JP4378898B2 - Toroidal continuously variable transmission and continuously variable transmission - Google Patents

Toroidal continuously variable transmission and continuously variable transmission Download PDF

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Publication number
JP4378898B2
JP4378898B2 JP2001165368A JP2001165368A JP4378898B2 JP 4378898 B2 JP4378898 B2 JP 4378898B2 JP 2001165368 A JP2001165368 A JP 2001165368A JP 2001165368 A JP2001165368 A JP 2001165368A JP 4378898 B2 JP4378898 B2 JP 4378898B2
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Japan
Prior art keywords
thrust
continuously variable
side disk
input
variable transmission
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Expired - Fee Related
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JP2001165368A
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JP2003028257A5 (en
JP2003028257A (en
Inventor
尚 今西
宏史 石川
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日本精工株式会社
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Priority to JP2001165368A priority patent/JP4378898B2/en
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Publication of JP2003028257A5 publication Critical patent/JP2003028257A5/ja
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Description

[0001]
[Industrial application fields]
The toroidal continuously variable transmission and continuously variable transmission according to the present invention are used as a transmission for various industrial machines or as a transmission unit constituting an automatic transmission for automobiles.
[0002]
[Prior art]
Research has been conducted on the use of a half-toroidal continuously variable transmission (hereinafter simply referred to as a toroidal continuously variable transmission) as schematically shown in FIGS. And some have been implemented. This toroidal type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 and is arranged concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Publication No. 62-71465. An output side disk 4 is fixed to the end of the output shaft 3. Inside the casing 5 (see FIG. 7 described later) in which the toroidal-type continuously variable transmission is housed, a trunnion 7 that swings around pivots 6 and 6 that are twisted with respect to the input shaft 1 and the output shaft 3. 7 are provided.
[0003]
Each of these trunnions 7, 7 is provided with the pivots 6, 6 on the outer side surfaces of both ends concentrically with each other, each pair of trunnions 7, 7. The central axes of the pivots 6 and 6 do not intersect with the central axes of the disks 2 and 4, but are twisted at right angles or substantially perpendicular to the direction of the central axes of the disks 2 and 4. Exists in the position. Further, the central portions of the trunnions 7 and 7 support the base halves of the displacement shafts 8 and 8, and the trunnions 7 and 7 are swung around the pivots 6 and 6 to swing the displacement shafts 8 and 8. , 8 can be adjusted freely. Power rollers 9 and 9 are rotatably supported around the front half of the displacement shafts 8 and 8 supported by the trunnions 7 and 7, respectively. These power rollers 9, 9 are sandwiched between the inner side surfaces 2a, 4a of both the input side and output side disks 2, 4.
[0004]
The inner side surfaces 2a and 4a of the input side and output side discs 2 and 4 facing each other are each obtained by rotating a cross section of an arc centered on the pivot 6 or a curve close to such an arc. It has an arcuate concave surface. And the peripheral surface 9a, 9a of each power roller 9, 9 formed in the spherical convex surface is made to contact | abut to the said inner surface 2a, 4a. In addition, a loading cam device 10 as a thrust generating device is provided between the input shaft 1 and the input side disc 2, and the input cam 2 is elastically directed toward the output side disc 4 by the loading cam device 10. While being pressed, it can be driven to rotate.
[0005]
When the toroidal continuously variable transmission configured as described above is used, the loading cam device 10 presses the input-side disk 2 against the plurality of power rollers 9 and 9 as the input shaft 1 rotates. Rotate. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 9, 9, and the output shaft 3 fixed to the output side disk 4 rotates.
[0006]
When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 7, 7 are swung around the pivot shafts 6, 6. As shown in FIG. 4, the peripheral surfaces 9 a and 9 a of the power rollers 9 and 9 are formed on a portion near the center of the inner surface 2 a of the input side disk 2 and a portion near the outer periphery of the inner surface 4 a of the output side disk 4. The displacement shafts 8 and 8 are inclined so as to contact each other.
[0007]
On the contrary, when the speed is increased, the trunnions 7, 7 are swung so that the peripheral surfaces 9a, 9a of the power rollers 9, 9 are as shown in FIG. Each of the displacement shafts 8 and 8 is inclined so as to abut the outer peripheral portion and the central portion of the inner side surface 4a of the output disk 4 respectively. If the inclination angle of each of the displacement shafts 8 and 8 is set intermediate between those shown in FIGS. 4 and 5, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
[0008]
6 to 7 show a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application No. 63-69293 (Japanese Utility Model Laid-Open No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around a cylindrical input shaft 11. A loading cam device 10 is provided between the end of the input shaft 11 and the input side disk 2. On the other hand, an output gear 12 is coupled to the output side disk 4 so that the output side disk 4 and the output gear 12 rotate in synchronization.
[0009]
The pivots 6, 6 provided concentrically with each other at both ends of the pair of trunnions 7, 7 are oscillated on the pair of support plates 13, 13 in the axial direction (front / back direction in FIG. 6, left / right direction in FIG. 7). Supports displaceability. And the base half part of the displacement shafts 8 and 8 is supported by the intermediate part of each said trunnion 7 and 7. FIG. These displacement shafts 8 and 8 have the base half and the tip half eccentric with respect to each other. And the base half part of these is rotatably supported by the intermediate part of each said trunnion 7 and 7, and the power rollers 9 and 9 are rotatably supported by each front half part.
[0010]
The pair of displacement shafts 8 and 8 are provided at positions opposite to the input shaft 11 by 180 degrees. In addition, the direction in which the base half and the front half of each of the displacement shafts 8 and 8 are eccentric is the same as the rotation direction of the input side and output side disks 2 and 4 (reverse left and right in FIG. 7). It is said. The eccentric direction is a direction substantially perpendicular to the direction in which the input shaft 11 is disposed. Accordingly, the power rollers 9 are supported so as to be slightly displaceable with respect to the direction in which the input shaft 11 is disposed.
[0011]
Further, thrust ball bearings 14 and 14 are arranged between the outer surface of each of the power rollers 9 and 9 and the inner surface of the intermediate portion of each of the trunnions 7 and 7 in order from the outer surface side of each of the power rollers 9 and 9. And thrust needle bearings 15 and 15 are provided. Of these, the thrust ball bearings 14 and 14 support the rotation of the power rollers 9 and 9 while supporting the load in the thrust direction applied to the power rollers 9 and 9. The thrust needle roller bearings 15, 15 support the thrust loads applied to the outer rings 16, 16 constituting the thrust ball bearings 14, 14 from the power rollers 9, 9, 8 and the outer rings 16 and 16 are allowed to swing around the base half of the displacement shafts 8 and 8. Further, the trunnions 7 and 7 can be freely displaced in the axial direction of the pivots 6 and 6 by hydraulic actuators 17 and 17, respectively.
[0012]
In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 11 is transmitted to the input side disk 2 via the loading cam device 10. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 through a pair of power rollers 9, 9, and the rotation of the output side disk 4 is taken out from the output gear 12.
[0013]
When the rotational speed ratio between the input shaft 11 and the output gear 12 is changed, the pair of trunnions 7 and 7 are moved in opposite directions by the actuators 17 and 17, respectively, for example, on the lower side of FIG. The power roller 9 is displaced to the right side of the figure, and the upper power roller 9 of the figure is displaced to the left side of the figure. As a result, the direction of the tangential force acting on the contact portion between the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. To do. As the force changes, the trunnions 7 and 7 swing in directions opposite to each other around the pivots 6 and 6 pivotally supported by the support plates 13 and 13. As a result, as shown in FIGS. 4 to 5 described above, the contact position between the peripheral surfaces 9a and 9a of the power rollers 9 and 9 and the inner surfaces 2a and 4a changes, and the input shaft 11 and The rotational speed ratio with the output gear 12 changes.
[0014]
At the time of power transmission by the toroidal continuously variable transmission, the power rollers 9 and 9 are displaced in the axial direction of the input shaft 11 based on elastic deformation of each component. The displacement shafts 8 and 8 that support the power rollers 9 and 9 are slightly rotated around the respective base halves. As a result of this rotation, the outer surfaces of the outer rings 16, 16 of the thrust ball bearings 14, 14 and the inner surfaces of the trunnions 7, 7 are relatively displaced. Since the thrust needle bearings 15, 15 exist between the outer surface and the inner surface, the force required for the relative displacement is small.
[0015]
In the case of the toroidal-type continuously variable transmission configured and operated as described above, power transmission between the input shaft 11 and the output gear 12 is performed by the two power rollers 9 and 9. Therefore, the force per unit area transmitted between the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner surfaces 2a, 4a of both the input side and output side discs 2, 4 is increased and can be transmitted. Limit the power. In view of such circumstances, it has been conventionally considered to increase the number of power rollers 9 and 9 in order to increase the power that can be transmitted by the toroidal-type continuously variable transmission.
[0016]
As an example of a structure for increasing the number of power rollers 9 and 9 for such a purpose, as shown in FIG. 8, input side disks 2A and 2B and output side disks 4 and 4 are provided around an input shaft 11a. A so-called double cavity type structure in which two each of the input side disks 2A, 2B and the output side disks 4, 4 are arranged in parallel with each other in the power transmission direction has been known. Has been implemented. In the structure shown in FIG. 8, the output gear 12a is supported around the intermediate portion of the input shaft 11a so as to be rotatable with respect to the input shaft 11a, and both end portions of a cylindrical portion provided at the center of the output gear 12a. The output side disks 4 and 4 are spline-engaged. The input disks 2A and 2B are supported at both ends of the input shaft 11a so as to be rotatable together with the input shaft 11a. The input shaft 11a is rotationally driven by a drive shaft 18 via a loading cam device 10 that is a thrust generator. In the case of such a double cavity type toroidal continuously variable transmission, power is transmitted from the input shaft 11a to the output gear 12a between the one input side disk 2A and the output side disk 4 and the other side. Since it is divided into two systems, between the input side disk 2B and the output side disk 4, large power can be transmitted.
[0017]
Further, when a toroidal continuously variable transmission constructed and operated as described above is incorporated into an actual continuously variable transmission for an automobile, it is possible to construct a continuously variable transmission in combination with a planetary gear mechanism. As described in JP-A Nos. 169169, 1-312266, 10-196759, 11-63146, etc., it has been proposed conventionally. That is, the torque applied to the toroidal continuously variable transmission during high speed traveling is transmitted by the toroidal type continuously variable transmission only at low speeds and by the planetary gear mechanism during high speed traveling. We try to reduce it. By comprising in this way, durability of each member which comprises the said toroidal type continuously variable transmission can be improved.
[0018]
FIG. 9 shows a continuously variable transmission described in Japanese Patent Application Laid-Open No. 11-63146 among the above publications. This continuously variable transmission comprises a combination of a double cavity type toroidal continuously variable transmission 19 and a planetary gear mechanism 20. The power is transmitted only by the toroidal type continuously variable transmission 19 during low-speed traveling, and the power is transmitted mainly by the planetary gear mechanism 20 during high-speed traveling, and the gear ratio by the planetary gear mechanism 20 is transmitted to the toroidal type continuously variable transmission. Adjustment is possible by changing the gear ratio of the continuously variable transmission 19.
[0019]
For this purpose, a base end portion (right end portion in FIG. 9) of the input shaft 11a penetrating through the central portion of the toroidal type continuously variable transmission 19 and supporting a pair of input side disks 2A and 2B at both ends, A transmission shaft 23 fixed to the center of a support plate 22 that supports a ring gear 21 constituting the planetary gear mechanism 20 is coupled via a high-speed clutch 24. Of the pair of input side disks 2A and 2B, the input side disk 2B on the front end side (the right side in FIG. 9) is similar to the conventional structure shown in FIG. 8, for example, with respect to the input shaft 11a. Thus, the rotation in synchronization with the input shaft 11a and the substantial movement in the axial direction of the input shaft 11a are supported. On the other hand, the input side disk 2A on the base end side (left side in FIG. 9) rotates with respect to the input shaft 11a in synchronism with the input shaft 11a in the same manner as the conventional structure shown in FIG. The input shaft 11a is supported so as to be movable in the axial direction. In any case, the configuration of the toroidal-type continuously variable transmission 19 is substantially the same as that of the conventional structure shown in FIG. 8 except for the pressing device 25 described below.
[0020]
Further, between the output side end portion (right end portion in FIG. 9) of the crankshaft 27 of the engine 26 as a driving source and the input side end portion (= base end portion = left end portion in FIG. 9) of the input shaft 11a. The starting clutch 28 and the hydraulic pressing device 25 are provided in series with each other in the power transmission direction. The pressing device 25 can generate a pressing force according to the magnitude (torque) of power transmitted from the crankshaft 27 to the toroidal continuously variable transmission 19 based on a signal from a controller (not shown). The oil pressure can be introduced freely.
[0021]
An output shaft 29 for taking out power based on the rotation of the input shaft 11a is arranged concentrically with the input shaft 11a. The planetary gear mechanism 20 is provided around the output shaft 29. The sun gear 30 constituting the planetary gear mechanism 20 is fixed to the input side end portion (left end portion in FIG. 9) of the output shaft 29. Therefore, the output shaft 29 rotates as the sun gear 30 rotates. The ring gear 21 is supported around the sun gear 30 so as to be concentric with the sun gear 30 and to be rotatable. A plurality of planetary gear sets 32 and 32 each including a pair of planetary gears 31 a and 31 b are provided between the inner peripheral surface of the ring gear 21 and the outer peripheral surface of the sun gear 30. Yes. The planetary gears 31a and 31b of each pair are meshed with each other, the planetary gear 31a disposed on the outer diameter side meshes with the ring gear 21, and the planetary gear 31b disposed on the inner diameter side meshes with the sun gear 30. is doing. Such planetary gear sets 32 and 32 are rotatably supported on one side surface (left side surface in FIG. 9) of the carrier 33. The carrier 33 is rotatably supported at the intermediate portion of the output shaft 29.
[0022]
Further, the carrier 33 and the pair of output side disks 4, 4 constituting the toroidal-type continuously variable transmission 19 are connected by a first power transmission mechanism 34 in a state where transmission of rotational force is possible. ing. The first power transmission mechanism 34 includes a transmission shaft 35 parallel to the input shaft 11a and the output shaft 29, a sprocket 36a fixed to one end portion (left end portion in FIG. 9) of the transmission shaft 35, and each of the outputs. The chain 37 spanned between the sprockets 36 b fixed to the side disks 4, 4, the other end (the right end in FIG. 9) of the transmission shaft 35, and the carrier 33, which are respectively fixed and meshed with each other, The second gears 38 and 39 are used. Accordingly, the carrier 33 rotates in the direction opposite to the output side disks 4 and 4 in accordance with the rotation of the output side disks 4 and 4 according to the number of teeth of the first and second gears 38 and 39. Rotate with. This is a case where the number of teeth of the pair of sprockets 36a and 36b is the same.
[0023]
On the other hand, the input shaft 11a and the ring gear 21 can be freely connected to each other through a transmission shaft 23 disposed concentrically with the input shaft 11a. Between the transmission shaft 23 and the input shaft 11a, the high-speed clutch 24 is provided in series with the shafts 23 and 11a. Therefore, in this example, Claim 4 The second power transmission mechanism 42 described in 1 is configured by the transmission shaft 23. When the high speed clutch 24 is connected, the transmission shaft 23 rotates at the same speed in the same direction as the input shaft 11a as the input shaft 11a rotates.
[0024]
The continuously variable transmission is , Ku A latch mechanism is provided. The clutch mechanism includes the high-speed clutch 24, a low-speed clutch 40 provided between the outer peripheral edge of the carrier 33 and one axial end of the ring gear 21 (the right end in FIG. 9), and the ring. It comprises a reverse clutch 41 provided between the gear 21 and a fixed part such as a housing (not shown) of the continuously variable transmission. When any one of the clutches 24, 40 and 41 is connected, the remaining two clutches are disconnected.
[0025]
The continuously variable transmission configured as described above first connects the low speed clutch 40 and disconnects the high speed clutch 24 and the reverse clutch 41 during low speed traveling. When the starting clutch 28 is connected and the input shaft 11a is rotated in this state, only the toroidal continuously variable transmission 19 transmits power from the input shaft 11a to the output shaft 29. When traveling at such a low speed, the transmission ratio between the pair of input side disks 2A, 2B and the output side disks 4, 4 is set to the toroidal type continuously variable transmission shown in FIG. Adjust in the same way.
[0026]
On the other hand, at the time of high speed traveling, the high speed clutch 24 is connected and the low speed clutch 40 and the reverse clutch 41 are disconnected. When the start clutch 28 is connected in this state and the input shaft 11a is rotated, the transmission shaft 23 and the planetary gear mechanism 20 transmit power from the input shaft 11a to the output shaft 29. That is, when the input shaft 11 a rotates during the high speed traveling, the rotation is transmitted to the ring gear 21 through the high speed clutch 24 and the transmission shaft 23. Then, the rotation of the ring gear 21 is transmitted to the sun gear 30 through the plurality of planetary gear sets 32, 32, and the output shaft 29 to which the sun gear 30 is fixed is rotated. In this state, if the revolution speed of each planetary gear set 32, 32 is changed by changing the gear ratio of the toroidal type continuously variable transmission 19, the gear ratio of the continuously variable transmission as a whole can be adjusted.
[0027]
That is, the planetary gear sets 32, 32 revolve in the same direction as the ring gear 21 during the high speed traveling. The lower the revolution speed of each planetary gear set 32, 32, the higher the rotational speed of the output shaft 29 to which the sun gear 30 is fixed. For example, if the revolution speed and the rotational speed (both angular speeds) of the ring gear 21 are the same, the rotational speeds of the ring gear 21 and the output shaft 29 are the same. On the other hand, if the revolution speed is slower than the rotation speed of the ring gear 21, the rotation speed of the output shaft 29 becomes faster than the rotation speed of the ring gear 21. On the contrary, if the revolution speed is higher than the rotation speed of the ring gear 21, the rotation speed of the output shaft 29 becomes slower than the rotation speed of the ring gear 21.
[0028]
Accordingly, during the high speed traveling, the speed ratio of the entire continuously variable transmission changes to the speed increasing side as the speed ratio of the toroidal type continuously variable transmission 19 is changed to the speed reducing side. In such a state during high speed running, torque is applied to the toroidal continuously variable transmission 19 from the output side disk 4 instead of the input side disks 2A and 2B (when the torque applied at low speed is a positive torque) Negative torque is applied to the That is, in the state where the high speed clutch 24 is connected, the torque transmitted from the engine 26 to the input shaft 11 a is transmitted to the ring gear 21 of the planetary gear mechanism 20 through the transmission shaft 23. Therefore, almost no torque is transmitted from the input shaft 11a side to each of the input side disks 2A and 2B.
[0029]
On the other hand, a part of the torque transmitted to the ring gear 21 of the planetary gear mechanism 20 through the second power transmission mechanism 42 is transmitted from the planetary gear sets 32 and 32 to the carrier 33 and the first power transmission. It is transmitted to the output side disks 4 and 4 via the mechanism 34. Thus, the torque applied to the toroidal type continuously variable transmission 19 from the output side disks 4 and 4 is such that the speed ratio of the toroidal type continuously variable transmission 19 is changed so as to change the speed ratio of the entire continuously variable transmission to the speed increasing side. It becomes smaller as the value is changed to the deceleration side. As a result, the torque input to the toroidal continuously variable transmission 19 during high-speed traveling can be reduced, and the durability of the components of the toroidal continuously variable transmission 19 can be improved.
[0030]
Further, when the output shaft 29 is reversely rotated in order to reverse the automobile, both the low speed and high speed clutches 40 and 24 are disconnected and the reverse clutch 41 is connected. As a result, the ring gear 21 is fixed, and the planetary gear sets 32 and 32 revolve around the sun gear 30 while meshing with the ring gear 21 and the sun gear 30. And this sun gear 30 and the output shaft 29 which fixed this sun gear 30 rotate in the reverse direction at the time of the above-mentioned low speed driving | running | working and the above-mentioned high speed driving | running | working.
[0031]
By the way, when the toroidal type continuously variable transmission configured and operated as described above or the continuously variable transmission configured and operated as described above is operated, the input side disks 2, 2 A and 2 B are pressed against the output side disk 4. Therefore, the magnitude of the thrust required for the thrust generator varies not only according to the magnitude of the torque to be transmitted but also depending on the gear ratio. That is, when the trunnions 7 and 7 are swung and displaced about the pivots 6 and 6 in order to change the transmission ratio, the peripheral surfaces 9a and 9a of the power rollers 9 and 9 and the disks 2, 2A, 2B, and 4 The position of the traction portion that is the contact point with the side surfaces 2a and 4a changes. As the position of the traction section changes, the thrust required to apply the pressing force necessary for the traction section changes. Specifically, assuming that the torque to be transmitted is constant, the rotational force between the input side disks 2, 2A, 2B and the output side disk 4 is substantially equal as indicated by the solid line α in FIG. When transmission is performed at a constant speed (the gear ratio is in the vicinity of 1), the required thrust becomes the largest. On the other hand, the trunnions 7 and 7 are inclined as shown in FIG. 4 or FIG. 5 to increase the reduction ratio or the speed increase ratio between the input side disks 2, 2 A and 2 B and the output side disk 4. Indeed, the required thrust becomes smaller.
[0032]
On the other hand, the loading cam device 10 incorporated as a thrust generating device in the conventional structure shown in FIGS. 4 to 5 generates a thrust according to the magnitude of torque to be transmitted, but includes a gear ratio. Even if factors other than torque fluctuations change, the thrust generated does not change. For this reason, in the case of the conventional structure having only the loading cam device 10 as the thrust generating device, the thrust generated by the loading cam device 10 requires the largest thrust as shown by the broken line β in FIG. It is set according to the case where the ratio is in the vicinity of 1. Therefore, in the case of such a conventional structure, when the gear ratio is other than near 1, the thrust generated by the loading cam device 10 becomes excessive, and the extent to which the thrust is excessive is limited to the speed reduction ratio or speed increase. The greater the ratio, the more significant. If the thrust becomes excessive and the pushing force of the traction part becomes excessive, not only the transmission efficiency in the traction part deteriorates but also the rolling fatigue life of the surfaces 2a, 4a, 9a constituting the traction part is short. Become.
[0033]
In view of such circumstances, Japanese Patent Publication No. 6-72652 discloses a thrust generator incorporated in a toroidal-type continuously variable transmission that generates thrust in a direction in which the input side disk and the output side disk approach each other. A structure composed of a cam device and a hydraulic actuator is described. Both the loading cam device and the hydraulic actuator generate thrust in a direction in which the input side disk and the output side disk are brought close to each other. Of these, the loading cam device generates the minimum required thrust (thrust required when the transmission gear ratio deviates greatly from the vicinity of 1) indicated by a chain line γ in FIG. When the gear ratio is close to 1, the thrust which is insufficient, that is, the thrust of the portion represented by the oblique grid in FIG. 10 is generated. The magnitude of the thrust generated by the hydraulic actuator, which corresponds to the portion indicated by the oblique grid in FIG. 10, can be adjusted by a signal from the controller in accordance with the gear ratio. For this reason, the thrust as the whole thrust generating device can be made appropriate according to the gear ratio, the transmission efficiency in the traction section can be improved, and the surfaces 2a, 4a, 9a constituting the traction section. The rolling fatigue life can be secured.
[0034]
[Problems to be solved by the invention]
In the case of the conventional structure as described in Japanese Patent Publication No. 6-72652, the function of the toroidal continuously variable transmission is stopped when the hydraulic actuator or the oil supply circuit to the hydraulic actuator fails. It may cause a failure. That is, if the thrust required by the hydraulic actuator does not occur for some reason, such as a failure of the hydraulic actuator itself, a failure of the oil pump or control valve that constitutes the oil supply circuit, or the inclusion of foreign matter, The thrust value of the entire device is smaller than the originally required value. As a result, the pressing force of the traction portion is insufficient, and there is a possibility that significant slip occurs in the traction portion.
[0035]
When a significant slip occurs, not only cannot the power be transmitted from the input side disk to the output side disk, but also the inner surface of each of the disks constituting the traction section and the peripheral surface of the power roller. In addition, damage such as early peeling due to metal contact is likely to occur.
In view of such circumstances, the present invention is capable of generating an appropriate thrust regardless of a change in the gear ratio, ensuring a minimum function even in the event of a failure, and leading to a more serious failure. It was invented to realize a structure that can be prevented.
[0036]
[Means for Solving the Problems]
The toroidal-type continuously variable transmission of the present invention is similar to the previously known toroidal-type continuously variable transmission, and includes an input side disk and an output side disk, a plurality of trunnions, a displacement shaft, a power roller, And a thrust generator.
Among these, the input side disk and the output side disk are supported concentrically and rotatably in a state where the inner side surfaces, which are concave surfaces each having an arcuate cross section, are opposed to each other.
Each trunnion swings about a pivot that is twisted with respect to the central axes of the input and output disks.
The displacement shaft is supported at a middle portion of each trunnion so as to protrude from the inner surface of each trunnion.
The power roller is disposed on the inner side of each trunnion and is rotatably supported around each displacement shaft while being sandwiched between the input side disk and the output side disk. The circumferential surface is a spherical convex surface.
Further, the thrust generating device generates a thrust in a direction in which the input side disk and the output side disk approach each other.
[0037]
In particular, in the toroidal type continuously variable transmission of the present invention, the thrust generating device is a combination of a first thrust generating unit and a second thrust generating unit.
The first thrust generating unit generates a thrust in a direction in which the input side disk and the output side disk approach each other in relation to the torque input to the input side disk, like a loading cam device. It is something to be made.
On the other hand, the second thrust generating unit is controlled separately from the thrust generated by the first thrust generating unit, like a hydraulic actuator, and moves the input side disk and the output side disk away from each other. It generates direction thrust.
[0038]
[Action]
The toroidal-type continuously variable transmission of the present invention configured as described above has been known in the past for the operation of transmitting power between the input side disk and the output side disk and changing the speed ratio. This is the same as the case of the toroidal type continuously variable transmission.
In particular, in the case of the toroidal continuously variable transmission according to the present invention, it is possible to generate an appropriate thrust regardless of a change in the gear ratio, and to secure a minimum function even in the event of a failure.
[0039]
In other words, the thrust in the direction in which the input side disk and the output side disk are brought close to each other generated by the thrust generating device incorporated in the toroidal type continuously variable transmission of the present invention is based on the thrust generated by the first thrust generating unit. The thrust generated by the second thrust generating unit is reduced.
Among these, the thrust generated by the first thrust generating unit is in accordance with the magnitude (torque) of power transmitted from the input side disk to the output side disk, whereas the second thrust is The thrust generated by the generating unit can be adjusted independently of the magnitude of the power.
Therefore, when the gear ratio between the input side disk and the output side disk is in the vicinity of 1, the thrust generated by the second thrust generating unit is reduced to 0 or very small, and the speed ratio in the vicinity of 1 is set. If the thrust generated by the second thrust generating unit is increased as the deviation from is increased, the thrust as the whole thrust generating device is the largest when the speed ratio is in the vicinity of 1, and this speed ratio Can be reduced as it deviates from the vicinity of 1.
For this reason, the pressing force of the traction part can be optimized, and the transmission efficiency and the rolling fatigue life can be improved.
[0040]
Even if the second thrust generating unit fails, the thrust generated by the entire thrust generating device is the thrust generated by the first thrust generating unit. Since the thrust generated by the first thrust generating unit is sufficiently large, even when the second thrust generating unit fails, the pressing force of the traction section is sufficiently secured, and significant slip occurs in the traction section. Can be prevented. For this reason, even when the second thrust generating unit fails, power is transmitted from the input disk to the output disk, and at the same time, damage such as premature peeling due to metal contact at the traction portion is prevented. it can.
[0041]
DETAILED DESCRIPTION OF THE INVENTION
FIG. Claims 1-3 The 1st example of embodiment of this invention corresponding to is shown. The feature of the present invention is that the traction is a contact portion between the inner side surfaces 2a, 4a of the input side disks 2A, 2B and the output side disks 4, 4 and the peripheral surfaces 9a, 9a of the power rollers 9, 9. In order to secure the pressing force of the part, the thrust generating device 43 has a structure in which one (left side in FIG. 1) input side disk 2A is pressed toward the other (right side in FIG. 1) input side disk 2B. . Since the structure and operation of the other parts are the same as in the case of the second example of the conventional concrete structure shown in FIG. 8, the same parts are denoted by the same reference numerals, and redundant explanations are omitted or In the following, the description will focus on the features of the present invention as well as the portions not previously described.
[0042]
In the toroidal type continuously variable transmission of the present invention, the thrust generating device 43 includes a loading cam device 10 that is a first thrust generating unit and a hydraulic actuator 44 that is a second thrust generating unit. Are arranged in series with respect to the generation direction of Of these, the structure and function of the loading cam device 10 are the same as those of the loading cam device 10 incorporated in the conventional structure described above. That is, the loading cam device 10 has a cam plate 45 that is rotationally driven by the drive shaft 18. Then, cam surfaces 46a and 46b, which are concave and convex surfaces in the circumferential direction, are formed on one surface (the right surface in FIG. 1) of the cam plate 45 and the outer surface (the left surface in FIG. 1) of the input side disk 2A that face each other. And a plurality of rollers 47, 47 between the cam surfaces 46a, 46b can be freely rotated around the imaginary axis of each cam surface 46a, 46b. It is pinched.
[0043]
When the cam plate 45 is rotationally driven by the drive shaft 18, the rollers 47 and 47 tend to run on the convex portions of the cam surfaces 46a and 46b, and the input side disk 2A is moved to the other input side disk 2B. Rotating while pressing. Accordingly, the force with which the loading cam device 10 presses the input side disk 2A against the other input side disk 2B, that is, the thrust, changes in relation to the torque with which the drive shaft 18 drives the cam plate 45 to rotate. That is, the magnitude of the thrust increases as the torque increases. In this way, the magnitude of the thrust generated by the loading cam device 10 can be adjusted to a desired value by changing the inclination angles of the cam surfaces 46a and 46b. The tendency of the thrust to increase with the increase of the torque can be adjusted as appropriate by changing the shapes of the cam surfaces 46a and 46b. In any case, in the case of this example, the loading cam device 10 is provided with the largest thrust (necessary when the gear ratio is close to 1) required during operation of the toroidal continuously variable transmission. Has the ability to generate.
[0044]
In the case of the toroidal type continuously variable transmission of this example, the pair of input side disks 2A and 2B are rotated at both ends of the input shaft 11b through ball splines 48a and 48b, respectively, and synchronized with the input shaft 11b. The input shaft 11b is supported so as to be movable in the axial direction. Loading nuts 49a and 49b are screwed into portions protruding from the outer surfaces of the input side disks 2A and 2B at both ends of the input shaft 11b.
[0045]
An inner ring 50 and a preload spring 51 are provided in this order from the loading nut 49a side between the loading nut 49a provided on the loading cam device 10 side and the input side disk 2A. Of these, the inner ring 50 constitutes a ball bearing 52 for allowing relative displacement between the cam plate 45 and the input shaft 11b. The preload spring 51 applies a preload that presses the input side disk 2A against the other input side disk 2B even when the loading cam device 10 is not in operation. On the other hand, a disc spring 53 is provided between a loading nut 49b provided on the opposite side of the loading cam device 10 and the input side disk 2B. The disc spring 53 also serves to apply the preload, and to relieve a thrust load applied to the input side disk 2B in an impact manner. The disc side spring 53 serves to reduce the input side relative to the input shaft 11b. The elasticity is large enough to suppress the displacement of the disk 2B.
[0046]
The hydraulic actuator 44 is provided between the intermediate outer peripheral surface of the input shaft 11b and the input side disk 2A on the loading cam device 10 side, which are combined as described above. Therefore, in the case of this example, the inner peripheral surface of the input side disk 2A has a stepped shape. The outer end portion (the left end portion in FIG. 1) of the inner peripheral surface is a small-diameter cylindrical surface, and a seal ring such as an O-ring is mounted in a locking groove formed in the intermediate portion in the axial direction. In other words, an inward flange-shaped flange portion 54 is formed at the outer surface side end portion of the inner peripheral surface of the input side disk 2A, and the seal ring is attached to an intermediate portion of the inner peripheral surface of the flange portion 54. Yes. Therefore, the outer peripheral surface outer end portion of the input side disk 2A is externally fitted on the outer peripheral surface of the input shaft 11b so as to be oil-tight and displaceable in the axial direction (left and right direction in FIG. 1).
[0047]
On the other hand, the inner end portion (right end portion in FIG. 1) of the inner peripheral surface of the input side disk 2A has a larger diameter than the outer end portion, and a female ball spline for constituting the ball spline 48a. Grooves are formed. Further, an intermediate portion of the inner peripheral surface of the input side disk 2A is a large-diameter cylindrical surface. The inner diameter of the intermediate portion is greater than or equal to the groove bottom diameter of the female ball spline groove (preferably larger than the groove bottom diameter). Further, in order to constitute the ball spline 48a, a large-diameter portion 55 having a slightly larger diameter than the portion adjacent in the axial direction is formed at a portion facing the female ball spline groove at an intermediate portion of the input shaft 11b. A male ball spline groove for forming the ball spline 48a is formed on the outer peripheral surface of the large diameter portion 55.
[0048]
The opening end of the male ball spline groove and the opening end of the female ball spline groove are not in operation of the loading cam device 10, as shown in FIG. Are located at the bottoms of the recesses constituting the cam surfaces 46a and 46b, so that their axial positions coincide with each other. At least the inner end position (left end in FIG. 1) of the female ball spline groove is positioned more than the inner end position of the male ball spline groove, regardless of the operating state of the toroidal-type continuously variable transmission. The size of each part is regulated so that it does not protrude to the outer surface side of 2A. This is because a portion near the outer diameter of the seal plate 56 for constituting the hydraulic actuator 44 described below is pushed in the axial direction at the inner end portion of the female ball spline groove, or the seal plate 56 is moved to the female ball. This is to prevent the inner end of the spline groove from being pushed. When the loading cam device 10 is operated and the loading cam device 10 generates thrust, the input side disk 2A is displaced to the right with respect to the input shaft 11b from the state shown in FIG. The opening end positions of the spline grooves are shifted from each other. In this state, the seal plate 56 and the inner end portion of the female ball spline groove are separated from each other.
[0049]
Further, a radial intermediate portion and an inner end portion of the seal plate 56 are abutted against an axial end surface (left end surface in FIG. 1) of the large diameter portion 55 facing the flange portion 54. The seal plate 56 is formed in an annular shape as a whole, and has sufficient rigidity and sealability such as oil-resistant rubber reinforced by a cored bar. However, moderate elasticity is given so that the inner peripheral part of the input side disk 2A can be passed while elastically deforming the outer peripheral edge part. In such a seal plate 56, a portion closer to the inner diameter on one side is brought into contact with the end surface in the axial direction of the large-diameter portion 55 over the entire circumference, and the outer peripheral edge is an intermediate portion in the axial direction of the inner peripheral surface of the input side disk 2A. In addition, they are in sliding contact over the entire circumference. Accordingly, a hydraulic chamber 57 that is shut off from the outside is provided between the seal plate 56 and the flange 54, and the hydraulic chamber 57 moves the input side disk 2A to the cam plate as pressure oil is introduced. The hydraulic actuator 44 is configured to be pressed to the left in FIG.
[0050]
Note that the distance L between the side surfaces of the flange portion 54 and the seal plate 56 constituting the hydraulic actuator 44 that are opposite to each other does not collide with each other regardless of the operating state of the loading cam device 10. In the same way, we have secured enough. That is, when the input disk 2A is pushed to the right in FIG. 1 with respect to the input shaft 11b in accordance with the operation of the loading cam device 10, the above-described operation is performed as long as no hydraulic pressure is introduced into the hydraulic chamber 57. The flange 54 approaches the seal plate 56. As will be described later, since the hydraulic pressure is not introduced into the hydraulic chamber 57 when the gear ratio is about 1, a state in which the flange portion 54 approaches the seal plate 56 can sufficiently occur. When the opposite side surfaces of the flange portion 54 and the seal plate 56 abut against each other, the loading cam device 10 can no longer press the input side disk 2A toward the output side disk 4. In such a case, there is a possibility that the pressing force of the input side disk 2A is insufficient.
[0051]
Therefore, as shown in FIG. 1, the distance L when the loading cam device 10 is not operated is made larger than the stroke of the loading cam device 10. The stroke of the loading cam device 10 has changed from a state in which the rollers 47 and 47 are present at the bottoms of the concave portions constituting the cam surfaces 46a and 46b to a state in which the rollers are also present at the tops of the convex portions. This is the amount of axial displacement between the input side disk 2A and the cam plate 45 that occurs in some cases. In this case, when the amount of elastic deformation of each part cannot be ignored, the amount of axial displacement is restricted in consideration of this amount of elastic deformation.
[0052]
Pressure oil can be supplied to and discharged from the hydraulic chamber 57 of the hydraulic actuator 44 through a supply / discharge passage 58 provided in the center of the drive shaft 18 and the end of the input shaft 11b. Therefore, in the case of this example, the drive shaft 18 is formed in a hollow tubular shape, and the front end portion (the right end portion in FIG. 1) of the drive shaft 18 is a central hole provided at the end portion of the input shaft 11b. 59 is inserted. A radial bearing 60 having a sealing function, such as a sliding bearing or a needle bearing with a seal ring, is provided between the inner peripheral surface of the center hole 59 and the outer peripheral surface of the tip end portion of the drive shaft 18, and the drive shaft 18 and the input shaft 11b are relatively rotated and the inside and outside of the center hole 59 are kept oiltight. Further, the center hole 59 and the hydraulic chamber 57 are communicated with each other by branch paths 61 and 61. The supply / discharge passage 58 is connected to a hydraulic source such as an oil supply pump (not shown) via a pressure adjustment valve (not shown).
[0053]
The pressure regulating valve supplies hydraulic pressure controlled according to the operation status of the toroidal continuously variable transmission, such as the transmission ratio of the toroidal continuously variable transmission and the torque transmitted to the drive shaft 18. The hydraulic chamber 57 is introduced through 58. Then, by introducing the hydraulic pressure into the hydraulic chamber 57, the hydraulic actuator 44 is caused to generate a thrust in the direction opposite to that of the loading cam device 10. In other words, the hydraulic actuator 44 cancels a part of the thrust generated by the loading cam device 10 with the introduction of the pressure oil into the hydraulic chamber 57, and accordingly, the thrust generating device 43 as a whole is canceled. Reduce the thrust.
[0054]
In the case of the toroidal continuously variable transmission according to the present invention configured as described above, it is possible to generate an appropriate thrust regardless of a change in the gear ratio, and to ensure a minimum function even in the event of a failure. In other words, the pair of input side disks 2A and 2B generated by the thrust generating device 43 incorporated in the toroidal type continuously variable transmission of the present invention are brought close to each other, and eventually, both the input side disks 2A and 2B are respectively connected. The thrust in the direction in which the output side disks 4 and 4 facing each other approach each other is obtained by subtracting the thrust generated by the hydraulic actuator 44 from the thrust generated by the loading cam device 10.
[0055]
The thrust generated by the loading cam device 10 is input from the drive shaft 18 to the toroidal-type continuously variable transmission, and further transmitted from the input disks 2A, 2B to the output disks 4, 4. In contrast to the magnitude (torque) of power, the thrust generated by the hydraulic actuator 44 is related to the magnitude of the power, but independently of the magnitude of the power. It is adjustable. For example, when it is assumed that the magnitude of the power is constant, the thrust generated by the loading cam device 10 is constant as shown by a chain line a in FIG. The thrust generated is changed in accordance with the gear ratio between the input disks 2A and 2B and the output disks 4 and 4 as indicated by the oblique grid in FIG.
[0056]
That is, in the case of the toroidal type continuously variable transmission according to the present invention, the thrust generated by the hydraulic actuator 44 is reduced to 0 or 0 when the speed ratio is in the vicinity of 1, contrary to the conventional structure described above. The thrust generated by the hydraulic actuator 44 is increased as the shift from the vicinity of 1 of the transmission ratio is increased. Accordingly, the thrust of the thrust generating device 43 as a whole is greatest when the gear ratio is in the vicinity of 1, as shown by a solid line B in FIG. 2, and decreases as the gear ratio deviates from the vicinity of 1. For this reason, the pressing force of the traction part can be optimized, and the transmission efficiency and the rolling fatigue life can be improved.
[0057]
Although FIG. 2 is drawn assuming that the torque input from the drive shaft 18 to the input side disk 2A is constant, this torque frequently fluctuates in an actual case. When the torque fluctuates, the chain line i representing the thrust generated by the loading cam 10 moves in the vertical direction in FIG. 2, and the hydraulic actuator 44 represented by the diagonal lattice is generated. The thrust to change also changes. That is, when the torque increases and the chain line i moves upward in FIG. 2, the oblique lattice portion not only moves upward together with the chain line i, but also the height of the oblique lattice itself increases. It increases with the increase. On the other hand, when the torque is reduced, not only the chain line a and the oblique lattice move downward in FIG. 2, but also the height of the oblique lattice is reduced. In short, the larger the deviation of the gear ratio from near 1 and the greater the torque, the greater the reverse thrust generated by the hydraulic actuator 44 in order to offset the thrust generated by the loading cam device 10. .
[0058]
Even if the hydraulic actuator 44 fails, the thrust generated by the entire thrust generating device 43 is the thrust generated by the loading cam device 10 indicated by the chain line a in FIG. As described above, the thrust generated by the loading cam device 10 is sufficiently large and has a magnitude greater than the maximum thrust required when the toroidal continuously variable transmission is operated, so that the hydraulic actuator 44 has failed. Even in this case, the pressing force of the traction part is sufficiently secured. Therefore, it is possible to prevent a significant slip from occurring in the traction portion. For this reason, even when the hydraulic actuator 44 fails, power is transmitted from the input side disks 2A, 2B to the output side disks 4, 4, and at the same time, damage such as premature peeling due to metal contact at the traction portion. It can be prevented from occurring.
[0059]
When the hydraulic actuator 44 fails, if the speed ratio deviates from the vicinity of 1, the pressing force of the traction portion becomes larger than necessary. However, even in such a case, the thrust is not adjusted based on the change in the transmission gear ratio, and the state is the same as that of the conventional structure described above, and the toroidal type continuously variable transmission is achieved even if transmission efficiency and durability are slightly reduced. The basic performance as a machine is not impaired. Therefore, the effect of preventing the occurrence of significant slippage in the traction portion and the inability to transmit power or the occurrence of significant wear due to metal contact is greatly increased.
[0060]
Further, in the illustrated example, in order to configure the hydraulic actuator 44, the portion where the male ball spline constituting the ball spline portion 48a is formed at the intermediate portion of the input shaft 11b has a large diameter. Unlike the case of the conventional structure shown in FIG. 8, the input disks 2A and 2B are externally fitted to the input shaft 11b from the end opposite to the axial direction. For this reason, male screw portions are formed at both ends of the input shaft 11b, and the loading nuts 49a and 49b are screwed to the male screw portions. However, as for the structure of this part, instead of the combination of the male screw part and the loading nuts 49a and 49b, various structures are adopted as long as other structures that can suppress axial displacement such as a combination of a locking groove and a cotter are used. it can. In this case, the structure of both ends of the input shaft 11b may be the same or different.
[0061]
In the example shown in the figure, a structure is shown in which two power rollers are provided between each of the input side disks 2A and 2B and the output side disks 4 and 4 in total. It is also possible to adopt a structure in which six are provided. Further, it can also be implemented with a single cavity type structure as shown in FIG. In the illustrated example, the input side disk 2 </ b> B opposite to the thrust generating device 43 is also pressed by the disc spring 53 to apply the preload. In this case, the preload spring 51 relating to the input side disk 2A on the thrust generating device 43 side can be omitted. On the contrary, if the preload spring 51 is provided, the plate spring 53 may be omitted. If the disc leaf spring 53 is omitted, the input side disk 2B opposite to the thrust generating device 43 is transmitted to the end of the input shaft 11b by the involute spline instead of the ball spline. Supporting freely is enough.
[0062]
Furthermore, in the above description, only the case where the hydraulic pressure introduced into the hydraulic chamber 57 of the hydraulic actuator 44 is adjusted according to the gear ratio has been described. It can also be done with consideration. For example, the magnitude of power that can be transmitted by the traction unit varies depending on the viscosity of traction oil present in the traction unit. When the temperature is low and the viscosity is low, the necessary power transmission can be performed with a relatively small pressing force, whereas when the temperature is high and the viscosity is low, the necessary power transmission is performed. Therefore, it is necessary to increase the pressing force. Therefore, if the adjustment of the hydraulic pressure is controlled by the oil temperature in addition to the gear ratio, a more appropriate pressing force can be obtained. That is, when the oil temperature detected by the separately provided oil temperature sensor is low, the hydraulic pressure introduced into the hydraulic chamber 57 is increased to reduce the thrust of the thrust generator 43 as a whole. On the other hand, when the oil temperature is high, the hydraulic pressure introduced into the hydraulic chamber 57 is lowered to increase the thrust of the thrust generator 43 as a whole. By configuring in this way, more appropriate control is possible, and transmission efficiency and durability of the toroidal-type continuously variable transmission can be ensured at a higher level.
[0063]
next, FIG. 3 also shows claims 1 to 3. The 2nd example of embodiment of this invention corresponding to is shown. In the case of this example, by increasing the pressure receiving area of the hydraulic actuator 44a that constitutes the thrust generating device 43a together with the loading cam device 10, the hydraulic pressure introduced into the hydraulic chamber 57a of the hydraulic actuator 44a can be kept low. Power loss associated with driving a pump to generate hydraulic pressure is reduced. Therefore, in the case of this example, the hydraulic actuator 44a is provided between the loading cam device 10 and the input side disk 2A.
[0064]
Specifically, a cylinder housing 62 having an L-shaped cross section and a ring shape as a whole is abutted against the outer surface side of the input side disk 2A. When In both cases, a spline tube 63 is stretched between the cylinder housing 62 and the input side disk 2A. The outer peripheral surface of the cylinder housing 62 and the input side disk 2A and the inner peripheral surface of the spline tube 63 are in spline engagement with each other. Accordingly, the cylinder housing 62 and the input side disk 2A rotate in synchronization with each other. Of the pair of cam surfaces 46a and 46b constituting the loading cam device 10, the cam surface 46b on the input disk 2A side is the outer diameter side of the outer side surface (the left side surface in FIG. 3) of the cylinder housing 62. It is formed in half.
[0065]
In the case of this example, the thrust generating device 43a is arranged around a sleeve 64 that is externally fitted to the proximal end (leftward in FIG. 3) of the input shaft 11c so as to be axially displaceable. And the piston plate 65 which comprises the said hydraulic actuator 44a is fixed to the front-end | tip part (right end part of FIG. 3) of the said sleeve 64. As shown in FIG. The outer peripheral edge of the piston plate 65 and the inner peripheral surface of the cylinder housing 62 and the inner peripheral edge of the cylinder housing 62 and the outer peripheral surface of the sleeve 64 are oil-tightly sealed with seal rings, respectively. It is out. In addition, a seal ring is attached to a position sandwiching the opening of the branch passages 61 and 61 for supplying and discharging pressure oil at two positions spaced apart in the axial direction on the inner peripheral surface of the sleeve 64, Oil tightness is maintained between the inner peripheral surface and the outer peripheral surface of the input shaft 11c. With these configurations, the hydraulic chamber 57a is formed between the piston plate 65 and the cylinder housing 62, and pressure oil can be supplied and discharged into the hydraulic chamber 57a through the branch passages 61 and 61. . In the case of this example, in order to allow pressure oil to be supplied and discharged freely in the hydraulic chamber 57a, a seal ring 66 independent of the radial bearing 60a is provided at a fitting portion between the input shaft 11c and the drive shaft 18. Is provided.
[0066]
Further, the inner ring 50 constituting the ball bearing 52 that supports the cam plate 45 constituting the loading cam device 10 is fitted in the sleeve 64 in a direction away from the cylinder housing 62 by a retaining ring 67. Displacement is prevented. In the case of this example, the inner surfaces 2a and 4a of the disks 2A, 2B and 4 and the peripheral surfaces 9a and 9a of the power rollers 9 and 9 (see FIG. 1; omitted in FIG. 3). A preload spring 51a for applying preload to the contact portion is provided between the flange portion 68 formed at the base end portion of the input shaft 11c and the inner ring 50. In this example, another preload spring 51b and a sleeve 69 are also provided in series between the inner ring 50 and the cylinder housing 62.
[0067]
Further, in the case of this example, concave portions 70 and 70 formed on the outer side inner diameter portions of the output side disks 4 and 4 and convex portions projecting at both axial ends of the sleeve 71 on which the output gear 12b is fixed. By engaging the portions 72 and 72, the output disks 4 and 4 and the output gear 12b are combined so as to be able to transmit the rotational force. Further, the input side disk 2B opposite to the thrust generating device 43a is placed near the tip of the input shaft 11c (right side in FIG. 3) by a normal spline (not a ball spline) so that the rotational force can be transmitted. It is fitted. Then, a holding ring 73 that is externally fitted to a portion protruding from the outer surface of the input side disk 2B at the tip of the input shaft 11c is held down by a cotter 74 so that the input side disk 2B does not come out of the input shaft 11c. Like. The retaining structure of the input side disk 2B is not limited to the combination of the restraining ring 73 and the cotter 74, but may be a conventional structure or a loading nut similar to the first example described above.
[0068]
In the case of the present example configured as described above, similarly to the case of the first example, the thrust generated by the thrust generating device 43a is regulated as shown in FIG. Appropriate thrust is generated, and the minimum functions can be secured even in the event of a failure. In particular, in the case of the structure of this example, the pressure receiving area of the hydraulic actuator 44a constituting the thrust generating device 43a can be made wider than in the case of the first example. For this reason, the hydraulic pressure required to obtain the thrust corresponding to the portion shown by the oblique grid in FIG. 2 can be kept low. As a result, the torque required to drive the pump for generating the hydraulic pressure is small, and the reduction in the efficiency of the toroidal continuously variable transmission due to the pump loss can be kept low.
[0069]
In the above description, the toroidal-type continuously variable transmission alone is described. However, the toroidal-type continuously variable transmission as shown in FIG. 1 or FIG. It can also be implemented by incorporating it into a continuously variable transmission. As described above, the power passing through the toroidal-type continuously variable transmission 19 incorporated in the continuously variable transmission is toroidal when the low speed and reverse clutches 40 and 41 are disconnected by connecting the high speed clutch 24. This is much smaller than when the type continuously variable transmission is operated alone. Therefore, the effect of applying the present invention to the continuously variable transmission is significant. In this case, since the thrust of the portion shown by the oblique lattice in FIG. 2 is increased, it is preferable to apply the structure of the second example shown in FIG. 3 from the viewpoint of reducing the pump loss.
[0070]
【The invention's effect】
As described above, the toroidal continuously variable transmission according to the present invention has excellent transmission efficiency and durability, and can reliably transmit power even when a hydraulic actuator fails, while suppressing the occurrence of significant wear. Can do. Therefore, it is possible to ensure transmission efficiency and durability while ensuring the reliability of the toroidal type continuously variable transmission.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention.
FIG. 2 is a diagram showing the relationship between the magnitude of thrust generated by the thrust generator and the gear ratio in order to explain the operation of the thrust generator.
FIG. 3 is a sectional view showing a second example of the embodiment of the present invention.
FIG. 4 is a schematic side view showing a basic structure of a toroidal-type continuously variable transmission in a state at the time of maximum deceleration.
FIG. 5 is a schematic side view showing the maximum speed increase state.
FIG. 6 is a cross-sectional view showing a first example of a specific structure conventionally known.
7 is a cross-sectional view taken along line AA in FIG.
FIG. 8 is a cross-sectional view showing a second example of a specific structure conventionally known.
FIG. 9 is a schematic cross-sectional view showing an example of a continuously variable transmission incorporating a toroidal type continuously variable transmission.
FIG. 10 is a diagram similar to FIG. 2 for explaining the operation of an improved thrust generating apparatus known conventionally.
[Explanation of symbols]
1 Input shaft
2, 2A, 2B input disk
2a inner surface
3 Output shaft
4 Output disk
4a inner surface
5 Casing
6 Axis
7 Trunnion
8 Displacement axis
9 Power roller
9a circumference
10 Loading cam device
11, 11a, 11b, 11c Input shaft
12, 12a, 12b Output gear
13 Support plate
14 Thrust ball bearing
15 Thrust needle bearing
16 Outer ring
17 Actuator
18 Drive shaft
19 Toroidal continuously variable transmission
20 Planetary gear mechanism
21 Ring gear
22 Support plate
23 Transmission shaft
24 High speed clutch
25 Pressing device
26 engine
27 Crankshaft
28 Starting clutch
29 Output shaft
30 sun gear
31a, 31b planetary gear
32 planetary gear set
33 Career
34 First power transmission mechanism
35 Transmission shaft
36a, 36b Sprocket
37 Chen
38 First gear
39 Second gear
40 Low speed clutch
41 Reverse clutch
42 Second power transmission mechanism
43, 43a Thrust generator
44, 44a Hydraulic actuator
45 Cam plate
46a, 46b Cam surface
47 Laura
48a, 48b Ball spline
49a, 49b Loading nut
50 inner ring
51, 51a, 51b Preload spring
52 Ball bearing
53 Disc leaf spring
54 Buttocks
55 Large diameter part
56 Seal plate
57, 57a Hydraulic chamber
58 Supply / Exhaust Route
59 Center hole
60, 60a radial bearing
61 fork
62 Cylinder housing
63 Spline tube
64 sleeve
65 Piston plate
66 Seal Ring
67 Retaining Ring
68 Buttocks
69 sleeve
70 recess
71 sleeve
72 Convex
73 Retaining ring
74 cotters

Claims (4)

  1.   An input side disk and an output side disk that are supported concentrically and rotatably in a state in which the inner side surfaces, which are concave surfaces each having a circular arc shape, are opposed to each other, and these input side disk and output side disk A plurality of trunnions that swing about a pivot that is twisted with respect to the central axis of the shaft, a displacement shaft that is supported in a state of projecting from the inner surface of each trunnion, and each of these trunnions A power roller that is disposed on the inner side of the trunnion and is rotatably supported around each displacement shaft in a state of being sandwiched between the input-side disk and the output-side disk and having a circumferential convex surface. And a toroidal continuously variable transmission including a thrust generating device that generates a thrust in a direction in which the input side disk and the output side disk approach each other, The thrust generating device includes a first thrust generating unit that generates a thrust in a direction in which the input side disk and the output side disk approach each other in relation to the torque input to the input side disk, and the first thrust generation unit. The second thrust generating unit is controlled separately from the thrust generated by the second thrust generating unit and generates a thrust in a direction in which the input side disk and the output side disk are moved away from each other. Toroidal-type continuously variable transmission.
  2.   The toroidal continuously variable transmission according to claim 1, wherein the first thrust generating unit is a loading cam device, and the second thrust generating unit is a hydraulic actuator.
  3. The toroidal continuously variable transmission according to any one of claims 1 to 2 , wherein the magnitude of the thrust generated by the first thrust generating unit is equal to or greater than the magnitude of the largest thrust required for the thrust generating device during operation. Machine.
  4. An input shaft connected to a drive source and driven to rotate by the drive source, an output shaft for taking out power based on the rotation of the input shaft, and a toroidal continuously variable transmission according to any one of claims 1 to 3 A planetary gear mechanism, a first power transmission mechanism that transmits power input to the input shaft via the toroidal continuously variable transmission, and power input to the input shaft to the toroidal continuously variable A second power transmission mechanism that transmits without passing through a transmission, and the planetary gear mechanism is provided between a sun gear and a ring gear arranged around the sun gear and is concentric with the sun gear. A planetary gear rotatably supported by a carrier that is rotatably supported meshes with the sun gear and the ring gear, and the power transmitted through the first power transmission mechanism and the second gear Power transmission Power transmitted through the sun gear, the ring gear, and the carrier, and the remaining one member of the sun gear, the ring gear, and the carrier. A continuously variable transmission having the output shaft coupled thereto.
JP2001165368A 2001-05-08 2001-05-31 Toroidal continuously variable transmission and continuously variable transmission Expired - Fee Related JP4378898B2 (en)

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JP2001137284 2001-05-08
JP2001165368A JP4378898B2 (en) 2001-05-08 2001-05-31 Toroidal continuously variable transmission and continuously variable transmission

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DE112004001100D2 (en) * 2003-06-17 2006-02-23 Ulrich Rohs Friction gear and method for operating such a friction gear
EP1581755B1 (en) 2003-01-06 2013-12-18 Rohs, Ulrich, Dr. Transmission with cone and friction ring, and method for operating such a friction gearing
US7011600B2 (en) 2003-02-28 2006-03-14 Fallbrook Technologies Inc. Continuously variable transmission
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