WO2005100821A1 - トロイダル型無段変速機 - Google Patents
トロイダル型無段変速機 Download PDFInfo
- Publication number
- WO2005100821A1 WO2005100821A1 PCT/JP2005/007234 JP2005007234W WO2005100821A1 WO 2005100821 A1 WO2005100821 A1 WO 2005100821A1 JP 2005007234 W JP2005007234 W JP 2005007234W WO 2005100821 A1 WO2005100821 A1 WO 2005100821A1
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- WIPO (PCT)
- Prior art keywords
- traverses
- continuously variable
- toroidal
- variable transmission
- type continuously
- 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
- 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
- a toroidal-type continuously variable transmission according to the present invention is used, for example, as a transmission unit constituting an automatic transmission for a vehicle (automobile).
- Toroidal-type continuously variable transmissions have been studied as transmissions for automobiles, and some of them have been implemented in power transmissions.
- automatic transmissions for four-wheel drive vehicles incorporating a large and large torque generating engine are incorporated.
- a structure suitable for a transmission unit of a device is described in Patent Document 1, for example, and a conventional force is also known.
- 7 to 10 show a toroidal-type continuously variable transmission disclosed in Patent Document 1 for a large displacement four-wheel drive vehicle.
- This toroidal type continuously variable transmission 1 has three first power ports 4 and 4 between a first input side disk 2 and a first output side disk 3 and a second input side disk 5 and a second input side disk 5.
- Three second power rollers 7 are provided between the two output discs 6, respectively, and power is transmitted by a total of six power rollers 4, 7.
- a torque converter 8 as a starting clutch is provided at the foremost part in the power transmission direction, and the output of the torque converter 8 is connected to the toroidal-type continuously variable transmission.
- the first half 9a of the input shaft 9 constituting 1 is incorporated.
- the first half 9a is rotationally driven by the torque converter 8 with the rotation of a traveling engine (not shown).
- the rear half 9b of the input shaft 9 is supported on the rear end of the front half 9a concentrically and rotatably relative to each other.
- a forward / reverse switching unit 10 for switching between forward and backward is provided in series with respect to the power transmission direction.
- the forward / reverse switching unit 10 which is a planetary gear mechanism, switches between a forward state and a reverse state by selectively connecting and disconnecting a forward clutch 11 and a reverse clutch 12, each of which is a wet multi-plate clutch. .
- the above-mentioned toe is provided at the rear side of the forward / reverse switching unit 10 as described above.
- a toroidal type continuously variable transmission 1 is provided.
- the speed change ratio between is continuously changed.
- the toroidal-type continuously variable transmission 1 is provided around the rear half 9b.
- the first and second input side disks 2 and 5 are concentric with each other in the vicinity of both front and rear ends of the rear half 9b, with the inner surfaces each having a concave surface having an arc-shaped cross section facing each other. And rotatably supported in synchronization with each other.
- the first input side disk 2 provided on the front side (the left side in FIG. 7) is spline-engaged with the base end of the carrier 15 constituting the forward / reverse switching unit 10, and Movement is blocked.
- the second input side disk 5 provided on the rear side (the right side in FIG. 7) is supported at the rear end of the rear half 9b via a ball spline 16. Then, the second input-side disc 5 is directed to the first input-side disc 2 and can be freely pressed by a hydraulic type reading device 17.
- a support cylinder 18 is provided concentrically with the rear half 9b around the middle of the rear half 9b. Both ends of the support cylinder 18 are supported and fixed by inner ends of the stays 19 and 19 on the inner diameter side. These stays 19, 19 support and fix their outer diameter ends to support rings 20, 20, which will be described later.
- the first and second support frames 23 and 24 for supporting the present position are configured.
- the rear half 9b is supported inside the support tube 18, and the first and second output disks 3, 6 are supported around the support tube 18 so as to be freely rotatable and axially displaceable. I have. Further, the two output side disks 3 and 6 are rotatable relative to each other while supporting axial loads applied to each other by a thrust bearing provided therebetween.
- a front wheel output gear 25 is fixed to the outer surface of the first output side disc 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 first output side disk 3 allows the front wheel drive shaft 13 to be rotatably driven.
- 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 of the second output disk 6, and the rear wheel output gear 28 and the rear wheel drive shaft 14 are connected to each other.
- the second output side disk 6 allows the rear wheel drive shaft 14 to rotate freely. Further, the rotation of the rear wheel drive shaft 14 can be transmitted to the rear wheel (also not shown) via a rear differential gear (not shown).
- first power rollers 4, 4 are provided between the inner surface of the first input side disk 2 and the inner surface of the first output side disk 3, and the second input side disk 3
- the three second power rollers 7 are sandwiched between the inner surface of the second output disk 5 and the inner surface of the second output disk 6.
- These first and second power rollers 4 and 7 are provided on the inner surfaces of the first and second traverses 30 and 31, respectively. It is rotatably supported around.
- the first and second traverses 30, 31 do not intersect with the center axis of each of the discs 2, 5, 3, and 6 provided concentrically at both ends thereof.
- the first and second pivots 33 (the second pivots are not shown) that exist in the twisted position that is at a right angle or near the right angle to the direction of the central axis of 2, 5, 3, and 6 Rocking around.
- the first and second traverses 30 and 31 are supported at both ends of the first and second swing frames 21 and 22 so as to be swingable.
- first and second swing frames 21 and 22 are placed between the support rings 20 and 20 constituting the first and second support frames 23 and 24, respectively.
- the discs 2, 5, 3, and 6 are supported so that they can swing freely about support shafts 34, 34 provided in a direction parallel to or nearly parallel to the central axes of the discs 2, 5, 3, and 6.
- the first and second support frames 23 and 24 each include a pair of support rings 20 and 20 arranged in parallel with each other, outside the three support portions 35 and 35 constituting the stay 19. They are connected to each other via radial ends.
- the support shafts 34, 34 constitute the first and second support frames 23, 24 at intermediate positions between the support portions 35, 35 in the circumferential direction of the support rings 20, 20, respectively.
- a pair of support rings 20 and 20 are bridged between each other. Therefore, the first and second swing frames 21 and 22 are swingably supported between the support portions 35 and 35 adjacent in the circumferential direction.
- first and second swing frames 21 and 22 are provided with hydraulic cylinders 36a and 36b provided between both end portions of the swing frames 21 and 22 and the support rings 20 and 20, respectively. This allows swing displacement.
- These hydraulic cylinders 36a, 36b are respectively connected to the support rings 20, 2, respectively. It is provided at a position corresponding to both ends of each of the swing frames 21 and 22 as a part of 0.
- rods 37a and 37b are provided at both ends of the first and second swing frames 21 and 22 at portions corresponding to the hydraulic cylinders 36a and 36b, respectively, in parallel with the support shafts 34 and 34.
- the first and second swing frames 21 and 22 are supported and fixed so as to penetrate both ends thereof.
- the pistons 38a and 38b fitted to the hydraulic cylinders 36a and 36b are engaged with the rods 37a and 37b.
- two hydraulic cylinders 36a, 36b are provided for each of the swing frames 21 and 22 (two for each swing frame, four for each toroidal-type continuously variable transmission 1 in total). Of these, one hydraulic cylinder 36a (36b) provided at one end in the longitudinal direction of each of the swing frames 21 and 22 is extended, and the other hydraulic cylinder 36b (36a) is contracted.
- the moving frames 21 and 22 are displaced by a predetermined amount in a predetermined direction.
- a control valve 39 for controlling the 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 surface 40 provided on the control valve 39 displaces a spool 42 of the control valve 39 via a plunger 41 attached to the control valve 39, thereby switching the control valve 39.
- the sleeve 43 constituting the control valve 39 together with the spool 42 is displaced to a predetermined position by a control motor 44 so that a desired gear ratio can be realized during gear shifting.
- control valve 39 and control motor 44 are provided on the first cavity 45 side including the first input side disk 2 and the first output side disk 3, and the second input side disk 5 and the second One is provided on the second cavity 46 side including the two output side discs 6, and two are provided in the entire toroidal type continuously variable transmission 1.
- the control valve 39 of the first cavity 45 is controlled by the control motor 44 of the first cavity 45
- the control valve 39 of the second cavity 46 is controlled by the control motor 44 of the second cavity 46.
- the first and second swing frames 21 and 22 are moved by the support shafts 34 and 22 based on the supply and discharge of hydraulic oil to and from the hydraulic cylinders 36a and 36b. Centered on the 34 Then, it swings and displaces by a predetermined amount in a predetermined direction. As a result, the first and second traverses 30, 31 supported by the swing frames 21, 22 make an arc movement (swivel movement) around the support shafts 34, 34. .
- the first and second traverses 30 and 31 are pivotally supported by the first and second swing frames 21 and 22 with the change in the direction of the force. It swings in the opposite directions about each pivot 33, and the contact position between the peripheral surface of each of the first and second power rollers 4 and 7 and each of the inner surfaces changes, so that the first and second power rollers 4 and 7 change.
- the rotation speed ratio between each input side disk 2, 5 and the first and second output side disks 3, 6 changes.
- the first and second input-side disks 2, 5 that rotate in synchronization with the rear half 9b of the input shaft 9 are synchronized with each other.
- the front wheel drive shaft 13 is driven to rotate by the power transmitted from the first input side disk 2 to the first output side disk 3 via the first power rollers 4 and 4.
- the rear wheel drive shaft 14 is rotationally driven by the power transmitted from the second input side disk 5 to the second output side disk 6 via the second power rollers 7.
- Patent Document 2 In the case of a structure in which the gear ratio is changed by causing the first and second swing frames 21 and 22 to move in an arc (swivel movement), Patent Document 2
- the first and second traverses 30, 31 are in the axial direction of the pivots 33, 33, compared to the structure in which the gear ratio is changed by directly displacing the traions with an actuator, as described in It becomes easy to rattle. Then, based on such rattling of each of the traverses 30, 31 and the difference in the amount of rattling of each of the traverses 30, 31, an unintended gear shifting operation or each of the power rollers 4, 7 is performed. There is a possibility that poor synchronization of the speed ratio of the vehicle may occur or the speed ratio control may become unstable.
- the torque transmission direction changes based on the no-load state where torque is not transmitted between the input side and output side disks 2, 5, 3, and 6, the engine brake, and the like.
- each of the traverses 30, 31 is displaced from one side in the axial direction to the other side or from the other side to one side due to the play.
- Such unnecessary axial displacement of the traverses 30 and 31 causes unintended gear shifting operation, and based on the difference in the amount of play of each of the traverses 30 and 31,
- Each power outlet within the same cavity 45, 46 There is a possibility that gear ratio synchronization failure may occur between the rollers 4 and 7, or the gear ratio control may become unstable.
- Japanese Patent Application No. 2003-32793 which discloses a method for preventing poor gear ratio synchronization and unstable gear ratio control, discloses two separate parts, a traverse and a displacement shaft.
- a power roller unit including a power roller, a thrust bearing, a driving frame, a support shaft, and a radial bearing is assembled in a positional relationship after the assembly is completed in an assembled state.
- each of the power rollers 4, 7 has a rolling contact portion (traction portion) between its peripheral surface and the inner surface of both the input side and output side disks 2, 3, 5, 6 based on the applied force. And a large axial load (thrust load) in the direction toward the inner surface of each of the traverses 30 and 31. Then, due to this axial load, each of the traverses 30, 31 is elastically deformed (radiated) in a direction in which the inner surface is concave.
- Patent Document 1 JP 2001-165262 A
- Patent Document 2 JP-A-11-153203
- the toroidal type continuously variable transmission of the present invention suppresses rattling in the axial direction of the traverse's pivot shaft based on the assembling clearance, thereby preventing poor synchronization or change in gear ratio.
- the present invention has been made to realize a structure that can prevent the speed ratio control from becoming unstable. Means for solving the problem
- the toroidal-type continuously variable transmission of the present invention includes an input-side disk and an output-side disk, a plurality of traverses, and a plurality of power rollers.
- the input-side disk and the output-side disk are rotatably supported concentrically and independently of each other, with the respective inner surfaces, each having a concave surface having an arc-shaped cross section, facing each other. .
- Each of the traverses swings about a pivot that is twisted with respect to the center axis of the input side disk and the output side disk.
- Each of the power rollers has a spherical convex surface on its peripheral surface, and is sandwiched between the input-side disk and the output-side disk while being supported by each of the traverses.
- each of the traverses is disposed between the swing frame and each of the traverses with respect to the axial direction of the pivot of each of the traverses. Is provided.
- each swing frame The biasing means provided between the traverse and each traion presses the traverse to one side in the axial direction of the pivot, so that it is possible to prevent the traverse from rattling in the axial direction of the pivot.
- the force by which the urging means presses each of the traverses to one side is the force by which the respective traverses are pressed to the other based on the torque when the direction of torque transmission changes based on engine braking or the like. Larger than By regulating the pressing force of the urging means in this way, even when the above-described torque transmission direction changes, each of the traverses does not displace in the axial direction of the pivot.
- FIG. 1 is a sectional view similar to FIG. 9, but showing a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the main part.
- FIG. 3 is a diagram showing a relationship between a gear ratio and a tilt angle of a power roller, wherein (A) shows a case of a conventional structure, and (B) shows a case of the present embodiment.
- FIG. 4 is a sectional view similar to FIG. 2, but showing a second embodiment of the present invention.
- FIG. 5 is a sectional view similar to FIG. 1, but showing a third embodiment of the present invention.
- FIG. 6 is a sectional view of the main part.
- FIG. 7 is a cross-sectional view showing one example of a conventional structure.
- FIG. 8 is a sectional view taken along line A—A in FIG. 7.
- FIG. 9 is a sectional view taken along line BB of FIG.
- FIG. 10 is a cross-sectional view showing a portion substantially the same as that of FIG. 9 cut along a plane including the central axis of a first pivot provided at both ends of the first traverse.
- the biasing means is constituted by providing a viscous material between the axial end surface of the pivot and the inner surface of the swing frame facing the end surface. 2) or a piston provided on the axial end surface of the pivot is fitted oil-tight to a cylinder provided on the inner surface of the swing frame, and pressure oil is introduced into this cylinder. (The structure described in claim 3).
- the urging means is provided outside the rolling bearing for supporting the trunnion on the swing frame so as to swing freely.
- the elastic member is provided between the ring or a member supporting the outer ring and the inner surface of the swing frame facing the end surface of the outer ring or the member.
- the rolling bearing is a radial needle bearing and a thrust needle bearing having the same outer ring.
- the member supporting the outer ring is a spacer for spherically fitting the outer ring. Then, the elastic material is provided between the spacer and the inner surface of the swing frame facing the end surface of the spacer.
- FIG. 1 and 2 show a first embodiment of the present invention, which corresponds to claims 1 and 2.
- FIG. The feature of the present invention is that the (first, second) trunnion 3 supported by the (first, second) swing frame 21 (22) is provided.
- 0 (31) is prevented from rattling in the axial direction of the pivots 33, 33, and (1st, 2nd) poor synchronization of the speed ratio of each of the power rollers 4 (7) occurs, and the toroidal type This is to prevent the gear ratio control of the continuously variable transmission from becoming unstable.
- the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 7 to 10 described above, overlapping drawings and explanations are omitted or simplified, and the structure of the parts shown in FIGS. And its effects. In the following description, "first" and “second” of the first and second members indicating different cavities will be omitted.
- Each of the swing frames 21 (22) is formed by fixing a pair of end plates 48, 48 to both end surfaces of a substantially U-shaped main body 47 with screws 49, 49.
- the pivots 33, 33 provided are supported so as to be able to swing only while preventing displacement in the axial direction. For this reason, in the case of the present embodiment, the radial-dollar bearings 52, 52 and the thrust are provided between the inner peripheral surfaces of the circular holes 51, 51 and both ends of the traverses 30 (31). Needle bearings 53 and 53 are provided.
- the needle bearings 52, 53 are internally fitted and fixed to the outer peripheral surfaces of the outer rings 54, 54 and the circular holes 51, 51, respectively.
- the inner peripheral surfaces of the spacers 55 and 55 are spherically fitted.
- the two needle bearings 52, 53 are provided with the outer races 54, 54 having the centering properties in this manner, the both end surfaces of the traverses 30 (31), and the outer peripheral surfaces of the pivots 33, 33. In between, a plurality of dollars are arranged.
- a cylindrical bottomed hole 57 for supporting the displacement shaft 32a is formed on the inner side surface. The direction of the center axis of the concave hole 57 is perpendicular to the axial direction of each of the pivots 33, 33.
- the displacement shaft 32a integrally formed with the outer ring 59 forming the angular thrust ball bearing 58 is rotatably supported by a radial-dollar bearing 60.
- a thrust-dollar bearing 61 is provided between the outer surface of the outer ring 59 and the inner surface of each of the traverses 30 (31), and the outer ring 59 and the power roller 4 centered on the displacement shaft 32a. (7) The displacement of can be performed smoothly.
- these traverses 30 (31) are connected between the respective swing frames 21 (22) and the respective traverses 30 (31) by the respective pivots 33. , 33 are provided in the axial direction.
- the urging means 62 is connected to the axial end face of one of the pivots 33, 33 (left side in FIG. 2) of the pivot 33, and the swing frame facing the end face. 21
- the structure is made by providing a conductive material 63 between the inner surface of (22).
- a concave hole 64 is provided in a portion opposed to the end surface of the pivot 33 so that the inner surface force is also recessed. Then, between the bottom surface of the concave hole 64 and the sliding member 65 provided on the end surface of the pivot 33, the above-mentioned elastic material 63 (a disk spring in this embodiment) such as a disk spring or a compression coil spring is provided.
- the elastic material 63 applies a force to the trunnions 30 (31) in a direction away from the one end plate 48 in the axial direction of the pivots 33, 33.
- the trunnions are determined based on the torque.
- the force is larger than the pressing force (to the other side in the axial direction of the pivots 33, 33).
- the sliding member 65 slides (smoothly slides) with respect to the elastic member 63. It swings with Tranion 30 (31).
- the sliding member 65 is made of a material that minimizes the frictional force in the swinging direction acting on the contact surface with the flexible member 63 as much as possible. ON 30 (31) to prevent hindering the swinging and to prevent wear of the reinforced material 63!
- the flexible member 63 constituting the urging means 62 is connected to the traverses 30 (31) by the pivots 33, 33. Press one side in the axial direction of. Therefore, it is possible to prevent these traverses 30 (31) from rattling in the axial direction of the pivots 33, 33.
- the direction in which torque is transmitted is changed by the elastic member 63 pressing one of the traverses 30 (31) to one side based on engine braking or the like, this torque is applied.
- Each of the traverses 30 (31) is made larger than the force pressed by the other based on the torque.
- the traverse 30 (31) is not displaced in the axial direction of the pivots 33, 33.
- Fig. 3 shows a non-load condition (torque) of the toroidal-type continuously variable transmission provided with the urging means 62 as described above and the toroidal-type continuously variable transmission not provided with the same.
- This shows the behavior of each of the power rollers 4 (7) in the state of no transmission.
- 3 (A) in FIG. 3 shows that the urging means 62 as described above is provided, and the speed ratio of the toroidal type continuously variable transmission and each of the trons constituting the toroidal type continuously variable transmission are shown.
- the relationship between the tilt angle of each of the supported power rollers is the same as B), and the gear ratio of the toroidal type continuously variable transmission provided with the urging means 62 as described above and this toroidal type continuously variable transmission are constituted.
- each power roller 4 (7) supported by each trunnion 30 (31) The relationship with the tilt angle of each power roller 4 (7) supported by each trunnion 30 (31) is shown.
- the horizontal axis in FIG. 3 represents the gear ratio of the toroidal-type continuously variable transmission, and the vertical axis represents the tilt angle of the power roller.
- the gears can be shifted in a state in which the tilt angles of the respective power rollers (trau-on) are close to each other.
- the urging means 62 in the case of a structure in which the urging means 62 is not provided, the speed is varied in a state where the tilt angles of the respective power rollers (trau-ons) do not match. Therefore, by providing the urging means 62 as described above, the rattling of each of the trains is suppressed, and synchronization failure of the gear ratio of each power roller occurs, or Control can be prevented from becoming unstable.
- FIG. 4 shows a second embodiment of the present invention corresponding to claims 1 and 3.
- the urging means 62a for pressing the traverse 30 (31) to one side in the axial direction of each of the pivots 33, 33 is of a hydraulic type. That is, the urging means 62a is connected to the piston 66 provided on the axial end face of one of the pivots 33, 33 (left side in FIG. 4) by the pivot frame 21 (22). Oil tightly fits into the cylinder 67 provided on the inner surface, and the hydraulic pressure It is configured by introducing (pressurizing oil) freely.
- the cylinder 67 is attached to the inner surface of one of the end plates 48a, 48 (left side in FIG.
- the force applied to each of the traverses 30 (31) based on the introduction of the hydraulic pressure is changed based on this torque when the direction of torque transmission changes based on engine braking or the like. Therefore, the force of each of the traverses 30 (31) is set to be larger than the force pressed (to the other side in the axial direction of the pivots 33, 33).
- the inner peripheral surface of the cylinder 67 and the outer peripheral surface of the piston 66 are oil-tight and easily and smoothly slide with each other (the piston 66 is easily rotated in the cylinder 67). are doing).
- FIGS. 5 to 6 show a third embodiment of the present invention corresponding to claims 1, 4, and 5.
- FIG. In the case of the first embodiment shown in FIGS. 1 and 2 described above, the sliding member 65 provided on the end face of one (left side in FIG. 2) of the pivot 33 is pressed by the elastic member 63 constituting the urging means 62. ing. That is, the sliding member 65, which is a member that swings with the traverse 30 (31), is pressed by the elastic material 63. On the other hand, in the case of the present embodiment, a member which does not swing together with the traverse 30 (31) is pressed by the elastic member 63a constituting the urging means 62b.
- the outer ring 54 constituting the radial needle bearing 52 and the thrust-dollar bearing 53 for supporting the traverse 30 (31) on the swing frame 21 (22) is spherically fitted.
- the elastic material 63a is provided between the inner surface and the inner surface.
- the recess 64a provided in the end plate 48 on one side (left side in FIG. 6) facing one end face (left end face in FIG. 6) of the spacer 55 is provided.
- the inner diameter is made larger than the inner diameter of the opening edge on one end side of the spacer 55.
- the elastic member 63a is sandwiched between the bottom surface of the concave hole 64a and one end surface of the spacer 55. Then, with the elastic member 63a sandwiched in this way, a force is applied to the traverse 30 (31) in a direction away from the one end plate 48 in the axial direction of the pivots 33, 33. I have.
- the spacer 55 corresponding to the member supporting the outer ring described in claim 4 is pressed by the elastic material 63a.
- the outer ring 54 which constitutes the radial-dollar bearing 52 and the thrust-dollar bearing 53, which also corresponds to the rolling bearing described in claim 4, can be directly pressed. .
- the traverse 30 (31) or the traverse 30 (31) is not limited to the hydraulic structure as shown in FIG. 4, for example. It is possible to press the traverse 30 (31) without directly contacting (sliding) the member swinging with (31) and the elastic member 63a. For this reason, the load on the pump for feeding pressure oil, which is a concern when using a hydraulic structure, increases the efficiency of the toroidal-type continuously variable transmission and complicates the structure. As a result, it is possible to prevent the production cost from increasing. Also, even if the traverse 30 (31) swings, the traverse 30 (31) or a member swinging together with the tralon 30 (31) slides on the elastic member 63a. These traverses 30 (31) and the elastic material 63a do not wear out. Therefore, the elastic material 63a does not change its dimensions due to such abrasion, and the elastic force of the elastic material 63a does not decrease.
- the traverse 30 (31) or a member that swings together with the traverse 30 (31) is brought into sliding contact with the conductive material, the large axial direction applied to the power roller 4 (7) Due to the elastic deformation (radius) of the traverse 30 (31) based on the load (thrust load), the traverse 30 (31) or a member swinging with the traverse 30 (31) and the elastic member There is a possibility that the material will not evenly contact (one side contact). If the traverse 30 (31) or the member swinging together with the traion 30 (31) and the elastic material come into contact with each other, the elastic material or the mating surface may be unevenly worn. there is a possibility. In contrast, in the case of the present embodiment, As described above, since the traverse 30 (31) is pressed through the spacer 55, the elastic material 63a does not hit one side, and the elastic force does not decrease due to wear.
- the swing frame 21 (22) is provided between the other end plate 48 (right side in FIG. 6) 48 and the traverse 30 (31).
- a swing limiting means 68 is provided for preventing the traverse 30 (31) from swinging more than a predetermined amount. That is, a pair of recesses 69, 69 having openings in a fan shape provided on the inner surface of the other end plate 48 are provided in the pair of recesses 69, 69 of the traverse 30 (31) (the right side in FIG. 6).
- the protrusions 71 of the stopper member 70 fixed to the end face are inserted.
- the trunnions 30 (31) are more than specified by contacting the inner surfaces of the recesses 69, 69 by the side force of the projections 71, 71 based on the swinging of the trunnions 30 (31). Stop rocking! /
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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DE112005000836T DE112005000836B4 (de) | 2004-04-15 | 2005-04-14 | Kontinuierlich verstellbares Getriebe der toroidalen Art |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2004119708 | 2004-04-15 | ||
JP2004-119708 | 2004-04-15 | ||
JP2004-318696 | 2004-11-02 | ||
JP2004318696A JP4815785B2 (ja) | 2004-04-15 | 2004-11-02 | トロイダル型無段変速機 |
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WO2005100821A1 true WO2005100821A1 (ja) | 2005-10-27 |
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PCT/JP2005/007234 WO2005100821A1 (ja) | 2004-04-15 | 2005-04-14 | トロイダル型無段変速機 |
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JP (1) | JP4815785B2 (ja) |
DE (1) | DE112005000836B4 (ja) |
WO (1) | WO2005100821A1 (ja) |
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JPH1089433A (ja) * | 1996-09-13 | 1998-04-07 | Nissan Motor Co Ltd | トロイダル型無段変速機 |
JPH10132044A (ja) * | 1996-10-31 | 1998-05-22 | Jatco Corp | トロイダル型無段変速機 |
JP2001165262A (ja) * | 1999-12-06 | 2001-06-19 | Nsk Ltd | トロイダル型無段変速機 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4444068A (en) * | 1982-01-26 | 1984-04-24 | Excelermatic Inc. | Infinitely variable traction roller transmission |
US4576055A (en) * | 1984-08-15 | 1986-03-18 | Excelermatic, Inc. | Hydraulically controlled infinitely variable traction roller transmission |
US4858484A (en) * | 1987-10-26 | 1989-08-22 | Excelermatic Inc. | Infinitely variable traction roller transmission |
JP3636414B2 (ja) * | 1997-09-30 | 2005-04-06 | 日産自動車株式会社 | トロイダル型無段変速機のトラニオン支持構造 |
JP3666216B2 (ja) * | 1997-11-21 | 2005-06-29 | 日本精工株式会社 | トロイダル型無段変速機の組立方法 |
DE10013182A1 (de) * | 2000-03-17 | 2001-09-20 | Zahnradfabrik Friedrichshafen | Stufenloses Reibradgetriebe |
-
2004
- 2004-11-02 JP JP2004318696A patent/JP4815785B2/ja not_active Expired - Fee Related
-
2005
- 2005-04-14 DE DE112005000836T patent/DE112005000836B4/de not_active Expired - Fee Related
- 2005-04-14 WO PCT/JP2005/007234 patent/WO2005100821A1/ja active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1847553A (en) * | 1930-05-15 | 1932-03-01 | Aeromarine Plane & Motor Compa | Variable speed transmission |
US3455177A (en) * | 1966-07-20 | 1969-07-15 | English Electric Co Ltd | Variable-ratio frictional drive gears |
JPH1089433A (ja) * | 1996-09-13 | 1998-04-07 | Nissan Motor Co Ltd | トロイダル型無段変速機 |
JPH10132044A (ja) * | 1996-10-31 | 1998-05-22 | Jatco Corp | トロイダル型無段変速機 |
JP2001165262A (ja) * | 1999-12-06 | 2001-06-19 | Nsk Ltd | トロイダル型無段変速機 |
Also Published As
Publication number | Publication date |
---|---|
DE112005000836T5 (de) | 2007-03-29 |
JP2005325994A (ja) | 2005-11-24 |
DE112005000836B4 (de) | 2012-07-12 |
JP4815785B2 (ja) | 2011-11-16 |
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