JP3780765B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an improvement in a toroidal type continuously variable transmission employed in a vehicle or the like.
[0002]
[Prior art]
Conventionally, a toroidal continuously variable transmission has been known as a transmission of a vehicle, for example, JP-A-10-205601.
[0003]
To explain this, as shown in FIG. 13, a pair of power rollers 20, 20 that are sandwiched and pressed by a pair of input / output disks that are coaxially supported by forming a toroidal groove on the opposing surface, The pivot shafts 24 and 24 supported at the base ends by a pair of trunnions 90 and 90 disposed with the rotary shaft 1C of the input / output disk interposed therebetween are rotatably and swingably supported. The rotary shafts 90c and 90c are supported so as to be displaceable in the axial direction and around the axis.
[0004]
Then, the hydraulic cylinders 30 and 30 connected to the lower end of the trunnion 90 drive the trunnions 90 and 90 in the axial direction, so that the power rollers 20 and 20 are rotated (referred to as tilt) around the rotation shaft 90c. The contact ratio between the disk and the output disk changes, and the gear ratio is continuously changed.
[0005]
The trunnions 90, 90 arranged opposite to each other are interconnected at the upper part by the upper link 18 and at the lower part by the lower link 19, and resist the thrust force applied to the power rollers 20, 20 against the upper link 18, the lower link 19. Keeps the distance between the rotating shafts 90c, 90c of the trunnions 90, 90 constant, and restricts the upper part of the trunnions 90, 90 from bending in the direction of the rotating shaft 1C of the input / output disk.
[0006]
The center portion of the upper link 18 is swingably supported by the upper link post 17 and is connected to a post base 116 fixed on the inner peripheral upper side of the casing 114 so as to be swingably supported. .
[0007]
On the other hand, shaft portions 92, 92 projecting from the upper portions of the trunnions 90, 90 are inserted into the through holes 18 a, 18 b provided at both ends of the upper link 18, and spherical bearings 60 provided on the outer periphery of these shaft portions 92. The trunnion 90 and the upper link 18 are connected to each other.
[0008]
The trunnions 90, 90 are displaced in the opposite axial directions by the upper link 18 that swings about the upper link post 17, and the spherical bearing 60 is allowed to rotate about the rotating shaft 90 c.
[0009]
For this reason, a spacer 93 and a snap ring 94 are provided on the upper end side of the shaft portion 92 formed on the trunnions 90, 90 in order to prevent the spherical bearing 60 from falling off.
[0010]
[Problems to be solved by the invention]
By the way, since the trunnion 90 is driven in the axial direction by the hydraulic cylinder 30, a gap L1 that is larger than the stroke of the hydraulic cylinder 30 is provided between the upper end surface of the shaft portion 92 and the inner periphery of the casing 114 or the lower surface of the post base 116. It is necessary to secure '.
[0011]
However, in the conventional toroidal-type continuously variable transmission, the shaft portion 92 protruding from the upper portion of the trunnion 90 has a spacer 93 that prevents the spherical bearing 60 from falling off, and a snap ring 94 that holds the spacer 93. Is mounted on the outer periphery of the shaft portion 92, it is necessary to protrude toward the upper side of the casing 114 (upward in FIG. 13) from the upper surface of the upper link 18.
[0012]
For this reason, the height H ′ from the rotary shaft 1C of the input / output disk to the inner periphery of the casing 114 increases by the amount that the shaft portion 92 protrudes from the upper link 18 in addition to the gap L1 ′ that is slightly larger than the stroke. As a result, there has been a problem that the transmission becomes larger and mountability on the vehicle is lowered.
[0013]
When the toroidal type continuously variable transmission shown in the conventional example is applied to an infinitely variable gear ratio continuously variable transmission disclosed in Japanese Patent Application Laid-Open No. 63-219956, as shown in FIG. The distance Lc between the rotary shaft 1C of the input / output disk of the toroidal-type continuously variable transmission serving as the first shaft and the axis 6C of the second shaft including the power circulation mode clutch 9 and the direct connection mode clutch is the upper end surface of the trunnion 90. It is set according to the size of the gap L1 ′ with the second shaft side member such as the power circulation mode clutch 9.
[0014]
For this reason, there is a problem in that the greater the height at which the shaft portion 92 projects from the upper surface of the upper link 18, the greater the inter-shaft distance Lc ', leading to an increase in the size of the transmission and lowering the mountability to the vehicle. .
[0015]
The present invention has been made in view of the above problems, and an object thereof is to promote downsizing of a toroidal-type continuously variable transmission while reliably preventing a spherical bearing from falling off.
[0017]
[Means for Solving the Problems]
1st inventionIncludes a pair of tiltable power rollers that are sandwiched between opposing surfaces of the input disk and the output disk, and pivotally supports the power rollers via a pivot shaft. A pair of trunnions displaceable around, a spherical bearing disposed at an outer peripheral position of a shaft portion formed at the end portion of the trunnion, and a spherical bearing of the shaft portion are engaged with through holes formed at both end portions. In this way, the trunnions arranged opposite to each other are connected, and a link whose center is swingably supported via a support member fixed to the casing, and an actuator for driving the pair of trunnions in opposite directions, respectively. In a toroidal type continuously variable transmission equipped with
  A screw integrally formed with a flange capable of contacting a spherical bearing is fastened to the end surface of the shaft portion exposed from the through hole of the link, and the screw is arranged offset with respect to the rotation shaft of the trunnion. Established.
[0018]
  Also,SecondThe invention ofFirstIn the invention, the screw is disposed offset from the trunnion rotating shaft to the rotating shaft side of the input / output disk.
[0019]
  Also,ThirdThe invention of the first aspectOr in the second inventionIn this case, a convex portion is formed on the surface of the flange that contacts the end surface of the shaft portion, and a groove portion that can be engaged with the convex portion is formed on the end surface of the shaft portion that faces the convex portion. .
[0020]
  Also,4thThe invention ofThirdIn the invention, the convex portion is formed in a wedge shape that is locked to the groove portion in the loosening direction of the screw, while the groove portion is provided with a tapered surface toward the fastening direction of the screw.
[0021]
  Also,5thThe first to thirteenth inventions4thIn any one of the inventions, the flange gradually increases in thickness from the outer periphery toward the inner periphery.
[0024]
【The invention's effect】
FirstIn the invention, the trunnion rotates around the axis due to the tilting of the power roller, and slip occurs between the spherical bearing rotating with the link and the flange of the screw, and the screw is loosened depending on the rotation direction of the trunnion. Although torque may be applied in the direction, the tightening position of the screw is offset with respect to the rotation axis of the trunnion, so that the torque in the loosening direction applied to the screw can be reduced. It is possible to prevent the spherical bearing from falling off.
  In addition, since the screw formed integrally with the flange is fastened to the end face of the shaft portion exposed from the through hole of the link, the shaft portion is linked to assemble the spacer and the snap ring as in the conventional example. It is no longer necessary to project from the upper surface, and the height of the casing can be reduced to improve the mountability to the vehicle. If the infinitely variable transmission is configured with the toroidal continuously variable transmission, the trunnion shaft Since the protrusion amount of the portion is reduced, the distance between the adjacent shafts can be reduced, and the transmission can be reduced in size and weight.
[0025]
  Also,SecondThis invention offsets the tightening position of the screw to the rotating shaft side of the input / output disk with respect to the rotating shaft of the trunnion, thereby reducing the torque in the loosening direction applied to the screw and shifting the screw hole for screwing the screw. Set inside the machine, trunnion can secure enough thickness on the way from the pivot shaft side to the shaft part without tightening the screw while tightening the screw on the end surface of the shaft part In addition, it is possible to easily ensure strength against a large thrust force.
[0026]
  Also,ThirdAccording to the invention, a screw flange is formed by forming a convex portion on a surface of the flange of the screw that contacts the end surface of the shaft portion, and forming a groove portion engageable with the convex portion on the end surface of the shaft portion. Later, the convex part of the flange can be locked in the groove part to prevent the screw from loosening.
[0027]
  Also,4thAccording to the invention, the convex portion provided on the flange is formed in a wedge shape that is locked to the groove portion in the loosening direction of the screw, while the groove portion formed on the end surface of the shaft portion has a tapered surface directed in the fastening direction of the screw. By providing, the wedge-shaped convex part can be smoothly tightened while sliding along the taper surface at the time of fastening, and when an external force in the loosening direction is applied to the screw, the convex part is locked to the groove part and loosened. Can be prevented.
[0028]
  Also,5thAccording to the invention, the flange of the screw is formed so as to gradually increase the thickness from the outer periphery to the inner periphery, and while preventing the increase in the thickness of the flange peripheral edge while ensuring the strength of the screw center portion, It is possible to prevent an increase in the gap between the inner circumference of the casing and the casing.
[0029]
Embodiment
Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
[0030]
1 to 3 show an example in which a toroidal continuously variable transmission is configured using a double cavity toroidal continuously variable transmission.
[0031]
As shown in FIG. 1, the unit input shaft 1a of the toroidal type continuously variable transmission connected to the crankshaft 13 of the engine is provided with a constant transmission 3 (reduction gear) composed of a gear 3a and a gear 3b. At the same time, the unit input shaft 1a is coaxially connected with a CVT shaft 1b as an input shaft of the toroidal type continuously variable transmission 2, and the toroidal type continuously variable transmission 2 and the constant transmission 3 are connected in parallel. Connected.
[0032]
The output shaft 4 of the toroidal-type continuously variable transmission 2 and the output shaft 3c of the constant transmission 3 are disposed on the unit output shaft 6 side, and these output shafts 4 and 3c are connected by a planetary gear mechanism 5. .
[0033]
A sprocket 4a provided on the output shaft 4 of the toroidal-type continuously variable transmission 2 is connected to the CVT shaft 1b via an output sprocket 2a and a chain 11 which are coaxially arranged. One end is coupled to the sun gear 5 a of the planetary gear mechanism 5, and the other end is coupled to the direct coupling mode clutch 10.
[0034]
The output shaft 3c of the constant speed change mechanism 3 coupled to the gear 3b is also supported coaxially and relatively rotatably with the unit output shaft 6, and is connected to the carrier 5b of the planetary gear mechanism 5 via the power circulation mode clutch 9. The ring gear 5c of the planetary gear mechanism 5 is coupled to the unit output shaft 6 that is the output shaft of the toroidal-type continuously variable transmission.
[0035]
A transmission output gear 7 is provided on the right side of the unit output shaft 6 in the figure. The transmission output gear 7 meshes with the final gear 12 of the differential gear 8, and there is no drive shaft connected to the differential gear 8. The driving force is transmitted at a gear ratio RATIO of the step transmission mechanism 2 and a unit gear ratio (unit input shaft speed / unit output shaft speed = total speed ratio) according to the operation mode.
[0036]
As shown in FIGS. 1 and 2, the toroidal-type continuously variable transmission 2 is configured by a double-cavity half-toroidal type that sandwiches and presses the power rollers 20 and 20 with two sets of input disks 21 and output disks 22, respectively. Is done.
[0037]
An output gear 2a is interposed between the output disks 22 and 22, and the output gear 2a is connected to the unit input shaft 1a and the CVT shaft 1b via the chain 11 in a stepless manner of the unit output shaft 6. It is connected to a gear 4 a formed on the transmission output shaft 4.
[0038]
Further, as shown in FIG. 1, the unit input shaft 1a and the CVT shaft 1b are coaxially arranged and coupled in the rotational direction via the loading cam device 23 of the toroidal type continuously variable transmission 2. The unit input shaft 1a forming the gear 3a of the constant transmission 3 is coupled to the crankshaft 13 of the engine, and the CVT shaft 1b is coupled to two sets of input disks 21 and 21, so that the unit input shaft 1a Due to the axial pressing force generated by the loading cam device 23 in accordance with the input torque from the power roller 20, the power rollers 20 and 20 are sandwiched and pressed by the input / output disk to transmit torque.
[0039]
In this toroidal continuously variable transmission, the power circulation mode clutch 9 is released, while the direct connection mode clutch 10 is engaged to transmit the driving force according to the gear ratio of the toroidal continuously variable transmission 2, and the power By engaging the circulation mode clutch 9 and releasing the direct connection mode clutch 10, the unit transmission of the entire toroidal continuously variable transmission is changed according to the difference in the transmission ratio between the toroidal continuously variable transmission 2 and the constant transmission 3. It is possible to selectively use a power circulation mode in which the ratio (transmission ratio between the unit input shaft 1a and the unit output shaft 6) is controlled almost continuously including a infinity from a negative value to a positive value.
[0040]
2 and 3, the power rollers 20 and 20 are rotatably and swingably supported by a pair of trunnions 40 and 40 disposed with the rotary shaft 1C of the input / output disk interposed therebetween. 40 and 40 are supported so as to be displaceable in the axial direction (= rotational tangent direction of the input / output disk) and the axis (= rotational tangent of the input / output disk) of the rotary shafts 40C and 40C, respectively.
[0041]
Then, the hydraulic cylinders 30 and 30 (actuators) respectively connected to the lower ends of the trunnions 40 and 40 drive the trunnions 40 and 40 in the axial direction, so that the power rollers 20 and 20 rotate around the rotation shaft 40C. The contact radius between the input disk 21 and the output disk 22 changes, and the gear ratio is continuously changed.
[0042]
The trunnions 40, 40 arranged opposite to each other are connected to each other by an upper link 18 at the upper part and a lower link 19 at the lower part, and resist the thrust force applied to the power rollers 20, 20 against the upper link 18 and the lower link. 19 keeps the distance between the rotation shafts 40C, 40C of the trunnions 40, 40 constant, and restricts the upper part of the trunnions 40, 40 from bending in the direction of the rotation shaft 1C of the input / output disk.
[0043]
The upper link 18 is formed with a through hole 18b in the center, and is supported by an upper link post 17 (support member) inserted into the through hole 18b so as to be swingable. It is connected to a fixed post base 16 and supported so as to be swingable. A pin (not shown) protrudes from the upper link post 17 in the penetrating direction of the paper surface of FIGS. 2 and 3, and this pin passes through the through hole 18 b of the upper link 18, whereby the upper link 18. Is supported by the upper link post 17 so as to be swingable.
[0044]
On the other hand, through holes 18a and 18b formed at both end portions of the upper link 18 are inserted shaft portions 42 and 42 projecting upward from the top of the trunnions 40 and 40 in the figure, and the outer periphery of these shaft portions 42 The trunnions 40, 40 and the upper link 18 are connected to each other via a spherical bearing 60 provided on the upper side.
[0045]
The trunnions 40, 40 are displaced in opposite axial directions by the upper link 18 that can swing around the upper link post 17, and are allowed to rotate around the rotation shaft 40 </ b> C by the spherical bearing 60.
[0046]
A screw 50 integrally formed with a thin flange portion 52 is fastened to the upper end surface 41 of the shaft portion 42 formed on the trunnion 40 in order to prevent the spherical bearing 60 from falling off.
[0047]
As shown in FIG. 3, the upper end surface 41 of the shaft portion 42 is formed with a screw hole 43 at a position 50C offset by a predetermined amount from the rotation shaft 40C of the trunnion 40 toward the rotation shaft 1C of the input / output disk. A screw part 51 protruding from the screw 50 is fastened to the screw hole 43.
[0048]
The screw 50 is formed by projecting a threaded portion 51 from the center of a disc-shaped flange portion 52, and the flange portion 52 abuts on the upper end surface 41 and can be abutted on the end surface of the spherical bearing 60. The spherical bearing 60 is prevented from being displaced in the axial direction, thereby preventing the spherical bearing 60 from falling off the shaft portion 42.
[0049]
In FIG. 3, the outer diameter of the flange portion 52 is set to be not less than the inner periphery of the spherical bearing 60 and less than the outer periphery of the spherical bearing 60 from the axis 50 </ b> C of the screw hole 43, and is arranged coaxially with the shaft portion 42. While abutting a part of the end face of 60 and preventing falling off, it is prevented from interfering with the through hole 18a of the swinging upper link 18.
[0050]
And the hole part 53 used at the time of an assembly | attachment is formed in the screw part 51 of the screw 50. For example, when a screw is formed in the hole part 53, the screw for assembly is screwed into the hole part 53, The screw part 51 is fastened to the screw hole 43. Alternatively, when the hole 53 is formed of a hexagonal hole or the like, a wrench is inserted into the hole 53 and the screw part 51 is fastened to the screw hole 43.
[0051]
Next, the operation will be described.
[0052]
The spherical bearing 60 disposed on the outer periphery of the shaft portion 42 of the trunnion 40 is configured such that a part of the flange portion 52 of the screw 50 fastened to the upper end surface 41 comes into contact with the end surface of the spherical bearing 60, thereby It is possible to prevent the spherical bearing 60 from dropping from 42.
[0053]
Since the outer diameter of the flange portion 52 is set to be less than the outer periphery of the spherical bearing 60, the screw 50 and the upper link 18 do not interfere with each other, and a smooth movement of the upper link 18 and the trunnion 40 can be ensured.
[0054]
2 and 3, the shaft portion 42 of the trunnion 40 is adjacent to the toroidal-type continuously variable transmission 2 as shown in FIG. When the maximum outer diameter of the member of the unit output shaft 6 (for example, the power circulation mode clutch 9) is indicated by 9 ', the gap L1 between the maximum outer diameter 9' and the flange portion 52 of the screw 50 is the same as that of the conventional example shown in FIG. Is set to a value slightly larger than the stroke of the hydraulic cylinder 30 in the same manner as the gap L1 ′ shown in FIG. 2, but the inter-axis distance Lc between the rotary shaft 1C of the toroidal-type continuously variable transmission 2 and the rotary shaft 6C of the unit output shaft 6 is set. Can be reduced by an amount that the upper end surface 41 of the shaft portion 42 does not protrude from the upper surface of the upper link 18 than the inter-axis distance Lc ′ shown in FIG.
[0055]
Here, in FIG. 1, when the distance Lc between the rotation shaft 1C of the unit input shaft 1a and the CVT shaft 1b and the rotation shaft 6C of the unit output shaft 6 is shortened, if the distance Lc between the shafts is shortened, a constant transmission is achieved. The outer diameters of the third gears 3a and 3b can be reduced.
[0056]
Furthermore, since the outer periphery of the gear 3b is close to the differential gear 8, if the outer diameter of the gear 3b can be reduced, the outer diameters of the transmission output gear 7 and the final gear 12 can also be reduced, and the rotation shaft 6C of the unit output shaft 6 can be reduced. Thus, the inter-axis distance Ld of the rotation shaft 8C of the drive shaft coupled to the differential gear 8 can also be shortened.
[0057]
Thus, when the toroidal continuously variable transmission 2 to which the present invention is applied and an infinitely variable transmission continuously variable transmission is configured, the distance between the two shafts from the unit input shaft 1a to the drive shaft is reduced, The transmission can be reduced in size and weight.
[0058]
Further, the trunnion 40 rotates around the rotation shaft 40c due to the tilting of the power roller 20, and slip occurs between the spherical bearing 60 that rotates together with the upper link 18 and the flange portion 52 of the screw 50. 50 may be applied with torque in the rotational direction.
[0059]
Depending on the direction of relative rotation between the trunnion 40 and the upper link 18, torque is applied in the direction of loosening the screw 50 fastened to the shaft portion 42.
[0060]
Therefore, by offsetting the position where the screw 50 is provided (the axis 50C of the screw hole 43) with respect to the rotating shaft 40c of the shaft portion 42 of the trunnion 40, the torque in the loosening direction applied to the screw 50 can be reduced. It is possible to prevent the screw 50 and the spherical bearing 60 from falling off by rotating relative to the upper link 18.
[0061]
In addition, the trunnion 40 is applied with a large thrust force from the power roller 20 sandwiched and pressed by the input / output disks 21 and 22, so that it is necessary to ensure the strength, but the axis 50 </ b> C of the screw hole 43 for fastening the screw 50. 3 is offset from the rotation shaft 40c of the trunnion 40, in other words, from the rotation shaft 40c of the trunnion 40 to the rotation shaft 1C side of the input / output disk. In FIG. It is possible to secure a sufficient thickness T in the middle of the connection to the upper end surface 41 of the shaft portion 42, and the strength against a large thrust force can be easily achieved without reducing the rigidity while forming the screw hole 43 in the upper end surface 41 of the shaft portion 42. It can be secured.
[0062]
Further, in the above-described conventional example, an example in which the spherical bearing 60 is held by the spacer and the snap ring is shown. However, although not shown, the disk-like shape according to the present invention is compared with the case where the spacer is fastened by a hexagon bolt or the like. The screw 50 provided with the flange portion 52 can reduce the amount of protrusion from the upper end surface of the shaft portion 42 and reduce the inter-axis distance Lc.
[0063]
4 to 9 show a second embodiment, in which a locking mechanism is added to the screw 50 of the first embodiment, and other configurations are the same as those of the first embodiment.
[0064]
First, in FIG. 4 to FIG. 6, the flange portion 52 of the screw 50 has a predetermined circumferential direction on the surface on which the screw portion 51 is protruded, that is, the surface that contacts the upper end surface 41 of the shaft portion 42. A large number of convex portions 54 are projected at intervals.
[0065]
As shown in FIG. 6, the convex portion 54 is formed with a tapered surface 54 a inclined toward the fastening direction of the screw 50 to form a wedge-shaped cross section.
[0066]
On the other hand, as shown in FIGS. 7 to 9, a groove 44 is provided in the circumferential direction on the upper end surface 41 of the shaft portion 42 to which the screw 50 is fastened, at a position facing the convex portion 54 provided on the flange portion 52. Are formed at predetermined intervals.
[0067]
As shown in FIG. 9, the groove portion 44 is provided with a tapered portion 44 a in the fastening direction of the screw 50, and a wall surface 44 b that stands up in the loosening direction of the screw 50.
[0068]
After the spherical bearing 60 is inserted into the shaft portion 42, when the screw 50 is screwed into the screw hole 43 opened in the shaft portion 42, the convex portion 54 of the flange portion 52 comes into sliding contact with the upper end surface 41.
[0069]
Further, when the screw is screwed in, the convex portion 54 slides on the upper end surface 41 while going into and out of the groove portion 44. At this time, the tapered surface 54a of the convex portion 54 passes over the tapered portion 44a of the groove portion 44 while passing over the tapered portion 44a. The fastening work can be performed smoothly.
[0070]
When the screw 50 is fastened and the flange portion 52 comes into contact with the upper end surface 41, each convex portion 54 holds the spherical bearing 60 in a state of entering the groove portion 44.
[0071]
In this fastened state, when an external force is applied in the loosening direction of the screw 50, the convex portion 54 having a wedge-shaped cross section is caught on the wall surface 44b of the groove portion 44 to prevent the screw 50 from loosening.
[0072]
When the speed change is performed, the trunnion 40 tilts and the upper link 18 swings so that the end surface of the spherical bearing 60 comes into sliding contact with the flange portion 52 of the screw 50 and torque is applied in the loosening direction of the screw 50. The convex portion 54 of the wedge-shaped cross section provided on the flange portion 52 is locked to the wall surface 44b of the groove portion 44 formed on the upper end surface 41 of the shaft portion 42 to prevent the screw 50 from loosening, and the spherical bearing 60 is connected to the shaft portion. 42 can be reliably prevented from falling off.
[0073]
10 and 11 show a third embodiment, in which a taper is provided on the upper surface of the flange portion 52 of the screw 50 of the first embodiment, and other configurations are the same as those of the first embodiment.
[0074]
The flange portion 52 is formed with a tapered portion 52a that increases in thickness from the outer periphery toward the inner periphery, and the strength of the flange portion 52 increases as the distance from the periphery toward the screw portion 51 increases. While securing the strength, as shown in FIG. 10, it is possible to prevent an increase in the thickness of the periphery of the flange portion 52 and maintain the gap L1 between the flange portion 52 and the member 9 ′ on the unit output shaft 6 side.
[0075]
FIG. 12 shows the fourth embodiment, which is an example in which the toroidal type continuously variable transmission of the first embodiment is employed in the normal automatic transmission shown in FIG. 13 of the conventional example.
[0076]
The upper link 18 that connects the opposed trunnions 40 is connected via a spherical bearing 60 inserted through the outer periphery of the shaft portion 42, and the flange portion 52 of the screw 50 fastened to the upper end surface 41 of the shaft portion 42 is a spherical surface. The bearing 60 is prevented from falling off.
[0077]
This toroidal-type continuously variable transmission is housed in a casing 214 employed in the FR method or the like, and an upper link post 17 that supports the upper link 18 so as to be swingable is a post fixed on the inner peripheral upper surface of the casing 214. Supported by the base 116.
[0078]
The inner peripheral side of the casing 214 facing the upper end surface 41 of the shaft portion 42 formed at the upper portion of the trunnion 40 at the closest position is the lower surface of the post base 116, and is driven in the axial direction by driving the hydraulic cylinder 30. The displaced trunnion 40 sets the gap L1 between the upper end surface 41 and the lower surface of the post base 116 to a value slightly larger than the stroke of the hydraulic cylinder 30.
[0079]
The member that protrudes from the upper surface of the upper link 18 is that the screw 50 only protrudes according to the thickness of the flange portion 52. Therefore, compared with the toroidal type continuously variable transmission shown in FIG. The height H from the rotary shaft 1C of the input / output disk to the inner peripheral surface of the casing 214 can be reduced, and the overall height of the transmission can be reduced to improve the mountability to the vehicle, and the minimum ground clearance of the vehicle can be easily achieved. It is possible to ensure.
[Brief description of the drawings]
FIG. 1 is a cross-sectional development view of an infinitely variable gear ratio continuously variable transmission using a toroidal continuously variable transmission according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view of the main part of the toroidal continuously variable transmission.
3 is an enlarged view of the main part of FIG.
FIG. 4 is a cross-sectional view of a screw according to a second embodiment.
FIG. 5 is a bottom view of the screw.
6 is a cross-sectional view taken along arrow AA in FIG.
FIG. 7 is a cross-sectional view of the main part of the upper part of the trunnion.
FIG. 8 is a front view showing an upper end surface of a trunnion shaft portion.
9 is a cross-sectional view taken along the line BB in FIG.
FIG. 10 is a cross-sectional view of a main part of a continuously variable transmission having an infinite gear ratio, showing a third embodiment and employing a toroidal continuously variable transmission.
FIG. 11 is an enlarged cross-sectional view showing the vicinity of the upper end surface of the shaft portion.
FIG. 12 is a cross-sectional view of a main part of a toroidal continuously variable transmission according to a fourth embodiment.
FIG. 13 is a cross-sectional view of a main part of a toroidal continuously variable transmission showing a conventional example.
FIG. 14 is a cross-sectional view of a main part of a continuously variable transmission with an infinite gear ratio using a toroidal continuously variable transmission, showing a conventional example.
[Explanation of symbols]
2 Toroidal continuously variable transmission
3 constant transmission
4 Continuously variable transmission output shaft
5 Planetary gear mechanism
6 Unit output shaft
7 Transmission output gear
9 Power circulation mode clutch
10 Direct coupling mode clutch
14 Casing
16 post base
17 Upper link post
18 Upper link
18a, 18b Through hole
20 Power roller
21 Input disk
22 Output disk
30 Hydraulic cylinder
40 trunnion
40C rotation axis
41 Top surface
42 Shaft
43 Screw holes
44 Groove
44a Taper part
44b Wall surface
50 screws
50c axis
51 Screw part
52 Flange
53 holes
54 Convex
54a Tapered surface
60 Spherical bearing

Claims (5)

A pair of power rollers that are sandwiched between the input disk and the output disk and that can be tilted; and
A pair of trunnions that respectively support the power rollers via pivot shafts and that can be displaced about the rotational tangential direction of the input / output disk and about the tangent lines;
A spherical bearing disposed at the outer peripheral position of the shaft portion formed at the end of the trunnion;
The trunnions arranged opposite to each other are connected by engaging the spherical bearings of the shaft portions with through holes formed at both ends, and the central portion is supported swingably through a support member fixed to the casing. Link and
In a toroidal continuously variable transmission comprising actuators that drive the pair of trunnions in opposite axial directions,
Wherein the end face of the shaft portion has concluded a screw that one body to form a can abut the flange to the spherical bearings exposed from the through hole of the link,
A toroidal-type continuously variable transmission , wherein the screw is disposed offset with respect to a rotation shaft of a trunnion . 2. The toroidal continuously variable transmission according to claim 1 , wherein the screw is disposed offset from a rotation shaft of the trunnion toward the rotation shaft of the input / output disk . A convex portion is formed on a surface of the flange that contacts the end surface of the shaft portion, and a groove portion that can be engaged with the convex portion is formed on an end surface of the shaft portion that faces the convex portion. A toroidal continuously variable transmission according to claim 1 or 2 . The said convex part is formed in the wedge shape latched by a groove part in the loosening direction of a screw | thread, On the other hand, the said groove part was provided with the taper surface toward the fastening direction of the screw | thread. Toroidal type continuously variable transmission. The toroidal continuously variable transmission according to any one of claims 1 to 4 , wherein the flange gradually increases in thickness from the outer periphery toward the inner periphery .

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