JP3674264B2 - Continuously variable transmission - Google Patents

Continuously variable transmission Download PDF

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Publication number
JP3674264B2
JP3674264B2 JP27691397A JP27691397A JP3674264B2 JP 3674264 B2 JP3674264 B2 JP 3674264B2 JP 27691397 A JP27691397 A JP 27691397A JP 27691397 A JP27691397 A JP 27691397A JP 3674264 B2 JP3674264 B2 JP 3674264B2
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Japan
Prior art keywords
input
rotation
shaft
continuously variable
variable transmission
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JP27691397A
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JPH11108149A (en
Inventor
尚 今西
慎司 宮田
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日本精工株式会社
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Priority to JP27691397A priority Critical patent/JP3674264B2/en
Priority claimed from DE1998136558 external-priority patent/DE19836558C2/en
Publication of JPH11108149A publication Critical patent/JPH11108149A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/02Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/086CVT using two coaxial friction members cooperating with at least one intermediate friction member

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an improvement of a continuously variable transmission incorporating a toroidal continuously variable transmission used as a transmission for an automobile, for example, and is small in size and can secure the durability of components of the toroidal continuously variable transmission. The structure is realized.
[0002]
[Prior art]
For example, the use of a toroidal continuously variable transmission as schematically shown in FIGS. This toroidal continuously variable transmission, for example, as disclosed in Japanese Utility Model Laid-Open No. 62-71465, supports an input side disk 2 concentrically with an input shaft 1, and outputs arranged concentrically with the input shaft 1. An output side disk 4 is fixed to the end of the shaft 3. On the inner side of the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 that swing around pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided.
[0003]
The pivots 5 and 5 are provided on the outer side surfaces of both ends of the trunnions 6 and 6. Further, by supporting the base ends of the displacement shafts 7 and 7 at the center of the trunnions 6 and 6, and by swinging the trunnions 6 and 6 around the pivot shafts 5 and 5, 7 tilt angle can be adjusted freely. Power rollers 8 and 8 are rotatably supported around the displacement shafts 7 and 7 supported by the trunnions 6 and 6, respectively. The power rollers 8 and 8 are sandwiched between the input side and output side disks 2 and 4. The inner side surfaces 2a and 4a of the input side and output side discs 2 and 4 facing each other have concave surfaces obtained by rotating arcs around the pivot shaft 5 around the central axes of the discs 2 and 4, respectively. There is no. And the peripheral surfaces 8a and 8a of each power roller 8 and 8 formed in the spherical convex surface are made to contact | abut to the said both inner surfaces 2a and 4a.
[0004]
A loading cam device 9 is provided between the input shaft 1 and the input side disc 2, and the loading cam device 9 presses the input side disc 2 toward the output side disc 4. The loading cam device 9 includes a cam plate 10 that rotates together with the input shaft 1 and a plurality of (for example, four) rollers 12 and 12 held by a cage 11. A cam surface 13 that is an uneven surface extending in the circumferential direction is formed on one side surface (left side surface in FIGS. 5 to 6) of the cam plate 10, and the outer side surface (right side in FIGS. 5 to 6) of the input side disk 2 is formed. The same cam surface 14 is also formed on the surface). The plurality of rollers 12 and 12 are supported so as to be rotatable about a radial axis with respect to the center of the input shaft 1.
[0005]
When the toroidal type continuously variable transmission configured as described above is used, when the cam plate 10 rotates with the rotation of the input shaft 1, the plurality of rollers 12, 12 are moved by the cam surface 13 to the outer surface of the input side disk 2. The cam surface 14 is pressed. As a result, the input side disk 2 is pressed against the plurality of power rollers 8 and 8 and at the same time, based on the pressing force between the pair of cam surfaces 13 and 14 and the plurality of rollers 12 and 12, The input side disk 2 rotates. The rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, 8, and the output shaft 3 fixed to the output side disk 4 rotates.
[0006]
When the rotational speed of the input shaft 1 and the output shaft 3 is changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 6 and 6 are swung around the pivot shafts 5 and 5. As shown in FIG. 5, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 are respectively formed on a portion near the center of the inner surface 2a of the input side disk 2 and a portion near the outer periphery of the inner surface 4a of the output side disk 4. The displacement shafts 7 and 7 are inclined so as to contact each other. On the contrary, to increase the speed, the trunnions 6 and 6 are swung, and the peripheral surfaces 8a and 8a of the power rollers 8 and 8 are formed on the inner surface 2a of the input side disk 2 as shown in FIG. The displacement shafts 7 and 7 are inclined so as to come into contact with the outer peripheral portion and the central portion of the inner side surface 4a of the output side disk 4, respectively. If the inclination angles of the displacement shafts 7 and 7 are set intermediate between those shown in FIGS. 5 and 6, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
[0007]
Further, in order to increase the torque that can be transmitted, as shown in FIG. 7, two each of the input side disks 2 and 2 and the output side disks 4 and 4 are arranged in parallel with each other in the power transmission direction. A so-called double cavity type toroidal continuously variable transmission is also known in the past, as described in, for example, Japanese Patent Publication No. 7-96901. In the structure shown in FIG. 7, a sleeve 16 is loosely fitted around an intermediate portion of the rotation transmission shaft 15, and an output gear 17 is fixed to the outer peripheral surface of the intermediate portion of the sleeve 16. The sleeve 16 is rotatably supported by a pair of angular ball bearings 20 and 20 inside a through hole 19 provided in an intermediate wall 18 provided inside the case. The rotation transmission shaft 15 is inserted into the sleeve 16 so as to be rotatable with respect to the sleeve 16. Further, the output side disks 4 and 4 are splined to both ends of the sleeve 16. Needle bearings 21 and 21 are provided between the inner peripheral surfaces of the output side disks 4 and 4 and the outer peripheral surface of the rotation transmission shaft 15, and the output side disks 4 and 4 are connected to the rotation transmission shaft 15. Around the periphery, rotation with respect to the rotation transmission shaft 15 and displacement in the axial direction of the rotation transmission shaft 15 are supported freely. The input side disks 2 and 2 are rotatably supported at both ends of the rotation transmission shaft 15 together with the rotation transmission shaft 15 via ball splines 22 and 22, respectively.
[0008]
As described above, a so-called double-cavity toroidal continuously variable transmission in which two input-side disks 2 and 2 and output-side disks 4 and 4 are arranged in parallel with each other in the power transmission direction is an input shaft. The rotation of 1a is transmitted to one input side disk 2 (to the right in FIG. 7) via the loading cam device 9. As a result, the one input side disk 2 and the other (left side in FIG. 7) input side disk 2 rotate in synchronization with each other via the rotation transmission shaft 15. The rotation of the pair of input side disks 2 and 2 is transmitted to the pair of output side disks 4 and 4 via power rollers 8 and 8, respectively. 16 is transmitted to the output gear 17 via 16. Since the transmission of the rotational force from the input shaft 1a to the output gear 17 is performed via the input side disks 2 and 2 and the output side disks 4 and 4, respectively, a large amount of power (torque) is provided. It can be transmitted freely. The double-cavity toroidal continuously variable transmission as described above supports the input side disks 2 and 2 on the rotation transmission shaft 15 by ball splines 22 and 22 so as to be displaceable in the axial direction. The reason is that both the disks 2 and 2 are connected to the rotation transmission shaft 15 based on the elastic deformation of the constituent members accompanying the operation of the loading cam device 9 while completely synchronizing the rotation of the both disks 2 and 2. This is to allow displacement in the axial direction.
[0009]
Furthermore, when incorporating a toroidal type continuously variable transmission into an actual continuously variable transmission for an automobile, combining with a planetary gear mechanism is disclosed in JP-A-1-169169, 1-312266, and JP-T-5. As described in JP-A-502498, it has been conventionally proposed. This continuously variable transmission is configured such that a toroidal continuously variable transmission and a planetary gear mechanism are arranged in series with respect to the power transmission direction, and the connection state of the planetary gear mechanism is switched according to the traveling state. In the case of such a continuously variable transmission, by combining a toroidal continuously variable transmission and a planetary gear mechanism, a gear ratio larger than that obtained by a toroidal continuously variable transmission alone is realized.
[0010]
[Structure considered prior to the present invention]
When the structure combining the toroidal type continuously variable transmission and the planetary gear mechanism as described above is implemented in the double cavity type toroidal type continuously variable transmission as described above, as shown in FIG. 8 or FIG. It can be considered to be a structure. First, the structure and operation of the first and second continuously variable transmissions shown in FIGS. 8 to 9 will be briefly described.
[0011]
In the following description, mode 1 in the structure of FIG. 8 is a relatively large mode in which the planetary gear mechanism is disconnected and power is transmitted only by the toroidal type continuously variable transmission when traveling at low speed including acceleration. Mode 2 represents a mode for obtaining the reduction ratio, and mode 2 represents a mode in which the planetary gear mechanism is used to reduce the reduction ratio (increase the speed increase ratio) when traveling at a constant speed or the like. On the other hand, mode 1 in the structure of FIG. 9 is to rotate the output shaft in the reverse direction in the opposite direction at a relatively low speed, or to obtain a relatively large reduction ratio such as during low speed running including acceleration, Mode 2 is a mode in which the planetary gear mechanism is used, and mode 2 is a mode in which power transmission is performed only by a toroidal type continuously variable transmission, such as during constant speed running, to reduce the reduction ratio. 8 and 9, the number of teeth of each of the gears 28, 29, 31 constituting the planetary gear mechanisms 24, 24a and the output of the toroidal continuously variable transmission 23 are input to the planetary gear mechanisms 24, 24a. The number of teeth of the drive side and driven side sprockets 27 and 35, and the drive and driven gears 37 and 38 for the purpose is determined in accordance with the characteristics required for the planetary gear mechanisms 24 and 24a.
[0012]
First, the structure of the first continuously variable transmission shown in FIG. 8 will be described. The first continuously variable transmission includes a double cavity type toroidal continuously variable transmission 23, Planetary gear mechanism 24. Of these, the structure and operation of the toroidal-type continuously variable transmission 23 are basically the same as those of the conventional structure shown in FIG. 7 described above. The description is omitted or simplified. The output of the engine 25 is transmitted to the input shaft 1a via the starting clutch 26, and the rotation of the input shaft 1a is transmitted to a pair of input disks 2, 2, a plurality of power rollers (not shown), and a pair of output sides. The drive side sprocket 27 fixed to the outer peripheral surface of the intermediate portion of the sleeve 16 is rotated via the disks 4 and 4 and transmitted to the sleeve 16.
[0013]
On the other hand, the planetary gear mechanism 24 is provided between a sun gear 28, a ring gear 29 disposed concentrically around the sun gear 28, and between the sun gear 28 and the ring gear 29. A carrier 30 that is concentrically and rotatably supported, and a plurality of planetary gears 31 and 31 that are rotatably supported by the carrier 30 and mesh with the sun gear 28 and the ring gear 29 are provided. The carrier 30 constituting such a planetary gear mechanism 24 has a rotation transmission shaft 15 constituting the toroidal-type continuously variable transmission 23. of The end portions are connected via the mode 2 clutch 32 and the driven shaft 33. Similarly, the rotation of the drive side sprocket 27 can be input to the sun gear 28 via a chain 34, a driven side sprocket 35, a transmission shaft 36, a drive gear 37, and a driven gear 38. Further, the base end portion (left end portion in FIG. 8) of the output shaft 39 is coupled to the center portion of the ring gear 29, and the tip end portion (right end portion in FIG. 8) of the output shaft 39 is connected to a cover such as a differential gear. The drive unit 40 is coupled. Further, a mode 1 clutch 41 is provided between the ring gear 29 and the carrier 30, and a reverse clutch 42 is provided between the carrier 30 and a fixed part such as a casing of the continuously variable transmission. Yes. These three clutches 32, 41 and 42 including the above-mentioned mode 2 clutch 32 connect only one clutch according to the required mode, and disconnect the remaining two clutches. Function.
[0014]
The operation of the first continuously variable transmission configured as described above is as follows. When it is not necessary to increase the rotational speed of the output shaft 39, such as when the vehicle is running at a low speed including acceleration, the clutch 41 for mode 1 is connected when it is necessary to input a large torque to the driven part 40. Then, the mode 32 clutch 32 and the reverse clutch 42 are disconnected. As a result, the relative rotation of the gears 28, 29, 31, 31 constituting the planetary gear mechanism 24 is blocked, and the planetary gear mechanism 24 is in a state of transmitting the rotation of the sun gear 28 to the ring gear 29 as it is. . In this state, the rotation of the drive side sprocket 27 constituting the toroidal type continuously variable transmission 23 is transmitted to the output shaft 39 via the chain 34, the driven side sprocket 35, the transmission shaft 36, the drive gear 37, and the driven gear 38. . In this state, the first continuously variable transmission operates like the simple double cavity toroidal continuously variable transmission that does not have the planetary gear mechanism 24 and rotationally drives the driven part 40. That is, in this state, the ring gear 29 and the output shaft 39 coupled and fixed to the ring gear 29 are connected to the sun gear 28 and the carrier. 30 And rotate at the same speed. In this mode 1, the speed ratio of the toroidal continuously variable transmission 23 is increased as the speed ratio between the input shaft 1a and the output shaft 39 is increased (High). .
[0015]
On the other hand, it is necessary to increase the speed increasing ratio between the input shaft 1a and the output shaft 39, such as when driving at a constant speed at high speed, but the driven part 40 When it is not necessary to apply a large torque to the clutch, the mode 2 clutch 32 is connected, and the mode 1 clutch 41 and the reverse clutch 42 are disconnected. As a result, the sun gear 28 constituting the planetary gear mechanism 24 rotates with the rotation of the drive side sprocket 27 constituting the toroidal-type continuously variable transmission 23, and at the same time, the carrier 30 also rotates. As a result, based on the differential function of the planetary gear mechanism 24, the ring gear 29 constituting the planetary gear mechanism 24 and the output shaft 39 coupled and fixed to the ring gear 29 rotate at a higher speed than the carrier 30. In this mode 2, as the speed ratio between the input shaft 1a and the output shaft 39 is increased, the speed ratio of the toroidal continuously variable transmission 23 is reduced (Low).
[0016]
Furthermore, at the time of reverse, the reverse clutch 42 is connected, Mode 2 Clutch 32 and Mode 1 The clutch 41 is disconnected. As a result, the rotation of the carrier 30 constituting the planetary gear mechanism 24 is prevented, and the planetary gears 31 and 31 rotatably supported by the carrier 30 are in a state in which only revolving motion is possible (revolution is impossible). Become. In this state, the rotation of the drive side sprocket 27 constituting the toroidal type continuously variable transmission 23 is caused by the chain 34, the driven side sprocket 35, the transmission shaft 36, the drive gear 37, the driven gear 38, the sun gear 28, the planetary gear 31, 31, and is transmitted to the output shaft 39 via the ring gear 29. In this state, the first continuously variable transmission rotates the driven unit 40 in the direction opposite to that in the mode 1 and the mode 2 described above.
[0017]
Next, the structure of the second continuously variable transmission shown in FIG. 9 will be described. This second continuously variable transmission is also a double cavity type toroidal continuously variable transmission 23, Planetary gear mechanism 24a. In the case of this second continuously variable transmission, the mode 2 clutch 32a is Planetary gear mechanism It is provided between the ring gear 29 and the carrier 30 constituting 24a. Further, the mode 1 clutch 41 a is provided between the end of the rotation transmission shaft 15 constituting the toroidal-type continuously variable transmission 23 and the driven shaft 33. Further, since the output shaft 39 is rotated in the reverse direction for reversing, it can be realized by changing the gear ratio of the toroidal-type continuously variable transmission 23 in mode 1, so that a reversing clutch is unnecessary. Furthermore, the toroidal type continuously variable transmission in mode 1 23 By adjusting the speed ratio, the output shaft 39 can be stopped while the input shaft 1a is rotated, so that the starting clutch 26 is also unnecessary.
[0018]
The second continuously variable transmission configured as described above connects the mode 1 clutch 41a and disconnects the mode 2 clutch 32a during low speed running including reverse or acceleration. As a result, the sun gear 28 constituting the planetary gear mechanism 24a rotates with the rotation of the drive side sprocket 27 constituting the toroidal-type continuously variable transmission 23, and at the same time, the carrier 30 also rotates. And the planetary gear mechanism 24 a The planetary gear mechanism 24 based on the differential function of a Is rotated. In this state, the driven part 40 can be driven to rotate at a lower speed and with a larger torque than in the case of a continuously variable transmission incorporating only the toroidal type continuously variable transmission 23. In this mode 1, as the speed ratio between the input shaft 1a and the output shaft 39 is increased (on the forward side), the speed ratio of the toroidal continuously variable transmission 23 is reduced (Low ) Side.
[0019]
On the other hand, when traveling at a constant speed, the mode 2 clutch 32a is connected, and the mode 1 clutch 41a is disconnected. As a result, the planetary gear mechanism 24 a Relative rotation of the gears 28, 29, 31, 31 constituting the planetary gear mechanism 24 is prevented. a Is the above Sun gear The rotation of 28 is transmitted to the ring gear 29 as it is. In this state, the rotation of the drive side sprocket 27 constituting the toroidal type continuously variable transmission 23 is transmitted to the output shaft 39 via the chain 34, the driven side sprocket 35, the transmission shaft 36, the drive gear 37, and the driven gear 38. . In this state, the second continuously variable transmission is the planetary gear mechanism 24. a The above-mentioned driven part operates in the same manner as a simple double cavity type toroidal continuously variable transmission without 40 Is driven to rotate. Of course, this mode 2 Then, as the gear ratio between the input shaft 1a and the output shaft 39 is increased (High), the gear ratio of the toroidal continuously variable transmission 23 is increased.
[0020]
[Problems to be solved by the invention]
In any of the structures shown in FIGS. 8 to 9, the thrust in the thrust direction generated by the loading cam device 9 constituting the toroidal-type continuously variable transmission 23 corresponds to the output of the engine 25. On the other hand, the torque transmitted through the input side disks 2 and 2, the power roller, and the output side disks 4 and 4 constituting the toroidal type continuously variable transmission 23 does not necessarily become the output torque of the engine 25. . That is, in the case of the first continuously variable transmission shown in FIG. 8, with the mode 2 clutch 32 connected, the input side disks 2, 2, the power roller, and the output side disks 4, 4 are passed through. The transmitted torque is smaller than the output torque of the engine 25. On the other hand, in the case of the second continuously variable transmission shown in FIG. 9, the input side disks 2, 2, the power roller, and the output side disk are mostly in the state where the mode 1 clutch 41a is connected. The torque transmitted through the motors 4 and 4 is larger than the output torque of the engine 25.
[0021]
When the torque transmitted through the input side disks 2 and 2, the power rollers and the output side disks 4 and 4 becomes smaller than the output torque of the engine 25, the inner surface of each disk 2 and 4 and the circumference of each power roller The contact pressure with the surface becomes excessive, and the rolling fatigue life of each surface decreases. On the other hand, when the torque transmitted through the input side disks 2 and 2, the power roller, and the output side disks 4 and 4 becomes larger than the output torque of the engine 25, The contact pressure with the peripheral surface of each power roller is insufficient, slip occurs at the contact portion of each surface, and the efficiency of the continuously variable transmission decreases.
[0022]
If the pressing device for bringing the inner surfaces of the disks 2 and 4 into contact with the peripheral surfaces of the power rollers is a hydraulic device instead of the loading cam device, it can be used according to the operating condition of the continuously variable transmission. Thus, the contact pressure can be adjusted. However, the hydraulic pressing device requires a pump device for generating high-pressure oil pressure, and problems such as an increase in engine power loss newly arise. In view of such circumstances, the continuously variable transmission according to the present invention is provided with the above-described loading cam in order to prevent a decrease in rolling fatigue life and occurrence of slippage even when a mechanical loading cam device 9 is used as a pressing device. A structure in which the thrust force generated by the device 9 in the thrust direction has a magnitude corresponding to the torque transmitted through the input side disks 2 and 2, the power roller, and the output side disks 4 and 4 is realized. .
[0023]
[Means for Solving the Problems]
A continuously variable transmission according to the present invention includes an input shaft connected to a drive source and rotationally driven by the drive source, an output shaft for extracting power based on the rotation of the input shaft, a toroidal continuously variable transmission, And a planetary gear mechanism.
The toroidal-type continuously variable transmission includes a rotation transmission shaft arranged concentrically with the input shaft, and a pair of input side disks supported with both inner surfaces facing each other at both ends of the rotation transmission shaft And with the respective inner surfaces facing the inner surfaces of the respective input-side discs, the intermediate portions of the rotation transmission shafts can freely rotate with respect to the rotation transmission shafts and can freely support rotations synchronized with each other. A pair of output side disks, a plurality of power rollers sandwiched between the input side disks and the output side disks, and the pair of input side disks as the input shaft rotates. A loading cam device that rotates the one input side disk while pressing the one input side disk toward the other input side disk, and changes the inclination angle of each power roller in synchronization with each other. Is to vary the transmission ratio between the input side disks and the output side disks rotated based on rotation of the input shaft.
The planetary gear mechanism is provided with a sun gear, a ring gear disposed concentrically around the sun gear, and adjacent to the sun gear and the ring gear, and is supported concentrically and rotatably with the sun gear. A carrier and a planetary gear that is rotatably supported by the carrier and meshed with the sun gear and the ring gear are provided. Then, rotation of the rotation transmission shaft can be freely input to any one member of the sun gear, ring gear and carrier, and rotation of the pair of output side disks can be input to the sun gear, ring gear and carrier. The rotation of the rotation transmission shaft can be input to one of the other members to which the rotation of the rotation transmission shaft is not transmitted, and the rotation transmission shaft can be rotated and output by any of the sun gear, the ring gear, and the carrier. The remaining one member that is not transmitted with any rotation of the side disk is coupled to the output shaft.
Further, the input shaft and the rotation transmission shaft are rotatably coupled in synchronization with each other. Of the pair of input side discs, the input side disc on the loading cam device side is rotatable with respect to the rotation transmission shaft. It is supported and can rotate with the rotation of the input shaft via the loading cam device, and the input side disk on the side away from the loading cam device is synchronized with the rotation transmission shaft on the rotation transmission shaft. It is connected freely.
[0024]
[Action]
The operation of the continuously variable transmission according to the present invention configured as described above when transmitting the rotational force between the input shaft and the output shaft is the same as that described above with reference to FIGS. This is similar to the case of the first and second continuously variable transmissions. In particular, in the case of the continuously variable transmission according to the present invention, since the input side disk on the loading cam device side is rotatable along with the rotation of the input shaft through the loading cam device, the loading cam device is The magnitude of the force that presses the input side disk is in accordance with the torque transmitted through the input side disk, the power roller, and the output side disk.
[0025]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 shows a first example of an embodiment of the present invention. The continuously variable transmission of the present invention is characterized in that the loading cam device 9 presses one (left side in FIG. 1) input side disk 2 against the other (right side in FIG. 1) input side disk 2. The size is adjusted to a size corresponding to the torque transmitted through the input side disks 2 and 2, a power roller (not shown), and the output side disks 4 and 4. In the case of this example, the configuration and operation of the other parts are the same as in the case of the continuously variable transmission previously considered shown in FIG. The description will be omitted or simplified, and the following description will focus on the features of the present invention.
[0026]
The input shaft 1a and the rotation transmission shaft 15 are integrally coupled so as to freely rotate in synchronization. That is, the input shaft 1a and the rotation transmission shaft 15 are constituted by a single shaft, and both the shafts 1a and 15 can be rotated in synchronization. Further, in order to constitute the double cavity type toroidal type continuously variable transmission 23, the loading cam device 9 side (FIG. 1) of the pair of input side disks 2 and 2 supported at both ends of the rotation transmission shaft 15 is used. The left side input side disk 2 is supported around one end portion (left end portion in FIG. 1) of the rotation transmission shaft 15 by a bearing 43 that allows rotation and axial displacement, such as a radial needle bearing. Accordingly, the input-side disk 2 on the loading cam device 9 side is supported around one end of the rotation transmission shaft 15 so as to be rotatable and displaceable in the axial direction. Such an input side disk 2 on the loading cam device 9 side is rotationally driven via the loading cam device 9 as the input shaft 1a and the rotation transmission shaft 15 rotate.
[0027]
On the other hand, the input side disk 2 on the side away from the loading cam device 9 (right side in FIG. 1) is fixed or splined to the other end of the rotation transmission shaft 15 and rotated in synchronization with the rotation transmission shaft 15. Is free. Therefore, the input side disk 2 on the side away from the loading cam device 9 rotates in synchronization with the input shaft 1a.
[0028]
As described above, in the case of the continuously variable transmission according to the present invention, the input-side disk 2 on the loading cam device 9 side is rotatable with the rotation of the input shaft 1 a via the loading cam device 9. For this reason, the loading cam device 9 is connected to the input side disk. 2 The magnitude of the force that presses the pressure is in accordance with the torque transmitted through the input side disks 2 and 2, the power roller (not shown), and the output side disks 4 and 4 constituting the toroidal continuously variable transmission 23. become. For example, when the continuously variable transmission is operated with the mode 2 clutch 32 and the reverse clutch 42 disconnected and the mode 1 clutch 41 connected, the input side disk 2 constituting the toroidal type continuously variable transmission 23 will be described. 2, the output torque of the engine 25 flows through the power roller (not shown) and the output side disks 4 and 4. In this case, the loading cam device 9 presses the input side disc 2 on the loading cam device 9 side toward the input side disc 2 on the side away from the loading cam device 9 with a force corresponding to the output torque. The same applies to the case where the continuously variable transmission is operated with the mode 32 clutch 32 and the mode 1 clutch 41 disconnected and the reverse clutch 42 connected.
[0029]
On the other hand, when the continuously variable transmission is operated with the mode 1 clutch 41 and the reverse clutch 42 disconnected and the mode 2 clutch 32 connected, the input constituting the toroidal continuously variable transmission 23 is performed. Torque smaller than the output torque of the engine 25 flows through the side disks 2 and 2, the power roller (not shown), and the output side disks 4 and 4. In this case, the loading cam device 9 presses the input side disc 2 on the loading cam device 9 side toward the input side disc 2 on the side away from the loading cam device 9 with a force corresponding to a torque smaller than the output torque. To do. Therefore, in any case, the contact pressure between the inner surface of both the input and output disks 2 and 4 and the peripheral surface of the power roller is made appropriate, and the contact pressure between these surfaces becomes excessive, or Can prevent slippage at the abutting portions of these surfaces.
[0030]
Next, FIG. 2 shows a second example of the embodiment of the present invention. In this example, the present invention is applied to the second continuously variable transmission shown in FIG. The basic configuration of the continuously variable transmission is the same as that of the above-described continuously variable transmission shown in FIG. 9, and the loading cam device 9 has one input side disk 2 (left side in FIG. 2). The magnitude of the force applied to the other input side disk 2 (on the right side in FIG. 2) depends on the torque transmitted through these input side disks 2, 2, a power roller (not shown), and output side disks 4, 4. The configuration and operation of the portion to be adjusted to the same size are the same as in the case of the first example shown in FIG. Therefore, the same parts as those in FIG. 9 or FIG.
[0031]
Next, FIGS. 3 to 4 show third to fourth examples of the embodiment of the present invention. In the case of these third to fourth examples, the second clutch 32b for mode 2 (in the case of the third example shown in FIG. 3) or the clutch 41b for mode 1 (in the case of the fourth example shown in FIG. 4) A planetary gear mechanism 44 is attached. In the cases of the third to fourth examples, the carrier of the planetary gear mechanisms 24 and 24a is connected with the mode 2 clutch 32b or the mode 1 clutch 41b connected based on the presence of the second planetary gear mechanism 44. The rotational speed of 30 is slower than the rotational speed of the rotation transmission shaft 15. Since the configuration and operation other than changing the rotation speed of the output shaft 39 by reducing the rotation speed of the carrier 30 in this manner are the same as those in the first example or the second example described above, Equivalent parts are denoted by the same reference numerals, and redundant description is omitted.
[0032]
【The invention's effect】
Since the present invention is configured and operates as described above, the inner surface of both the input side and output side disks constituting the toroidal type continuously variable transmission incorporated in the continuously variable transmission and the peripheral surface of the power roller are in contact with each other. Proper contact pressure prevents excessive contact pressure on each of these surfaces, or prevents slippage at the contact portions of each of these surfaces, improving durability or improving efficiency. I can plan.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram showing a first example of an embodiment of the present invention.
FIG. 2 is a schematic configuration diagram showing the second example.
FIG. 3 is a schematic configuration diagram showing the third example.
FIG. 4 is a schematic configuration diagram showing a fourth example.
FIG. 5 is a partially cut side view showing a conventionally known toroidal continuously variable transmission in a state of maximum deceleration.
FIG. 6 is a partially cut side view showing the state of the maximum speed increase.
FIG. 7 is a cross-sectional view of a main part showing an example of a conventionally known double cavity type continuously variable transmission.
FIG. 8 is a schematic configuration diagram showing a first example of a continuously variable transmission considered prior to the present invention.
FIG. 9 is a schematic configuration diagram showing the second example.
[Explanation of symbols]
1, 1a Input shaft
2 Input disk
2a inner surface
3 Output shaft
4 Output disk
4a inner surface
5 Axis
6 Trunnion
7 Displacement axis
8 Power roller
8a circumference
9 Loading cam device
10 Cam plate
11 Cage
12 Laura
13, 14 Cam surface
15 Rotation transmission shaft
16 sleeve
17 Output gear
18 Middle wall
19 through holes
20 Ball bearing
21 Needle bearing
22 Ball spline
23 Toroidal continuously variable transmission
24, 24a Planetary gear mechanism
25 engine
26 Starting clutch
27 Drive side sprocket
28 Sun Gear
29 Ring gear
30 career
31 planetary gear
32, 32a, 32b Mode 2 clutch
33 Driven shaft
34 Chen
35 Driven side sprocket
36 Transmission shaft
37 Drive gear
38 Driven gear
39 Output shaft
40 Driven parts
41, 41a, 41b Mode 1 clutch
42 Reverse clutch
43 Bearing
44 Second planetary gear mechanism

Claims (1)

  1. An input shaft connected to the drive source and driven to rotate by the drive source; an output shaft for extracting power based on the rotation of the input shaft; a toroidal continuously variable transmission; and a planetary gear mechanism;
    The toroidal-type continuously variable transmission includes a rotation transmission shaft arranged concentrically with the input shaft, and a pair of input side disks supported with both inner surfaces facing each other at both ends of the rotation transmission shaft And with the respective inner surfaces facing the inner surfaces of the respective input-side discs, the intermediate portions of the rotation transmission shafts can freely rotate with respect to the rotation transmission shafts and can freely support rotations synchronized with each other. A pair of output side disks, a plurality of power rollers sandwiched between the input side disks and the output side disks, and the pair of input side disks as the input shaft rotates. A loading cam device that rotates the one input side disk while pressing the one input side disk toward the other input side disk, and changes the inclination angle of each power roller in synchronization with each other. Is intended to alter the transmission ratio between the input side disks and the output side disks rotated based on rotation of the input shaft,
    The planetary gear mechanism includes a sun gear, a ring gear arranged concentrically around the sun gear, a carrier provided adjacent to the sun gear and the ring gear, and supported concentrically and rotatably with the sun gear. A planetary gear rotatably supported by the carrier and meshed with the sun gear and the ring gear, and the rotation transmission shaft is rotated by any one of the sun gear, the ring gear and the carrier. Rotation of the pair of output side disks is freely input to one member where rotation of the rotation transmission shaft is not transmitted by any of the sun gear, ring gear and carrier. The remaining one member to which neither the rotation of the rotation transmission shaft nor the rotation of the output side disk is transmitted by any of the sun gear, the ring gear and the carrier is coupled to the output shaft. ,
    The input shaft and the rotation transmission shaft are coupled so as to be rotatable in synchronization with each other. Of the pair of input side disks, the input side disk on the loading cam device side is rotatably supported with respect to the rotation transmission shaft. Thus, the input disk can be rotated by the rotation of the input shaft via the loading cam device, and the input side disk on the side away from the loading cam device can be rotated by the rotation transmission shaft in synchronization with the rotation transmission shaft. A continuously variable transmission that is coupled to
JP27691397A 1997-10-09 1997-10-09 Continuously variable transmission Expired - Fee Related JP3674264B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP27691397A JP3674264B2 (en) 1997-10-09 1997-10-09 Continuously variable transmission

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP27691397A JP3674264B2 (en) 1997-10-09 1997-10-09 Continuously variable transmission
DE1998136558 DE19836558C2 (en) 1997-08-12 1998-08-12 Infinitely adjustable toroidal gear system
US09/132,669 US6171210B1 (en) 1997-08-12 1998-08-12 Toroidal type continuous variable transmission system

Publications (2)

Publication Number Publication Date
JPH11108149A JPH11108149A (en) 1999-04-20
JP3674264B2 true JP3674264B2 (en) 2005-07-20

Family

ID=17576142

Family Applications (1)

Application Number Title Priority Date Filing Date
JP27691397A Expired - Fee Related JP3674264B2 (en) 1997-10-09 1997-10-09 Continuously variable transmission

Country Status (1)

Country Link
JP (1) JP3674264B2 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10013179A1 (en) * 2000-03-17 2001-09-20 Zahnradfabrik Friedrichshafen Automotive continuously variable transmission component arrangement occupies less space
US7014588B2 (en) 2001-08-16 2006-03-21 Nsk Ltd. Toroidal-type continuously variable transmission and continuously variable transmission apparatus
DE102005024738A1 (en) * 2005-05-31 2006-12-14 Zf Friedrichshafen Ag A power split transmission comprising a variator
JP5614148B2 (en) * 2010-07-28 2014-10-29 日本精工株式会社 Continuously variable transmission
JP5862184B2 (en) * 2011-10-13 2016-02-16 日本精工株式会社 Continuously variable transmission

Also Published As

Publication number Publication date
JPH11108149A (en) 1999-04-20

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