WO2006003886A1 - Toroidal type stepless speed change device - Google Patents
Toroidal type stepless speed change device Download PDFInfo
- Publication number
- WO2006003886A1 WO2006003886A1 PCT/JP2005/011831 JP2005011831W WO2006003886A1 WO 2006003886 A1 WO2006003886 A1 WO 2006003886A1 JP 2005011831 W JP2005011831 W JP 2005011831W WO 2006003886 A1 WO2006003886 A1 WO 2006003886A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- swing
- supported
- toroidal
- continuously variable
- concave
- Prior art date
Links
Classifications
-
- 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
- the toroidal continuously variable transmission according to the present invention is used as a transmission unit that constitutes an automatic transmission device for a vehicle (automobile), for example.
- FIGS. 5 to 8 show a toroidal continuously variable transmission for a four-wheel drive vehicle with a large displacement described in Patent Document 1.
- FIG. This toroidal continuously variable transmission 1 includes three first power rollers 4 and 4 between a first input disk 2 and a first output disk 3, and a second input disk 5 and a second output. Three second power rollers 7 are respectively provided between the side disk 6 and a total of six power rollers 4 and 7 transmit power.
- a torque converter 8 that is a starting clutch is provided at the most front stage in the power transmission direction, and the toroidal-type continuously variable transmission is provided at the output of the torque converter 8.
- the front half 9a is driven to rotate by the torque converter 8 as the traveling engine (not shown) rotates.
- the rear half 9b of the input shaft 9 is supported on the rear end of the front half 9a so as to be concentric with each other and relatively rotatable.
- a forward / reverse switching unit 10 for switching between forward and backward movement is provided in series between the front half portion 9a and the rear half portion 9b in the power transmission direction.
- This forward / reverse switching unit 10 which is a planetary gear mechanism, switches between a forward state and a reverse state by selecting and connecting a forward clutch 11 and a reverse clutch 12, each of which is a wet multi-plate clutch. .
- the above-described forward / reverse switching unit 10 has a A toroidal continuously variable transmission 1 is provided.
- the toroidal continuously variable transmission 1 has an input portion connected to the output portion of the forward / reverse switching unit 10 and an output portion, that is, a portion connected to the front wheel drive shaft 13 and the rear wheel drive shaft 14.
- the gear ratio between is continuously changed.
- the toroidal continuously variable transmission 1 is provided around the latter half 9b. That is, the first and second input side disks 2 and 5 are concentric with each other in the state where the inner side surfaces, which are concave surfaces each having an arcuate cross section, face each other in the vicinity of both front and rear end portions of the latter half portion 9b.
- the first input side disk 2 provided on the front side is spline-engaged with the base end portion of the carrier 15 constituting the forward / reverse switching unit 10 and also moved forward. Is blocked.
- the second input side disk 5 provided on the rear side is supported on the rear end portion of the rear half portion 9b via the ball spline 16. Then, the second input disk 5 is pressed toward the first input disk 2 by a hydraulic opening device 17 so as to be freely pressed.
- a support cylinder 18 is provided concentrically with the latter half 9b around the middle part of the latter half 9b.
- the support cylinder 18 is supported and fixed at both ends by the inner diameter side ends of the stays 19 and 19.
- These stays 19 and 19 support and fix their outer diameter side ends to support rings 20 and 20 described later, respectively, and first and second swing frames 21 and 22 described later also swing themselves.
- the first and second support frames 23 and 24 are configured to support each other.
- the latter half 9b is supported inside the support cylinder 18, and the first and second output side disks 3 and 6 are supported around the support cylinder 18 so as to be freely rotatable and axially displaceable. Yes. Further, these output side disks 3 and 6 can freely rotate relative to each other while supporting the axial load applied between them by a thrust bearing provided therebetween.
- a front wheel output gear 25 is fixed to the outer surface side of the first output side disk 3, and the front wheel output gear 25 and the front wheel drive shaft 13 are connected via a front wheel driven gear 26.
- the front output shaft 13 can be driven to rotate by the first output side disk 3. Further, the rotation of the front wheel drive shaft 13 can be transmitted to a front wheel (not shown) via a front wheel differential gear 27.
- a rear wheel output gear 28 is fixed to the outer surface side of the second output side disk 6, and the rear wheel output gear 28 and the rear wheel drive shaft 14 are connected to each other.
- the rear wheel driven shaft 29 is engaged, and the second output side disk 6 allows the rear wheel drive shaft 14 to be rotationally driven.
- the rotation of the rear wheel drive shaft 14 can be transmitted to the rear wheels via a rear wheel differential gear (not shown).
- first power rollers 4, 4 are provided between the inner side surface of the first input side disc 2 and the inner side surface of the first output side disc 3, and the second input side disc.
- the three second power rollers 7 are sandwiched between the inner surface of 5 and the inner surface of the second output side disk 6.
- the first and second power rollers 4 and 7 are respectively provided on the inner surfaces of the first and second trolleys 30 and 31, respectively, with the displacement shafts 32 and 32 provided in a state where the inner surface force protrudes. It is supported so that it can rotate freely.
- These first and second traons 30 and 31 do not intersect the central axes of the disks 2, 5, 3, and 6 provided concentrically with each other at both ends.
- First and second pivots 33 (second pivots not shown) present at twisted positions at right angles to or near right angles to the directions of the central axes of 2, 5, 3, 6 Rocks around the center.
- the first and second troons 30 and 31 are supported at both ends of the first and second swing frames 21 and 22 so as to be swingably displaceable.
- the disk 2, 5, 3, 6 is supported so as to be swingable and displaceable about a support shaft 34, 34 provided in a direction parallel or nearly parallel to the central axis of the disk 2, 5, 3, 6.
- Each of the first and second support frames 23 and 24 has a pair of support rings 20 and 20 arranged in parallel to each other, outside the three support portions 35 and 35 constituting the stay 19. They are connected to each other through the radial end.
- the support shafts 34 and 34 constitute the first and second support frames 23 and 24 at intermediate positions of the support columns 35 and 35 in the circumferential direction of the support rings 20 and 20, respectively.
- a pair of support rings 20 and 20 are spanned between each other. Accordingly, the first and second swing frames 21 and 22 are swingably supported between the column portions 35 and 35 adjacent to each other in the circumferential direction.
- first and second swing frames 21 and 22 are provided with hydraulic cylinders 36a and 36b provided between both ends of the swing frames 21 and 22 and the support rings 20 and 20, respectively. This makes it possible to swing and displace freely.
- These hydraulic cylinders 36a and 36b are respectively connected to the support rings 20 and 2 respectively. A part of 0 is provided at a position aligned with both end portions of the swing frames 21 and 22.
- rods 37a and 37b are arranged in parallel with the support shafts 34 and 34 at the ends of the first and second swing frames 21 and 22 that are aligned with the hydraulic cylinders 36a and 36b.
- the first and second swing frames 21 and 22 are supported and fixed so as to penetrate both end portions.
- a control valve 39 for controlling supply and discharge of pressure oil to and from the hydraulic cylinders 36a and 36b is supported by the support rings 20 and 20, respectively.
- the cam face 40 provided on the control valve 39 displaces the spool 42 of the control valve 39 via the plunger 41 attached to the control valve 39 to switch the control valve 39.
- the sleeve 43 that constitutes the control valve 39 together with the spool 42 is displaced to a predetermined position by the control motor 44 so that a desired gear ratio can be realized at the time of shifting.
- Such a control valve 39 and a control motor 44 are provided on the first input side disk 2 and the first output side disk 3, and one on the second input side.
- One on the second cavity 46 side which includes the disk 5 and the second output side disk 6, and two toroidal-type continuously variable transmissions 1 as a whole.
- a control motor 39 on the first cavity 45 side is provided with the control valve 39 on the first cavity 45 side, and a control valve 39 on the second cavity 46 side is provided on the control motor 44 on the second cavity 46 side.
- the control is performed in synchronization with each other (in a straight traveling state) or independently of each other (in a turning state).
- a contact ellipse formed on a rolling contact portion (traction portion) between the peripheral surface of each of the power rollers 4 and 7 and the inner surface of each of the disks 2, 5, 3, 6 is the disc 2, 5, It becomes easy to ride on the edge of 3 and 6, and each of these power rollers 4 and 7 and each disk 2, 5, 3, 6 It becomes easy to cause damage based on edge load. Such damage is undesirable because it reduces the durability of each of the power rollers 4 and 7 and the disks 2, 5, 3, and 6.
- Patent Document 1 Japanese Patent Laid-Open No. 2001-165262
- Patent Document 2 Japanese Utility Model Publication No. 6-43404
- the toroidal continuously variable transmission of the present invention has been invented to realize a structure having excellent durability by preventing the power roller from being excessively inclined in view of the above-described circumstances. is there.
- a toroidal continuously variable transmission includes an input side disk and an output side disk, a plurality of trons, and a plurality of power rollers.
- the input-side disk and the output-side disk are concentric and independent of each other with their inner surfaces facing each other, which are concave surfaces having a circular arc cross section. It is supported to roll freely.
- Each of the power rollers has a spherical convex surface, and is sandwiched between the input side disk and the output side disk in a state of being supported by the trone.
- Limiting means are provided.
- each of these trons is extended by the swing limiting means provided between each of the swing frames and each of the trons. Therefore, it is possible to prevent the power rollers supported by the respective trons from being inclined excessively. That is, in the state where each of these power rollers is greatly inclined (the transmission gear ratio of the toroidal type continuously variable transmission is greatly deviated from 1), the transmission gear ratio exceeds the predetermined value and converges to the predetermined value. Even if the overshoot tends to occur, the trunnions that support the power rollers are prevented from excessively swinging by the swing limiter.
- the contact ellipse formed at the rolling contact portion (traction portion) between the peripheral surface of each power roller supported by each trunnion and the inner surface of each disc is the disc of each disc. It is possible to ensure the durability of each power roller and each disk as well as riding on the edge.
- FIG. 1 is a cross-sectional view of a main part showing Embodiment 1 of the present invention.
- FIG. 2 A view taken along arrow A with the portion omitted.
- FIG. 3 Stow-back member, (A) with the surface facing the end surface of the trunnion facing upward, (B) with the end The perspective view which each shows the surface facing the inner surface of a board on the upper side.
- ⁇ 4 A view similar to FIG. 2, showing Embodiment 2 of the present invention.
- FIG. 6 is a cross-sectional view taken along the line BB in FIG.
- the swing limiting means is constituted by a convex portion and a concave portion.
- These convex portions and concave portions are respectively provided on the end surfaces of the pivots provided at both ends of each troon and the inner surfaces of the swing frames facing the respective end surfaces (the end surfaces of the pivot and the inner surfaces of the swing frames). It does not matter which of the projections or depressions is provided).
- the convex portion is combined with the concave portion in such a manner that the displacement (displacement relative to the swing direction of each of these trons) can be inserted.
- the side surfaces of the convex portions and the inner surface of the concave portions are brought into contact with each other based on the swinging of the trons, thereby preventing the trunnions from swinging more than a predetermined amount.
- resistance between the side surface of the convex portion and the inner surface of the concave portion is a resistance to the swing of the trunnion.
- Resistance means in other words, resistance means (damper means) for applying a damping force (damping force) to the above-described trunnion is provided.
- the lubricating oil introduced into the space constituted by the side surface of the convex portion and the inner surface of the concave portion is removed from this space based on the displacement of the convex portion. It shall have a configuration for entering and exiting.
- the resistance means is configured by sandwiching an elastic member between the side surface of the convex portion and the inner surface of the concave portion facing each other.
- FIGS. 1 to 3 show Embodiment 1 of the present invention corresponding to claims 1 to 4.
- FIG. The feature of the present invention is that the (first and second) power rollers 4 (7) supported by the (first and second) trunnions 30 (31) are prevented from being inclined excessively.
- the first and second) are to ensure the durability of the power rollers 4 (7) and (first and second) the input side and output side disks 2, 5, 3, 6 (see FIG. 5). Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 5 to 8, the overlapping illustrations and explanations are omitted or simplified, and the structure of the parts shown in FIGS. The operation will be described. In the following explanation, “first” and “second” of the first and second members indicating that the cavities are different will be omitted.
- Each swing frame 21 (22) is supported by the support frame 23 (24) via the support shaft 34 (see FIGS. 5 to 8).
- the end plates 48, 48 are connected and fixed by screws 49, 49.
- the pivots 33 and 33 provided on the shaft are supported only in a swinging manner in a state where axial displacement is prevented. For this reason, in the case of the present embodiment, between the inner peripheral surface of each of the circular holes 51 and 51 and the outer peripheral surface of each of the pivot shafts 33 and 33, the radial-one dollar bearing 52, 52 and the thrust-one dollar bearing. 53 and 53 are provided.
- needle bearings 52 and 53 In order to arrange these needle bearings 52 and 53 concentrically, they are fitted and fixed to the outer peripheral surfaces of the outer rings 54 and 54 of the needle bearings 52 and 53 and the circular holes 51 and 51, respectively.
- the inner circumferential surfaces of the spacers 55 and 55 are spherically fitted.
- the both needle bearings 52, 53 are arranged between the outer rings 54, 54, which are aligned in this way, and the inner rings 76, 76 fitted on the outer peripheral surfaces of the pivots 33, 33.
- Each is composed of several dollars.
- each trunnion 30 (31) is supported in an intermediate manner between each trunnion 30 (31), which is supported by the respective swing frames 21 (22) so that only the swing displacement about the pivots 33 and 33 is freely supported.
- the base half portion of the displacement shaft 32a is supported on the portion so as to be swingable and displaceable.
- each of these traons 30 (31) A circular hole 56 is formed in an intermediate portion of the trunnion 30 (31) so as to penetrate both inner and outer peripheral surfaces.
- Each of the circular holes 56 has a stepped shape in which a large-diameter portion 57 on the inner surface side and a small-diameter portion 58 on the outer surface side of each of the above-described trolons 30 (31) are continuously connected by a step portion 59.
- the displacement shaft 32a formed integrally with the outer ring 61 constituting the angiular thrust ball bearing 60 is rotatably supported by the radial-dollar bearing 62 in such a circular hole 56.
- a thrust needle bearing 63 is provided between the outer side surface of the outer ring 61 and the inner side surface of each of the truons 30 (31), and the outer ring 61 and the power inlet 4 around the displacement shaft 32a.
- the displacement of (7) can be performed smoothly.
- the thrust roller bearing 60 and another radial-single bearing 64 support the power roller 4 (7) rotatably around the front half of the displacement shaft 32a.
- each trunnion 30 (31) swings more than a predetermined amount between each swing frame 21 (22) and each trunnon 30 (31).
- Oscillation limiting means 65, 65 are provided to prevent this.
- each of the swing restricting means 65, 65 is constituted by a pair of convex portions 66, 66 and a pair of concave portions 67, 67, respectively. That is, on the inner side surfaces of the end plates 48 and 48 coupled and fixed to both ends of the swing frames 21 (22), the pivots 33 and 33 provided on both ends of the trone 30 (31) are provided.
- a bottomed concave hole 68, 68 is provided in a portion facing the end surface of the base plate in a state where the inner surface force is also recessed.
- the concave portions 67 and 67 each having a fan-like opening are provided at two positions on the opposite sides in the radial direction of the concave holes 68 and 68, respectively.
- the partition members 69 and 69 are fitted in the respective recessed hole portions 68 and 68 in a state in which the rotation in the respective recessed portions 68 and 68 is prevented.
- the respective recesses 67 and 67 are constituted by the portions surrounded by the side surfaces of the members 69 and 69 and the inner surfaces (inner peripheral surface and bottom surface) of the recessed hole portions 68 and 68.
- the partition members 69 and 69 are displaced in the circumferential direction of the recessed hole portions 68 and 68 in a state where they are engaged with the engaging recessed portions 70 and 70 provided on the bottom surfaces of the recessed hole portions 68 and 68. Is prevented.
- the outer peripheral surfaces of the partition members 69 and 69 are fitted into the inner peripheral surfaces of the concave holes 68 and 68, so that the partition members 69 and 69 are in the radial direction of the concave holes 68 and 68. Is prevented from displacement.
- cooling and lubrication of the thrust ball bearing 60 and the radial-dollar bearings 62 and 64 are provided at the center of the partition members 68 and 68.
- a first oil passage 71 is provided to supply the lubricating oil to the required part, and the lubricating oil is supplied and discharged into the recesses 67 and 67 on the radially outer side of the first oil passage 71.
- Second oil passages 72, 72 are provided for this purpose.
- the recessed holes 68, 68 provided on the inner surfaces of the end plates 48, 48 at the end surfaces of the pivots 33, 33 provided at both ends of the respective trone 30 (31).
- An annular stopper member 73 is fixed at a position opposite to. As shown in detail in FIG. 3, the stopper member 73 projects the convex portions 66, 66 and the locking convex portions 75, 75 on both side surfaces in the axial direction of the disc portion 74 from the respective side surfaces in the axial direction. Each is provided in a state.
- Each of the convex portions 66, 66 is a radially outward portion of one side surface of the disk portion 74 (the lower side surface of Fig.
- the stopper member 73 is locked to each of the trough-on by locking the locking protrusions 75, 75 into locking recesses (not shown) formed on the end surfaces of the pivots 33, 33. It is fixed to both ends of the 30 (31) in a state in which relative rotation with respect to this Trion 30 (31) is prevented. In this state, the convex portions 66 and 66 are inserted into the concave portions 67 and 67 so as to be able to be displaced in the swing direction of the trunnions 30 (31).
- the side surfaces of the projections 66 and 66 come into contact with the side surfaces of the partition members 69 and 69 on the inner surfaces of the recesses 67 and 67 based on the swing of each of the trolons 30 (31). This prevents each of these TR-ONs 30 (31) from swinging more than a predetermined amount.
- the protrusions 66, 66 are inserted into the recesses 67, 67, and the displacement of the trol-on 30 (31) in the swinging direction is changed. As long as the side surface does not abut against the inner surface of the recesses 67, 67, it is allowed.
- the side surfaces of the convex portions 66 and 66 are abutted on the basis of the distance between the side surfaces of the convex portions 66 and 66 and the inner surface of the concave portions 67 and 67 based on the swing of the trunnions 30 (31).
- each of these trunnions 30 (31) and eventually each of these trunnions 30 (31) The inclination angle of each of the supported power rollers 4 (7) can be regulated within a desired range.
- the swing limiting means 65, 65 provided between each swing frame 21 (22) and each trol-on 30 (31), that is, Due to the convex portions 66 and 66 and the concave portions 67 and 67, the respective trolons 30 (31) and the respective power rollers 4 (7) supported by the respective truons 30 (31) are excessively inclined. Can be prevented.
- the predetermined ratio is exceeded after the transmission ratio exceeds a predetermined value.
- the trunnion 30 (31) that supports the power rollers 4 (7) has the side surfaces of the convex portions 66, 66 on the side surfaces of the concave portions 67, 67.
- the partition members 69 and 69 which are the inner surfaces of the inner surface, further swinging is prevented. Therefore, the rolling contact portion between the peripheral surface of each of the power rollers 4 (7) supported by each of the trons 30 (31) and the inner surface of each of the input side and output side disks 2, 5 (3, 6).
- the contact ellipse formed in the (traction part) does not run on the edge of each of these disks 2, 5 (3, 6).
- Each of these power rollers 4 (7) and each disk 2, 5 (3, 6) Durability.
- the power rollers 4 ( Each trunnion 30 (31) supporting 7) is prevented from excessively swinging based on the force. For this reason, such hunting is less likely to occur, and it is possible to prevent a decrease in transmission efficiency, an increase in vibration, and a decrease in running stability.
- the force (damping force, damping force) applied to each trol-on 30 (31) via the respective convex portions 66, 66 is the same as that of the second oil passages 72, 72.
- the desired values can be regulated.
- FIG. 4 shows a second embodiment of the present invention corresponding to claims 1 to 3 and 5.
- the side surfaces of the convex portions 66, 66 provided on the stopper member 73 and the concave portions 67, 67 provided on the end plate 48 constituting the swing frame 21 (see FIG. 1).
- resistance means is provided that provides resistance to the swinging of the trolley 30 (see FIG. 1).
- the lubricating oil is placed in the space formed by the side surfaces of the convex portions 66 and 66 and the inner surfaces of the concave portions 67 and 67. not filled.
- the second oil passages 72 and 72 are not provided in the cutting member 69 constituting the recesses 67 and 67.
- Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112005001589T DE112005001589B4 (en) | 2004-07-06 | 2005-06-28 | Continuously variable transmission of the toroidal type |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004198755A JP4774694B2 (en) | 2004-07-06 | 2004-07-06 | Toroidal continuously variable transmission |
JP2004-198755 | 2004-07-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006003886A1 true WO2006003886A1 (en) | 2006-01-12 |
Family
ID=35782693
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/011831 WO2006003886A1 (en) | 2004-07-06 | 2005-06-28 | Toroidal type stepless speed change device |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP4774694B2 (en) |
CN (1) | CN100460715C (en) |
DE (1) | DE112005001589B4 (en) |
WO (1) | WO2006003886A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013044412A (en) * | 2011-08-25 | 2013-03-04 | Nsk Ltd | Toroidal continuously variable transmission |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130035200A1 (en) * | 2011-02-03 | 2013-02-07 | Nsk Ltd | Toroidal continuously variable transmission |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11257449A (en) * | 1998-03-12 | 1999-09-21 | Nissan Motor Co Ltd | Toroidal type continuously variable transmission |
JP2001165262A (en) * | 1999-12-06 | 2001-06-19 | Nsk Ltd | Toroidal type continuously variable transmission |
JP2003083410A (en) * | 2001-07-05 | 2003-03-19 | Nissan Motor Co Ltd | Full toroidal type continuously variable transmission |
JP2003336707A (en) * | 2002-05-20 | 2003-11-28 | Nissan Motor Co Ltd | Trunnion link connection structure in toroidal continuously variable transmission and method of assembly |
JP2003336708A (en) * | 2002-05-20 | 2003-11-28 | Nsk Ltd | Trunnion of toroidal continuously variable transmission and toroidal continuously variable transmission |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5768881U (en) * | 1980-10-14 | 1982-04-24 | ||
JP2591441Y2 (en) * | 1992-11-12 | 1999-03-03 | 日本精工株式会社 | Toroidal type continuously variable transmission |
JP3355941B2 (en) * | 1996-07-16 | 2002-12-09 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
JP3711688B2 (en) * | 1997-03-22 | 2005-11-02 | マツダ株式会社 | Toroidal continuously variable transmission |
JP3624367B2 (en) * | 1999-12-09 | 2005-03-02 | 日産自動車株式会社 | Toroidal continuously variable transmission |
JP2002295618A (en) * | 2001-04-03 | 2002-10-09 | Koyo Seiko Co Ltd | Toroidal continuously variable speed transmission |
JP2003021210A (en) * | 2001-07-10 | 2003-01-24 | Nsk Ltd | Toroidal type continuously variable transmission and continuously variable transmission device |
JP2004003594A (en) * | 2002-01-25 | 2004-01-08 | Makoto Kida | Turning mechanism for turning member and turned base member |
KR100867108B1 (en) * | 2002-09-19 | 2008-11-06 | 삼성전자주식회사 | Installation Equipment for Display and Jig for Installation Equipment |
DE102004006445B4 (en) * | 2004-02-03 | 2006-02-02 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Variator for a toroidal transmission |
-
2004
- 2004-07-06 JP JP2004198755A patent/JP4774694B2/en not_active Expired - Fee Related
-
2005
- 2005-06-28 WO PCT/JP2005/011831 patent/WO2006003886A1/en active Application Filing
- 2005-06-28 DE DE112005001589T patent/DE112005001589B4/en not_active Expired - Fee Related
- 2005-06-28 CN CNB2005800230036A patent/CN100460715C/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11257449A (en) * | 1998-03-12 | 1999-09-21 | Nissan Motor Co Ltd | Toroidal type continuously variable transmission |
JP2001165262A (en) * | 1999-12-06 | 2001-06-19 | Nsk Ltd | Toroidal type continuously variable transmission |
JP2003083410A (en) * | 2001-07-05 | 2003-03-19 | Nissan Motor Co Ltd | Full toroidal type continuously variable transmission |
JP2003336707A (en) * | 2002-05-20 | 2003-11-28 | Nissan Motor Co Ltd | Trunnion link connection structure in toroidal continuously variable transmission and method of assembly |
JP2003336708A (en) * | 2002-05-20 | 2003-11-28 | Nsk Ltd | Trunnion of toroidal continuously variable transmission and toroidal continuously variable transmission |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013044412A (en) * | 2011-08-25 | 2013-03-04 | Nsk Ltd | Toroidal continuously variable transmission |
Also Published As
Publication number | Publication date |
---|---|
JP2006022828A (en) | 2006-01-26 |
CN100460715C (en) | 2009-02-11 |
JP4774694B2 (en) | 2011-09-14 |
DE112005001589B4 (en) | 2010-08-26 |
CN1997841A (en) | 2007-07-11 |
DE112005001589T5 (en) | 2007-06-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP3666879B2 (en) | Toroidal continuously variable transmission for four-wheel drive vehicles | |
WO2008001690A1 (en) | Toroidal type stepless transmission and stepless transmission | |
JP4190117B2 (en) | Toroidal continuously variable transmission | |
WO2006003886A1 (en) | Toroidal type stepless speed change device | |
WO2006003887A1 (en) | Toroidal type continuously variable transmission for four-wheel drive car | |
JP4172890B2 (en) | Half toroidal continuously variable transmission | |
JP4204157B2 (en) | Toroidal continuously variable transmission for four-wheel drive vehicles | |
JP5141668B2 (en) | Toroidal continuously variable transmission | |
JP4172889B2 (en) | Toroidal continuously variable transmission | |
JP4513391B2 (en) | Toroidal continuously variable transmission | |
JP4492007B2 (en) | Toroidal continuously variable transmission and continuously variable transmission | |
JP4815785B2 (en) | Toroidal continuously variable transmission | |
JP2003021210A (en) | Toroidal type continuously variable transmission and continuously variable transmission device | |
JP5177576B2 (en) | Toroidal continuously variable transmission | |
JPH08135746A (en) | Toroidal type continuously variable transmission | |
JP2000193057A (en) | Toroidal type continuously variable transmission | |
JP4144166B2 (en) | Continuously variable transmission for pumping pump or generator | |
JP4158320B2 (en) | Continuously variable transmission | |
JP2576534Y2 (en) | Toroidal type continuously variable transmission | |
JP4222009B2 (en) | Continuously variable transmission | |
JP2000240748A (en) | Toroidal type continuously variable transmission | |
JP5796308B2 (en) | Toroidal continuously variable transmission | |
JP2001165264A (en) | Toroidal type continuously variable transmission | |
US20030032522A1 (en) | Toroidal-type continuously variable transmission | |
JP2006017144A (en) | Toroidal type continuously variable transmission |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KM KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NG NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 200580023003.6 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120050015890 Country of ref document: DE |
|
RET | De translation (de og part 6b) |
Ref document number: 112005001589 Country of ref document: DE Date of ref document: 20070628 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase | ||
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8607 |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8607 |