subjected to a quenching process in which the steel is heated for 45 minutes at the temperature shown in Table 1 and then rapidly cooled, and a tempering process in which the steel is heated at the temperature shown in Table 1 for 120 minutes. By further polishing, a test roller (20) and a disc-like disk (22) were produced.
- Example 1 1.0 1.5 0.45 2.0 0.4 Remaining 860 280 0.55 5.4
- Example 2 1.0 1.0 0.45 3.5 0.4 Remaining 900 220 0.50 5.6
- Example 3 1.0 3.0 0.45 5.0 0.4 Remaining 940 260 0.60 5.2
- Comparative example 1 1.0 1.0 0.45 2.0 0.4 Remaining 860 260 0.56 6.5
- Comparative example 2 1.0 3.5 0.45 2.0 0.4 Remaining 860 300 0.73 5.2
- Comparative example 3 1.0 1.0 0.45 6.0 0.4 Remaining 890 220 0.62 6.7
- a disk-shaped dummy roller (21) having a diameter of 58 mm and a thickness of 8 mm was manufactured by the following method using the steel having the composition of Example 1. In other words, after turning the above steel into a predetermined shape, it is subjected to quenching treatment in which it is heated at 850 ° C for 45 minutes and then rapidly cooled, and tempering treatment in which it is heated at 260 ° C for 120 minutes and then further polished. Make 7 dummy rollers (21).
- the average particle diameter and amount (area ratio) of the spherical carbide in the surface layer portion of the rolling surface of the roller (20) outer peripheral surface, and the amount of retained austenite were measured. These measurement positions are the depth at which the maximum contact surface pressure during operation, which will be described later, is calculated and the shear stress is maximized.
- the rotating shafts (20a) (21a) (22a) are fixed to the centers of both rollers (20X21) and the disc (22), respectively, and both rollers (20) (21)
- the rotating shafts (20a) and (21a) of the roller (20) are horizontal and parallel to each other, the rotating shaft (22a) of the disc (22) is vertical, and the rolling surfaces of both rollers (20) and (21) ( (Outer peripheral surface) Force disk (22)
- the discs were arranged so as to make rolling contact at the same radial and circumferential positions on the raceway surfaces on both sides.
- Both rollers (20X21) can be rotated at different speeds via a transmission (24) by a single motor (2 3), and the roller (20) to be tested is tracked by the disk (22). Slip against the surface.
- both rollers (20X21) were rotated under the operating conditions shown in Table 2 until separation occurred on the rolling surface of the roller (20) to be tested.
- the average particle diameter and the amount (area ratio) of the spherical carbide in the surface layer portion of the rolling surface of the roller to be tested (20) and the retained austenite amount are measured at the measurement positions described above. did.
- AO average particle size before the start of operation
- Aa average particle size after the end of operation
- B0 area ratio before the start of operation
- Ba area ratio after the end of operation
- ⁇ amount of retained austenite before the start of operation : amount of residual austenite after the end of operation
- Na number of repeated stresses during peeling occurs
- .nu.0: 1Omikuron is 6 (number of stress repetition amount of retained austenite begins to decrease).
- Example 1 0.55 0.51 0.001 5.4 5.2 0.003 ⁇ 6 0.07 68.6 to 0 6
- Example 2 0.50 0.46 0.001 5.6 5.4 0.006 15 11 0.17 31.2 to 0 6
- Example 3 0.60 0.57 0.001 5.2 4.9 0.007 21 19 0.08 40.6X10 6
- Comparative Example 1 0.56 0.37 0.020 6.5 5.0 0.158 ⁇ 7 0.42 9.5 to 0 6
- Comparative Example 2 0.73 0.63 0.008 5.2 3.4 0.141 18 15 0.23 12.8 to 0 6
- Comparative Example 3 0.62 0.50 0.006 6.7 4.5 0.116 21 16 0.26 ⁇ 9 to 0 6
- the average particle size change index X is 0 to 0.005
- the area ratio change index Y is 0 to 0.01
- the stress-induced transformation index Z is 0.2 or less by performing the test described above, It can be evaluated that the steel force rolls and the sliding member has a long life.
- the rolling and sliding member according to the present invention is suitably used as a roller and each disk of a toroidal-type continuously variable transmission, for example.
- FIG. 1 is a schematic longitudinal sectional view showing a variator part of a full toroidal continuously variable transmission.
- FIG. 2 is a schematic view showing the arrangement of a test roller, a dummy roller, and a disk in a test conducted to evaluate Examples 1 to 3 and Comparative Examples 1 to 3.
- FIG. 3 is a graph showing the relationship between the spherical carbide average particle size change index and the number of stress repetitions.
- FIG. 4 is a graph showing the relationship between the spherical carbide area ratio change index and the number of stress repetitions.
- FIG. 5 A graph showing the relationship between the stress-induced transformation index of retained austenite and the number of stress repetitions.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05793472A EP1811052A1 (en) | 2004-10-15 | 2005-10-17 | Roll/slide member, toroidal continuously variable transmission utilizing the same, and process for producing roll/slide member |
US11/665,502 US20070284020A1 (en) | 2004-10-15 | 2005-10-17 | Roll/slide member, toroidal continuously variable transmission utilizing the same, and process for producing roll/slide member |
JP2006540998A JPWO2006041184A1 (ja) | 2004-10-15 | 2005-10-17 | 転がり、摺動部材、これを用いたトロイダル型無段変速機および転がり、摺動部材の製造方法 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-301684 | 2004-10-15 | ||
JP2004301684 | 2004-10-15 |
Publications (1)
Publication Number | Publication Date |
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WO2006041184A1 true WO2006041184A1 (ja) | 2006-04-20 |
Family
ID=36148469
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/019036 WO2006041184A1 (ja) | 2004-10-15 | 2005-10-17 | 転がり、摺動部材、これを用いたトロイダル型無段変速機および転がり、摺動部材の製造方法 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20070284020A1 (ja) |
EP (1) | EP1811052A1 (ja) |
JP (1) | JPWO2006041184A1 (ja) |
KR (1) | KR20070099534A (ja) |
WO (1) | WO2006041184A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1826460A1 (en) | 2006-02-28 | 2007-08-29 | JTEKT Corporation | Manufacturing method for an input disc, output disc and power roller of a toroidal continuously variable transmission |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB201419494D0 (en) * | 2014-10-31 | 2014-12-17 | Torotrak Dev Ltd | Variations |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001181784A (ja) * | 1999-12-20 | 2001-07-03 | Ntn Corp | 動力伝達部品および駆動装置 |
JP2003502505A (ja) * | 1999-06-17 | 2003-01-21 | エスケイエフ エンジニアリング アンド リサーチ センター ビーブイ | ころがり構造物鋼 |
JP2003035316A (ja) * | 2001-07-24 | 2003-02-07 | Koyo Seiko Co Ltd | 転がり軸受 |
JP2004150592A (ja) * | 2002-10-31 | 2004-05-27 | Nsk Ltd | トロイダル型無段変速機 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4022607B2 (ja) * | 1999-07-21 | 2007-12-19 | 日産自動車株式会社 | 耐高面圧部材の製造方法 |
-
2005
- 2005-10-17 EP EP05793472A patent/EP1811052A1/en not_active Withdrawn
- 2005-10-17 KR KR1020077007944A patent/KR20070099534A/ko not_active Application Discontinuation
- 2005-10-17 US US11/665,502 patent/US20070284020A1/en not_active Abandoned
- 2005-10-17 JP JP2006540998A patent/JPWO2006041184A1/ja not_active Withdrawn
- 2005-10-17 WO PCT/JP2005/019036 patent/WO2006041184A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003502505A (ja) * | 1999-06-17 | 2003-01-21 | エスケイエフ エンジニアリング アンド リサーチ センター ビーブイ | ころがり構造物鋼 |
JP2001181784A (ja) * | 1999-12-20 | 2001-07-03 | Ntn Corp | 動力伝達部品および駆動装置 |
JP2003035316A (ja) * | 2001-07-24 | 2003-02-07 | Koyo Seiko Co Ltd | 転がり軸受 |
JP2004150592A (ja) * | 2002-10-31 | 2004-05-27 | Nsk Ltd | トロイダル型無段変速機 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1826460A1 (en) | 2006-02-28 | 2007-08-29 | JTEKT Corporation | Manufacturing method for an input disc, output disc and power roller of a toroidal continuously variable transmission |
Also Published As
Publication number | Publication date |
---|---|
KR20070099534A (ko) | 2007-10-09 |
JPWO2006041184A1 (ja) | 2008-05-22 |
EP1811052A1 (en) | 2007-07-25 |
US20070284020A1 (en) | 2007-12-13 |
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