WO2017138396A1 - Stepless transmission - Google Patents

Abstract

This stepless transmission (1) has a transmission motor (7), a clamping motor (8), a control device (9), and a variator (2). The variator (2) has a primary pulley (3), a secondary pulley (4), and a belt (5). The stepless transmission (1) also has a planetary gear mechanism (6) and screw-feeding mechanisms (35, 45) so that the speed of the variator (2) is changed on the basis of the output torque of the transmission motor (7) and the transmission ratio of the variator (2) is fixed on the basis of the output torque of the clamping motor (8).

Description

Continuously variable transmission

The present invention relates to a continuously variable transmission.

A belt-type continuously variable transmission for a vehicle has a variator in which a belt is wound around a pair of pulleys (a primary pulley and a secondary pulley). The gear ratio is realized.

In the pulley, a V groove around which the belt is wound is formed between the sheave surface of the fixed pulley and the sheave surface of the movable pulley provided so as to be movable in the rotation axis direction at the shaft portion of the fixed pulley. By moving the movable pulley in the direction of the rotation axis and changing the groove width of the V-groove, the belt winding radius in the pulley is changed.

Patent Document 1 discloses a continuously variable transmission configured to convert a rotational driving force of a motor into a thrust in the direction of the rotation axis by a linear motion mechanism and to displace the movable pulley in the direction of the rotation axis.

Here, in the pulley, a stress that attempts to displace the movable pulley in the direction of widening the groove width of the V-groove acts from the belt wound around the pulley. If the movable pulley is displaced by this stress and the belt wrapping radius in the pulley changes, the speed ratio realized by the continuously variable transmission changes.
Therefore, the continuously variable transmission of Patent Document 1 employs a motor having a high holding torque in a non-excited state, and maintains the gear ratio by the high locking force of this motor.

However, in the continuously variable transmission of Patent Document 1, since the belt is merely locked to the pulley, and the belt is not actively clamped by the pulley, the belt slips when a high torque is input to the pulley. May occur.
Therefore, it is required to generate a clamping force for clamping the belt.

JP 2002-54706 A

The present invention
A first motor;
A second motor;
A variator having a first pulley, a second pulley, and a belt wound around the first pulley and the second pulley;
With
The continuously variable transmission is configured to shift the variator based on the torque of the first motor, while fixing the speed ratio of the variator based on the torque of the second motor.

According to the present invention, by having the second motor, it is possible to generate a clamping force when fixing the gear ratio of the variator.

1 is a schematic configuration diagram of a belt-type continuously variable transmission according to an embodiment. It is a figure explaining a screw feed mechanism. It is a figure explaining the control aspect of a motor. It is a figure explaining transmission of torque. It is a figure explaining transmission of torque.

Embodiments of the present invention will be described below.
FIG. 1 is a schematic configuration diagram of a belt-type continuously variable transmission 1 according to an embodiment.
In FIG. 1, for convenience of explanation, only half of the primary pulley 3 and the secondary pulley 4 that are inside the rotation axes X1 and X2 are shown.

As shown in FIG. 1, a continuously variable transmission 1 for a vehicle includes a primary pulley 3, a secondary pulley 4, and a belt 5 wound around the primary pulley 3 and the secondary pulley 4. 2 has.
In this variator 2, the ratio (speed ratio) between the input rotational speed of the input shaft 21 and the output rotational speed of the output shaft 22 of the variator 2 is changed by changing the winding radius of the belt 5 in the primary pulley 3 and the secondary pulley 4. It is designed to change steplessly.

In the continuously variable transmission 1, when a rotational driving force of a driving source (not shown) is input to the variator 2 via the torque converter T / C and the input shaft 21, the input rotational driving force is desired in the variator 2. After the gear ratio is changed, the output is made to the drive wheel side (not shown) via the output shaft 22 and the differential device DEF.

The primary pulley 3 includes a fixed pulley 31 and a movable pulley 32 provided by extrapolating a cylindrical shaft portion 321 to the shaft portion 311 of the fixed pulley 31. The primary pulley 3 is movable with the fixed pulley 31. The pulley 32 is connected so as to be relatively movable along the axial direction of the rotation axis X1 in a state where relative rotation about the rotation axis X1 is restricted.

In the fixed pulley 31 and the movable pulley 32, the opposing surfaces of the sheave portions 312 and 322 extending in the radial direction from the shaft portions 311 and 321 are sheave surfaces 312a and 322a inclined at a predetermined angle with respect to the rotation axis X1. A V-groove 33 around which the belt 5 is wound is formed between the sheave surfaces 312a and 322a.

The secondary pulley 4 includes a fixed pulley 41 and a movable pulley 42 that is provided by extrapolating a cylindrical shaft portion 421 to the shaft portion 411 of the fixed pulley 41. The secondary pulley 4 is movable with the fixed pulley 41. The pulley 42 is connected so as to be relatively movable along the axial direction of the rotation axis X2 in a state where relative rotation about the rotation axis X2 is restricted.

In the fixed pulley 41 and the movable pulley 42, the opposing surfaces of the sheave portions 412 and 422 extending in the radial direction from the shaft portions 411 and 421 are sheave surfaces 412a and 422a inclined at a predetermined angle with respect to the rotation axis X2. A V-groove 43 around which the belt 5 is wound is formed between the sheave surfaces 412a and 422a.

In the primary pulley 3 and the secondary pulley 4, screw feeding mechanisms 35, 45 are provided on the opposite side of the sheave portions 322 a, 422 from the sheave surfaces 322 a, 422 a. , 43 is configured to generate a thrust force that presses the movable pulleys 32, 42 in the direction of narrowing the groove width.

2A and 2B are diagrams for explaining the screw feeding mechanisms 35 and 45. FIG. 2A is a diagram schematically showing a main part of the screw feeding mechanism 35, and FIG. It is the figure which showed the part typically.
As shown in FIG. 2, the screw feed mechanisms 35 and 45 include inner members 36 and 46 that are extrapolated to the shaft portions 311 and 411 of the fixed pulleys 31 and 41, and cylindrical portions 361 of the inner members 36 and 46, And outer members 37 and 47 extrapolated to 461.
The inner members 36 and 46 are integrally formed from disk portions 362 and 462 that are orthogonal to the rotation axes X1 and X2, respectively, and cylindrical portions 361 and 461 that surround the outer periphery of the disk portions 362 and 462 over the entire circumference. Has been.

The inner peripheral portions 362a and 462a of the disk portions 362 and 462 are one of the bearings B1 and B1 that rotatably support the shaft portions 311 and 411 of the primary pulley 3 and the secondary pulley 4, and the rotation axis X1, X2 is positioned in the axial direction, and the inner members 36 and 46 are provided so as to be rotatable relative to the fixed pulleys 31 and 41 in a state where movement in a direction away from the fixed pulleys 31 and 41 is restricted. Yes.

The cylindrical portions 361 and 461 extend on the outer diameter side of the shaft portions 321 and 421 of the movable pulleys 32 and 42 toward the sheave portions 322 and 422 along the rotation axes X1 and X2, respectively. , 461 are provided with concave grooves 361a, 461a extending spirally along the circumferential direction around the rotation axes X1, X2.

The cylindrical pressing portions 371 and 471 of the outer members 37 and 47 are located on the outer diameter side of the cylindrical portions 361 and 461. The outer members 37 and 47 include the pressing portions 371 and 471, the cylindrical portions 372 and 472 having a larger outer diameter than the pressing portions 371 and 471, the outer periphery of the pressing portions 371 and 471, and the inner periphery of the cylindrical portions 372 and 472. Disk-shaped connecting portions 373 and 473 that connect the two.

The pressing portions 371 and 471 have lengths along the axial direction of the rotation axes X1 and X2 that are longer than the cylindrical portions 361 and 461 located on the inner diameter side, and are on one end side in the rotation axis X1 and X2 directions. The contact portions 371b and 471b are in contact with the sheave portions 322 and 422 of the movable pulleys 32 and 42 via the thrust bearing SB.
The pressing portions 371 and 471 are supported by the shaft portions 321 and 421 of the movable pulleys 32 and 42 through the bearings B2 and B2 in the regions closer to the contact portions 371b and 471b than the connection portions 373 and 473, respectively. The outer members 37 and 47 having the pressing portions 371 and 471 are provided to be rotatable relative to the movable pulleys 32 and 42.

In the pressing parts 371 and 471, concave grooves 371 a and 471 a extending in a spiral shape along the circumferential direction around the rotation axes X <b> 1 and X <b> 2 are provided on the inner periphery of the region facing the cylindrical parts 361 and 461. The balls Ba engaged with the concave grooves 371 a and 471 a of the pressing portions 371 and 471 are also engaged with the concave grooves 361 a and 461 a of the inner members 36 and 46.

In the embodiment, the inner members 36 and 46 having the concave grooves 361a and 461a, the outer members 37 and 47 having the concave grooves 371a and 471a, and the concave grooves 361a and 461a and the concave grooves 371a and 471a are straddled. A plurality of engaged balls Ba constitute screw feed mechanisms 35 and 45 (ball screw feed mechanism).
Therefore, when rotation is input to the outer members 37 and 47, the outer members 37 and 47 are rotated about the rotation axes X1 and X2 by the screw feed mechanisms 35 and 45, and the axial directions of the rotation axes X1 and X2 are rotated. It is displaced to.

The cylindrical portions 372 and 472 located on the outer diameter side of the pressing portions 371 and 471 are gears 62 and 64 on the planetary gear mechanism 6 side described later with tooth portions provided on the outer periphery of the cylindrical portions 372 and 472 (see FIG. 1). ). When rotational torque is input to the cylindrical portions 372 and 472 from the planetary gear mechanism 6 side and the outer members 37 and 47 rotate about the rotation axes X1 and X2, the outer members 37 and 47 are moved relative to the inner members 36 and 46, respectively. It is displaced in the direction of the rotation axis X1, X2.

In the embodiment, when changing the transmission gear ratio in the variator 2, the output torque (rotational torque) input from the planetary gear mechanism 6 side causes the screw feed mechanism 35 to press the movable pulley 32 with the pressing portion 371. When converted into the displacement of the outer member 37 in the direction of narrowing the groove width of the V-groove 33, the screw feed mechanism 45 causes the pressing portion 471 to move away from the movable pulley 42 (the groove width of the V-groove 43). The width of the outer member 47 is changed to a direction in which the widening of the outer member 47 is allowed.

Further, when changing the gear ratio in the variator 2, the output torque (rotational torque) input from the planetary gear mechanism 6 side causes the screw feed mechanism 35 to move the pressing portion 371 away from the movable pulley 32 (V groove). In the case of being converted into the displacement of the outer member 37 in the direction in which the widening of the groove width of 33 is permitted, in the screw feed mechanism 45, the direction in which the movable pulley 42 is pressed by the pressing portion 471 (the groove width of the V groove 43). It is converted into the displacement of the outer member 47 in the direction of narrowing.

As shown in FIG. 1, the planetary gear mechanism 6 uses at least one of the output torque (rotational driving force) of the transmission motor 7 and the output torque (rotational driving force) of the clamping motor 8 as a screw feed mechanism 35. , 45, and in the embodiment, the sun gear S, the ring gear R that surrounds the outer periphery of the sun gear S, the pinion gear P that meshes with the sun gear S and the ring gear R, and the pinion gear P are supported. A single pinion type planetary gear mechanism composed of a pinion carrier PC is adopted.

In the planetary gear mechanism 6, the motor pinion 72 of the speed change motor 7 meshes with the tooth portion 61 provided on the outer periphery of the ring gear R. The speed change motor 7 and the ring gear R are connected to each other so as to transmit rotation through a motor pinion 72 fixed to the output shaft 71 of the speed change motor 7 and a tooth portion 61 meshed with the motor pinion 72. .

Further, on the inner diameter side of the ring gear R, a sun gear S to which the output shaft 81 of the clamping motor 8 is connected is arranged coaxially with the ring gear R. The sun gear S capable of transmitting rotation between the clamping motor 8 and the ring gear R capable of transmitting rotation between the speed-changing motor 7 are provided so as to be relatively rotatable on a common rotation axis X.

Between the sun gear S and the ring gear R in the radial direction of the rotation axis X, a pinion gear P that meshes with an inner tooth (not shown) of the ring gear R and an outer tooth (not shown) of the sun gear S is provided. A plurality of pinion gears P are provided at predetermined intervals in the circumferential direction around the rotation axis X.
Each of the pinion gears P is supported by a pinion carrier PC provided so as to be rotatable around the rotation axis X. In the pinion carrier PC, each of the pinion gears P is rotated around a rotation axis Xc parallel to the rotation axis X. It is rotatably supported.

One end of a rotation transmission shaft 63 extending toward the variator 2 along the rotation axis X is connected to the pinion carrier PC, and a gear 64 is connected to the other end of the rotation transmission shaft 63.
The gear 64 meshes with the outer member 47 of the screw feed mechanism 45 described above. When the pinion carrier PC rotates about the rotation axis X, the rotation transmission shaft 63 and the gear 64 rotate together with the pinion carrier PC. , The output torque of the planetary gear mechanism 6 is input to the screw feed mechanism 45.

Further, an annular gear 62 is connected to the ring gear R so as to be integrally rotatable.
The gear 62 meshes with the outer member 37 of the screw feed mechanism 35 described above. When the ring gear R rotates about the rotation axis X, the output torque of the planetary gear mechanism 6 is also input to the screw feed mechanism 35. .

The planetary gear mechanism 6 uses a torque for changing a gear ratio in the variator 2 based on an output torque (rotational driving force) of the transmission motor 7 and an output torque (rotational driving force) of the clamping motor 8, It is provided to adjust the torque for fixing the ratio.

In the embodiment, when changing the gear ratio in the variator 2, the output torque (rotational torque) of the motor output via the planetary gear mechanism 6 is converted into the outer member 37, by the screw feed mechanisms 35, 45. 47 is converted into a thrust force that displaces the rotary shafts X1 and X2 in the direction, and one of the outer member 37 and the outer member 47 presses the movable pulleys 32 and 42, and the movable pulleys 32 and 42 are rotated. Displace in the X1 and X2 directions.
Here, as the amount of rotation input to the screw feed mechanisms 35 and 45 increases, the amount of displacement of the movable pulleys 32 and 42 increases. Therefore, when the movable pulleys 32 and 42 are displaced in the directions of the rotation axes X1 and X2, The output torque of the motor with the largest maximum number of revolutions (transmission motor 7) is input to the screw feed mechanisms 35 and 45.

When the movable pulleys 32 and 42 are held at predetermined positions in the directions of the rotation axes X1 and X2, the output torque (rotational torque) of the motor adjusted by the planetary gear mechanism 6 is adjusted by the screw feed mechanisms 35 and 45. The outer member 37, 47 is converted into a holding force that holds the outer member 37, 47 at a predetermined position in the direction of the rotation axis X1, X2 (regulation force that restricts the rotation of the outer member 37, 47), and the rotation axis X1 of the outer member 37 and the outer member 47 , Displacement in the X2 direction is restricted.
Here, the greater the torque input to the screw feed mechanisms 35 and 45, the stronger the force that regulates the displacement of the movable pulleys 32 and 42. Therefore, the movable pulleys 32 and 42 are moved at predetermined positions in the directions of the rotation axes X1 and X2. At the time of holding, the output torque of the motor (clamping motor 8) having a large maximum output torque is input to the screw feed mechanisms 35 and 45.

In the embodiment, adjustment of the output torque output from the planetary gear mechanism 6 is performed by the control device 9 that controls the drive of the motors (shifting motor 7 and clamping motor 8).
As control modes of the motors (shifting motor 7 and clamping motor 8) by the control device 9, (A) a mode for changing the gear ratio of the variator 2 (normal transmission mode), and (B) a gear ratio of the variator 2 Are prepared (speed change ratio fixed mode), and (C) an aspect (speed change assist mode) for quickly changing the speed change ratio of the variator 2 is prepared.

FIG. 3 is a diagram for explaining the control mode of the motor (shifting motor 7 and clamping motor 8) by the control device 9, and the relationship between the motor (shifting motor 7 and clamping motor 8) and the control mode. FIG.
FIG. 4 is a diagram for explaining a torque transmission path in a mode in which the output torque for shifting is output from the planetary gear mechanism 6.
FIG. 5 is a diagram for explaining a torque transmission path in a mode in which the output torque for clamping is output from the planetary gear mechanism 6.

[Normal shift mode]
As shown in FIG. 3 and FIG. 4, in the normal speed change mode, the control device 9 generates a holding torque by the clamping motor 8 and drives (forward or reverse) the speed changing motor 7. That is, the clamping force of the belt is generated by the clamping motor 8 while the variator 2 is shifted based on the torque of the shifting motor 7. That is, the variator 2 is shifted by changing the torque of the transmission motor 7 to generate a differential thrust between the primary pulley 3 and the secondary pulley 4.
In this case, the output torque (output rotation) of the speed change motor 7 is input to the ring gear R via the motor pinion 72 and the tooth portion 61, and the ring gear R rotates about the rotation axis X.
Then, the annular gear 62 connected to the ring gear R rotates around the rotation axis X in the same direction as the ring gear R, and the pinion gear P meshed with the inner teeth (not shown) of the ring gear R It rotates about the rotation axis Xc.

Here, the sun gear S in which the pinion gear P meshes with external teeth (not shown) is connected to the output shaft 81 of the clamping motor 8, and the rotation of the sun gear S around the rotation axis X is restricted. .
Therefore, when the pinion gear P rotates about the rotation axis Xc by the output rotation transmitted from the ring gear R, the pinion carrier PC supporting the pinion gear P rotates about the rotation axis X in the same direction as the ring gear R. become.
Then, the gear 64 connected to the pinion carrier PC via the rotation transmission shaft 63 and the gear 62 connected to the ring gear R rotate in the same direction around the rotation axis X.

The gear 64 and the gear 62 mesh with the outer members 37 and 47 of the screw feed mechanisms 35 and 45, respectively, so as to be able to transmit rotation. Therefore, rotation (output torque) around the rotation axis X of the gear 64 and the gear 62 is converted into displacement of the outer members 37 and 47 in the rotation axis X1 and X2 directions by the screw feed mechanisms 35 and 45. .

For example, when the pressing portion 371 of the outer member 37 presses the sheave portion 322 of the movable pulley 32 to displace the movable pulley 32 in the direction of narrowing the V-groove 33, the pressing portion 471 of the outer member 47 is movable. Since the movable pulley 42 is allowed to move away from the sheave portion 422 of the pulley 42 in the direction in which the V-groove 43 is widened, the movable pulley 42 widens the V-groove 43 by the pressing force acting from the belt 5. Will be displaced in the direction.
As a result, the wrapping radii of the belt 5 at the primary pulley 3 and the secondary pulley 4 change, and the transmission ratio of the variator 2 is changed.

Incidentally, when the pressing portion 371 of the outer member 37 is separated from the sheave portion 322 of the movable pulley 32 and allows the displacement of the movable pulley 32 in the direction in which the V-groove 33 is widened, the movable pulley 32 is connected to the belt. 5 is displaced in the direction of widening the V-groove 33, while the pressing portion 471 of the outer member 47 presses the sheave portion 422 of the movable pulley 42 to move in the direction of narrowing the V-groove 43. The pulley 42 is displaced.

As described above, in the normal speed change mode, the control device 9 generates the holding torque by the clamping motor 8 and drives (forward or reverse) the speed changing motor 7. As a result, the primary pulley 3, the secondary pulley 4, During this time, a differential thrust is generated, and the variator 2 is shifted.

[Gear ratio fixed mode]
The speed ratio fixing mode is performed to generate a thrust for fixing the speed ratio after the end of the speed change.
As shown in FIGS. 3 and 5, in this speed ratio fixing mode, the control device 9 fixes the speed ratio of the variator 2 based on the torque (holding torque) generated by the clamping motor 8.
In order to stabilize the holding torque, it is preferable that a predetermined torque is also generated in the speed change motor 7. That is, in the fixed gear ratio mode, torque is generated in both the clamping motor 8 and the transmission motor 7 and both the clamping motor 8 and the transmission motor 7 are not rotated (fixed state).
In this case, the output torque (holding torque) of the clamping motor 8 is input to the sun gear S, and the torque is transmitted via the sun gear S.
Then, torque is also transmitted to the pinion gear P meshed with the external teeth (not shown) of the sun gear S.

Here, the ring gear R in which the pinion gear P meshes with the internal teeth (not shown) prevents the rotation of the ring gear R from the speed change motor 7 that can transmit the rotation via the motor pinion 72 and the tooth portion 61. Rotation is regulated by inputting torque in the direction of rotation.
Therefore, the output torque (holding torque) of the clamping motor 8 is transmitted to the gear 64 after being transmitted in the order of the sun gear S, the pinion gear P, and the pinion carrier PC.

The gear 64 meshes with the outer member 47 of the screw feed mechanism 45 so as to be able to transmit rotation. Therefore, the output torque (holding torque) of the clamping motor 8 transmitted to the gear 64 is converted into a displacement force of the outer member 47 in the direction of the rotation axis X2 by the screw feed mechanism 45.

For example, the direction of the torque transmitted to the gear 64 is the arrow CCW direction in FIG. 5, and the direction of the displacement force generated in the outer member 47 on the screw feed mechanism 45 side is the direction indicated by the arrow M1 in the drawing (the movable pulley 42). The pressing force F (see FIG. 5) acting on the belt 5 from the pressing portion 471 via the sheave portion 422 is wound around the belt 5. It acts on the primary pulley 3 (see the solid line thick arrow in the figure).

In the primary pulley 3, the pressing force F acts via the belt 5 in the direction of displacing the movable pulley 32 in the direction of widening the groove width of the V groove 33, so that the sheave portion 322 of the movable pulley 32 is moved to the screw feed mechanism. The outer member 37 (pressing portion 371: see FIG. 2A) is brought into pressure contact.
As a result, the stress in the direction in which the pressing portion 371 is separated from the sheave portion 322 acts on the outer member 37 on the screw feed mechanism 35 side from the movable pulley 32 side.

Here, when the direction of the torque transmitted to the gear 64 is in the direction of the arrow CCW, the ring gear R receives from the transmission motor 7 in the direction of the arrow CW in order to restrict the rotation of the ring gear R. Holding torque is acting.
Therefore, a holding torque in a direction for rotating the gear 62 in the direction of arrow CW (the direction opposite to the rotation direction of the gear 64) acts on the gear 62 connected to the ring gear R.

Then, the holding torque transmitted to the gear 62 is converted into a displacement force in the direction of the rotation axis X1 of the outer member 37 by the screw feeding mechanism 35, and the pressing member 371 is applied to the outer member 37 on the screw feeding mechanism 35 side. The stress F1 (see FIG. 5) in the direction of contacting the sheave portion 322 is applied.

As a result, the pressing force F1 in the direction of narrowing the groove width 33 acts on the sheave portion 322 from the screw feed mechanism 35 side, while the pressing force F in the direction of widening the groove width 33 acts on the belt V side. It will be.

In the embodiment, the pressing force F1 generated by the holding torque generated by the speed change motor 7 is set so as to balance the pressing force F generated by the rotational torque generated by the clamping motor 8.
Therefore, in the gear ratio fixed mode, the groove width 33 of the primary pulley 3 and the groove width 43 of the secondary pulley 4 are maintained without being changed.

Further, in the fixed gear ratio mode, the output torque of the clamping motor 8 is the planetary gear mechanism 6, the screw feed mechanism 45, the secondary pulley 4 (movable pulley 42), the belt 5, the primary pulley 3 (movable pulley 32), the screw feed. Circulation (loop) is performed in the order of the mechanism 35 and the planetary gear mechanism 6.
Then, the output torque from the planetary gear mechanism 6 is amplified and the holding force for holding the belt 5 is increased. Therefore, the movement of the movable pulleys 32 and 42 in the directions of the rotation axes X1 and X2 is reliably restricted, and the variator 2 Is maintained.

[Shift assist mode]
In the shift assist mode, when shifting the variator 2 based on the torque of the shift motor 7, the clamping motor 8 is controlled to increase the differential thrust between the primary pulley 3 and the secondary pulley 5 and increase the shift speed. It is a mode to make it. Specifically, the thrust difference between the primary pulley 3 and the secondary pulley 4 is increased by reducing the holding torque of the clamping motor 8 as compared with the case of the normal shift. An example of a control instruction that requires an increase in shift speed is a kick down instruction.
In this case, the output torque (output rotation) of the speed change motor 7 is input to the ring gear R via the motor pinion 72 and the tooth portion 61, and the ring gear R rotates about the rotation axis X.
Then, the pinion gear P meshed with the inner teeth (not shown) of the ring gear R rotates about the rotation axis Xc.

Here, the sun gear S in which the pinion gear P meshes with external teeth (not shown) is connected to the output shaft 81 of the clamping motor 8, and the sun gear S is a ring gear by torque control of the clamping motor 8. It rotates in the direction opposite to the rotation direction of R.
Therefore, when the pinion gear P rotates around the rotation axis Xc by the output rotation transmitted from the ring gear R, and the pinion carrier PC supporting the pinion gear P rotates around the rotation axis X, the sun gear S rotates in the reverse direction. However, as a result of acting in the direction of assisting (promoting) the rotation of the pinion gear P, the rotation of the pinion carrier PC around the rotation axis X is advanced (assisted).

Then, the gear 64 connected to the pinion carrier PC via the rotation transmission shaft 63 and the gear 62 have a higher rotational speed than when only the output torque of the speed change motor 7 is input to the planetary gear mechanism 6. Thus, it rotates around the rotation axis X.
As a result, the rotational speed transmitted from the gear 64 and the gear 62 to the outer members 37 and 47 of the screw feed mechanisms 35 and 45 is increased, and the displacement speed of the outer members 37 and 47 in the directions of the rotation axes X1 and X2 is increased. Therefore, the groove widths of the V grooves 33 and 43 are changed earlier than when only the output torque of the transmission motor 7 is input to the planetary gear mechanism 6.
Therefore, in the gear shift assist mode, the groove widths of the V grooves 33 and 43 reach the groove width that achieves the target gear ratio in a shorter time than in the normal gear shift mode. It can be done in a short time.

As described above, in the embodiment,
(1) a transmission motor 7 (first motor);
Clamping motor 8 (second motor,
A variator 2 having a primary pulley 3 (first pulley), a secondary pulley 4 (second pulley), and a belt 5 wound around the primary pulley 3 and the secondary pulley 4;
A transmission mechanism (planetary gear mechanism 6, screw feed mechanisms 35, 45) for shifting the variator 2 based on the output torque of the transmission motor 7 and fixing the transmission ratio of the variator 2 based on the output torque of the clamping motor 8. A continuously variable transmission 1 having a configuration including

If comprised in this way, a clamping force can be generated when the gear ratio of the variator 2 is fixed by having the motor 8 for clamping and the transmission mechanism.
Further, it is not necessary to provide a dedicated transmission mechanism for transmitting the output torque for each motor (transmission motor 7 and clamping motor 8).

(2) The maximum rotational speed of the transmission motor 7 is higher than the maximum rotational speed of the clamping motor 8, and the maximum output torque of the clamping motor is higher than the maximum output torque of the transmission motor 7.

With this configuration, the speed-changing motor 7 improves the speed of shifting with high rotation and low torque, while the clamping motor 8 improves the clamping force with low speed and high torque. Since it is not necessary to prepare a large motor with high rotation and high torque and high power consumption, each motor can be reduced in size and power consumption can be reduced.

(3) The control device 9 (control unit) is configured to vary the torque of the clamping motor 8 during the speed change of the variator 2.

With this configuration, by varying the torque of the clamping motor 8, the differential thrust between the movable pulleys 32 and 42 can be improved, and the groove width variation speed of the movable pulleys 32 and 42 can be increased. Therefore, for example, when there is a kick down instruction, the return to the low shift is improved.

(4) The transmission mechanism is
A planetary gear mechanism 6 (torque transmission mechanism) having a ring gear R (first element), a pinion carrier PC (second element), and a sun gear S (third element) in the arrangement order on the alignment chart;
A screw feed mechanism 35 for converting the output torque from the planetary gear mechanism 6 into the thrust of the primary pulley 3,
A screw feed mechanism 45 that converts the output torque from the planetary gear mechanism 6 into the thrust of the secondary pulley 4, and the output torque of the transmission motor 7 is transmitted to the ring gear R;
The output torque of the clamping motor 8 is transmitted to the sun gear S,
The output torque of the pinion carrier PC is transmitted to the screw feed mechanism 45,
The output torque of the ring gear R is transmitted to the screw feed mechanism 35.

If comprised in this way, since adjustment of the output torque transmitted to the screw feed mechanisms 35 and 45 can be performed with one planetary gear mechanism 6, it outputs for every motor (the motor 7 for shifting, the motor 8 for clamping). There is no need to provide a dedicated transmission mechanism for transmitting torque.

(5) The movable pulley 32 (movable pulley 32) externally attached to the shaft portion 311 of the fixed pulley 31 (first fixed pulley) from the direction of the rotation axis X1 (first rotating shaft) is rotated relative to the fixed pulley 31. It is provided to be movable in the direction of the rotation axis X <b> 1 in a restricted state, and the groove width of the V groove 33 between the sheave portion 312 of the fixed pulley 31 and the sheave portion 322 of the movable pulley 32 is the rotation of the movable pulley 32. A primary pulley 3 (first pulley) that changes according to the position in the direction of the axis X1,
Relative rotation of the movable pulley 42 (movable pulley 42) inserted into the shaft portion 411 of the fixed pulley 41 (second fixed pulley) from the direction of the rotation axis X2 (second rotary shaft) with the fixed pulley 41 is restricted. The groove width of the V-groove 43 between the sheave portion 412 of the fixed pulley 41 and the sheave portion 422 of the movable pulley 42 is set in the direction of the rotation axis X2 of the movable pulley 42. Secondary pulley 4 (second pulley) that changes according to the position of
A variator 2 having a V groove 33 of the primary pulley 3 and a belt 5 wound around the V groove 43 of the secondary pulley 4;
By changing the groove width of the V-groove 33 of the primary pulley 3 and the V-groove 43 of the secondary pulley 4 and changing the wrapping radius of the belt 5 between the primary pulley 3 and the secondary pulley 4, the primary pulley 3 and the secondary pulley 4. In the belt-type continuously variable transmission 1 configured to transmit the rotation (torque) between the first and second gears at a desired speed ratio,
A speed change motor 7 (first motor);
A clamping motor 8 (second motor) having a maximum rotation speed smaller than that of the transmission motor 7 and a maximum output torque larger than that of the transmission motor 7;
A planetary gear mechanism 6 that outputs at least one of an output torque of the transmission motor 7 and an output torque of the clamping motor 8;
A screw feed mechanism 35 (first conversion mechanism) capable of converting the output torque of the planetary gear mechanism 6 into a thrust force that presses the movable pulley 32 in the direction of narrowing the groove width of the V-groove 33;
A screw feed mechanism 45 (second conversion mechanism) capable of converting the output torque of the planetary gear mechanism 6 into a thrust force that presses the movable pulley 42 in the direction of narrowing the groove width of the V-groove 43;
A control device 9 (control means) for controlling the drive of the transmission motor 7 and the clamping motor 8;
The control device 9
When the movable pulley 32 and the movable pulley 42 are displaced in the directions of the rotation axes X1 and X2 in order to change the speed ratio, the output torque of the speed change motor 7 is output from the planetary gear mechanism 6,
In order to maintain the speed ratio, the stepless configuration is configured to output the output torque of the clamping motor 8 from the planetary gear mechanism 6 when the positions of the movable pulley 32 and the movable pulley 42 in the directions of the rotation axes X1 and X2 are maintained. A transmission 1 was obtained.

The maximum rotational speed of the transmission motor 7 is larger than the maximum rotational speed of the clamping motor 8, and the maximum output torque of the transmission motor 7 is smaller than the maximum output torque of the clamping motor 8. , A motor that outputs a rotational torque suitable for displacing the movable pulley 32 and the movable pulley 42 in the direction of narrowing the groove width of the V grooves 33 and 43. The clamping motor 8 includes the movable pulley 32 and the movable pulley 42. In order to hold the groove widths of the V grooves 33 and 43 at a predetermined width, the motor outputs a rotational torque suitable for holding the positions of the movable pulley 32 and the movable pulley 42 in the rotation axis direction.
Therefore, when the movable pulley 32 and the movable pulley 42 are displaced in the direction of narrowing the groove widths of the V- grooves 33 and 43 with the configuration as described above, the output torque of the speed change motor 7 is output from the planetary gear mechanism 6. When the positions of the movable pulley 32 and the movable pulley 42 are maintained, the output torque of the clamping motor 8 is output from the planetary gear mechanism 6 so that the rotational torque suitable for the purpose can be output.

In the case of performing displacement and holding of the positions of the movable pulley 32 and the movable pulley 42 with one motor, it is necessary to prepare a large high-performance motor with a large maximum rotational speed and a large maximum output torque. It is difficult to install a large motor in a limited space in the transmission case of the continuously variable transmission. If a large motor is used, the transmission case becomes large.
On the other hand, a dedicated motor specialized for maximum rotation speed and maximum output torque is smaller than a high-performance motor, so even if two dedicated motors are required, the speed of the continuously variable transmission Installation in a limited space in the machine case is easier than in the case of a large motor.
Therefore, the displacement and holding of the positions of the movable pulley 32 and the movable pulley 42 can be performed without increasing the size of the transmission case.

In addition, the work of the high-rotation and high-torque motor is shared by the high-rotation and low-torque transmission motor 7 and the low-rotation and high-torque clamping motor 8, so that the work of the high-rotation and high-torque motor can be A small size motor can be used.
As a result, the mountability to the continuously variable transmission is improved and the energy consumption of the motor can be reduced, so that the fuel efficiency of a vehicle equipped with the continuously variable transmission is expected.

Furthermore, since the output torque of the clamping motor 8 is output from the planetary gear mechanism 6 in order to generate a thrust when the shift is completed, it is possible to suitably prevent the thrust for gripping the belt 5 from being an excessive thrust. As a result, the friction of the belt 5 is reduced, so that an improvement in fuel consumption of a vehicle equipped with a continuously variable transmission is expected.

(6) The planetary gear mechanism 6 is a single pinion type planetary gear having a ring gear R (first element), a pinion carrier PC (second element), and a sun gear S (third element) in the arrangement order on the collinear diagram. A gear mechanism,
In the planetary gear mechanism 6,
A ring gear R that can transmit rotation to and from the output shaft 71 of the speed change motor 7 and a sun gear S that can transmit rotation to and from the output shaft 81 of the clamping motor 8 are relative to each other on the common rotation axis X. A pinion carrier PC that is rotatably provided and supports a pinion gear P that meshes with the inner teeth of the ring gear R and the outer teeth of the sun gear S so as to be able to rotate about a rotation axis Xc parallel to the rotation axis X. It is provided so as to be rotatable around the rotation axis X,
The screw feed mechanism 35 can convert the output torque of the ring gear R into a thrust that presses the movable pulley 32 in the direction of narrowing the groove width of the V groove 33.
The screw feed mechanism 45 is configured to be able to convert the output torque of the pinion carrier PC into a thrust force that presses the movable pulley 42 in the direction of narrowing the groove width of the V groove 43.

With this configuration, the output torque output from the planetary gear mechanism 6 can be appropriately adjusted from the output torque of the speed change motor 7 and the output torque of the clamping motor 8, and the output torque to the screw feed mechanisms 35 and 45 can be adjusted. Transmission can be performed using one planetary gear mechanism 6.
Therefore, it is not necessary to prepare a dedicated mechanism for transmitting the output torque to the screw feed mechanisms 35 and 45 in each of the transmission motor 7 and the clamping motor 8.
Also, by setting the number of teeth for each gear (sun gear S, pinion gear P, ring gear R), the magnitude of the thrust converted from the output torque can be adjusted to the desired magnitude, so the type of continuously variable transmission It becomes easy to optimize the thrust every time.

(7) The control device 9
When the movable pulley 32 and the movable pulley 42 are displaced in the directions of the rotation axes X1 and X2 in order to change the gear ratio,
A structure in which the ring gear R is rotated by the output torque of the transmission motor 7 and the rotation of the sun gear S is regulated by the holding torque of the clamping motor 8 so that the output torque of the transmission motor 7 is output from the planetary gear mechanism 6. did.

In the variator 2, the thrust acting on the movable pulley 32 and the acting on the movable pulley 42 when the groove widths of the V grooves 33 and 43 in the primary pulley 3 and the secondary pulley 4 become groove widths that realize a desired gear ratio. The thrust to do is balanced.
Therefore, if the output torque of the speed change motor 7 is changed, the balance between the thrust acting on the movable pulley 32 and the thrust acting on the movable pulley 42 is lost, and the groove widths of the V grooves 33 and 43 balance the thrust. Since the groove width is quickly changed to a new groove width, a desired gear ratio can be realized only by changing the output torque of the speed change motor 7.
In addition, the output torque output from the planetary gear mechanism 6 by simply driving / stopping the speed change motor 7 and the clamping motor 8 is used to maintain the output torque suitable for the purpose (the output torque suitable for the speed change and the transmission ratio). Suitable output torque).
Therefore, the variator 2 is suitable for a continuously variable transmission that frequently changes and maintains the gear ratio.

(8) The control device 9
When the movable pulley 32 and the movable pulley 42 are displaced in the directions of the rotation axes X1 and X2 in order to change the gear ratio,
The ring gear R is rotated by the output torque of the transmission motor 7 and the sun gear S is rotated by the output torque of the clamping motor 8 in the direction opposite to the rotation direction of the ring gear R around the rotation axis X, thereby causing a planetary gear mechanism. 6 is configured to amplify the output torque of the speed change motor 7 to be output from 6.

With this configuration, when the pinion gear P rotates about the rotation axis Xc by the output rotation transmitted from the ring gear R, and the pinion carrier PC supporting the pinion gear P rotates about the rotation axis X, the sun gear S The reverse rotation acts in the direction of assisting (promoting) the rotation of the pinion gear P.
As a result, the output torque of the clamping motor 8 acts in the direction of advancing (assisting) the rotation of the pinion carrier PC around the rotation axis X, so that the gear connected to the pinion carrier PC via the rotation transmission shaft 63. 64 and the gear 62 rotate around the rotation axis X at a faster rotational speed than when the pinion carrier PC is rotated only by the speed change motor 7.

As a result, the rotational speed transmitted from the gears 64 and 62 to the outer members 37 and 47 of the screw feed mechanisms 35 and 45 becomes faster, and the displacement speed of the outer members 37 and 47 in the directions of the rotation axes X1 and X2 increases. Therefore, the groove widths of the V grooves 33 and 43 can be changed faster than when only the speed change motor 7 is rotationally driven.
Therefore, in the gear shift assist mode, the groove widths of the V grooves 33 and 43 reach the groove width that achieves the target gear ratio in a shorter time than in the normal gear shift mode. It can be done in a short time.

Moreover, the displacement of the movable pulleys 32 and 42 is promoted by the output torque of the clamping motor 8 during sudden gear shifting, and a phase difference between the pulleys (primary pulley 3 and secondary pulley 4) is created, so that the gear ratio can be quickly increased. Since it can be changed, the gear ratio can be quickly returned to the low side.

(8) The control device 9
When the positions of the movable pulley 32 and the movable pulley 42 are held, the transmission motor 7 and the clamping motor 8 are set in a state where output torque (holding torque) is generated, respectively, and the holding torque of the transmission motor 7 is used. The rotation of the ring gear R is restricted and the holding torque of the clamping motor 8 is input to the sun gear S, and is transmitted to the screw feed mechanism 45 via the sun gear S, the pinion gear P, the pinion carrier PC, and the gear 64. Displacement force that restricts the movement of the operating pulley 32 in the direction of the rotation axis X2 while the holding torque of the clamping motor 8 acts in the direction of pressing the movable pulley 32 of the secondary pulley 3 against the belt 5 by the screw feed mechanism 45. Changed to (thrust).

If comprised in this way, it is suitable for holding | maintaining the output torque suitable for the objective (output torque suitable for a gear shift, and a transmission gear ratio) from the planetary gear mechanism 6 only by driving / stopping the gear shifting motor 7 and the clamping motor 8. Output torque) can be adjusted and output.
Therefore, the variator 2 is suitable for a continuously variable transmission that frequently changes and maintains the gear ratio.

(9) The screw feed mechanism 35 (first conversion mechanism)
An outer member 37 (first outer member) that rotates around the rotation axis X1 of the primary pulley 3 with the output torque of the planetary gear mechanism 6;
An inner member 36 (first inner member) disposed inside the outer member 37 in a state where movement in the direction of the rotation axis X1 is restricted;
The outer member 37 and the inner member 36 are disposed so as to straddle the spiral groove 361 a provided on the outer periphery of the inner member 36 and the spiral groove 371 a provided on the inner periphery of the outer member 37. And a plurality of balls Ba for supporting relative rotation so that
The outer member 37 that rotates around the rotation axis X1 is a ball screw feed mechanism that is displaced in the direction of the rotation axis X1.

If comprised in this way, the output torque (rotation torque) input from the planetary gear mechanism 6 side will be converted into the thrust which displaces the outer side member 37 to the rotating shaft X1 direction, and the movable pulley 32 pushed by the outer side member 37 will be demonstrated. Can be smoothly displaced in the direction of narrowing the groove width of the V-groove 33.

(10) The screw feed mechanism 45 (second conversion mechanism)
An outer member 47 (second outer member) that rotates around the rotation axis X2 by the output torque of the planetary gear mechanism 6;
An inner member 36 (second inner member) disposed inside the outer member 47 in a state where movement in the rotation axis X2 direction is restricted;
The outer member 47 and the inner member 46 are arranged so as to straddle the spiral groove 461a provided on the outer periphery of the inner member 46 and the spiral groove 471a provided on the inner periphery of the outer member 47. A plurality of balls Ba that are rotatably supported, and
The outer member 47 rotating around the rotation axis X2 is configured to be a ball screw feed mechanism that displaces in the direction of the rotation axis X2.

With this configuration, the output torque (rotational torque) input from the planetary gear mechanism 6 side is converted into a thrust that displaces the outer member 47 in the direction of the rotation axis X <b> 2, and the movable pulley 42 pushed by the outer member 47. Can be smoothly displaced in the direction of narrowing the groove width of the V-groove 43.

(11) In the screw feed mechanism 35, when the output torque of the planetary gear mechanism 6 is converted into a thrust force that pushes the movable pulley 32 in the direction of narrowing the groove width of the V-groove 33, the sheave portion 322 of the movable pulley 32 is applied. A contact portion 371b that contacts from the rotation axis X1 direction and presses the sheave portion 322 is provided on the outer member 37,
In the screw feed mechanism 45, when the output torque of the planetary gear mechanism 6 is converted into a thrust force that presses the movable pulley 42 in the direction of narrowing the groove width of the V-groove 43, the rotational axis X1 is applied to the sheave portion 422 of the movable pulley 42. A pressing portion 471b that contacts from the direction and presses the sheave portion 422 is provided on the outer member 37,
When the screw feeding mechanism 35 displaces the outer member 37 in a direction in which the abutting portion 371b abuts on the sheave portion 322, the screw feeding mechanism 45 in a direction in which the pressing portion 471b is separated from the sheave portion 422. The outer member 47 is displaced;
When the screw feeding mechanism 35 displaces the outer member 37 in a direction in which the abutting portion 371b is separated from the sheave portion 322, the screw feeding mechanism 45 is in a direction in which the pressing portion 471b abuts on the sheave portion 422. The outer member 47 is configured to be displaced.

With this configuration, the output torque (rotational output) of the motor (transmission motor 7 and clamping motor 8) is, for example, the pinion carrier PC, the rotation transmission shaft 63, the gear 64, the screw feed mechanism 45, the secondary pulley 4 ( Movable pulley 42), belt 5, primary pulley 3 (movable pulley 32), screw feed mechanism 35, gear 62, ring gear R, pinion gear P, pinion carrier PC, rotation transmission shaft 63, and planetary gear mechanism 6 Circulates with the variator 2.
Then, the output torque (rotational speed) transmitted from the gear 64 to the screw feed mechanism 45 is increased and circulated (looped) between the planetary gear mechanism 6 and the variator 2, so that the belt 5 is held. As a result, the output torque (rotational speed) increases as the speed increases, and as a result, the movement of the movable pulleys 32 and 42 in the direction of the rotation axes X1 and X2 is reliably restricted, and the transmission ratio in the variator 2 is maintained. Will be.

In the above-described embodiment, the output torque of the transmission motor 7 is transmitted to the ring gear R (first element), and the output torque of the clamping motor 8 is transmitted to the sun gear S (third element). The constructed planetary gear mechanism 6 is exemplified.
The present invention is not limited to this mode, and the output torque of the clamping motor 8 is transmitted to the ring gear R (first element), and the output torque of the transmission motor 7 is the sun gear S (third element). ) May be a planetary gear mechanism configured to be transmitted.

Furthermore, in the above-described embodiment, the planetary gear mechanism for outputting one of the output torque of the transmission motor 7 and the output torque of the clamping motor 8 to the screw feed mechanisms 35 and 45 is a single pinion type. The case where it was a planetary gear mechanism was illustrated.
The present invention is not limited to this aspect, and the planetary gear mechanism is coaxial with the sun gear, the inner pinion gear that meshes with the sun gear, the outer pinion gear that meshes with the inner pinion gear, and the sun gear that meshes with the outer pinion gear. You may employ | adopt the double pinion type planetary gear mechanism comprised from the arrange | positioned ring gear and the pinion carrier which pivotally supports an inner side pinion gear and an outer side pinion gear.

Alternatively, a Ravigneaux planetary gear mechanism, which is a composite planetary gear in which a single pinion planetary gear and a double pinion planetary gear are integrated, may be employed.
Furthermore, a combination of a plurality of simple gears may be used as long as a collinear diagram similar to the planetary gear set can be drawn by a combination of a plurality of simple gears. Further, it may be a combination of a plurality of planetary gears.

The present invention is not limited to the above-described embodiment, and includes various changes and improvements that can be made within the scope of the technical idea.

Claims (6)

1. A first motor;
   A second motor;
   A variator having a first pulley, a second pulley, and a belt wound around the first pulley and the second pulley;
   With
   A continuously variable transmission that shifts the variator based on the torque of the first motor and fixes the speed ratio of the variator based on the torque of the second motor.
2. The maximum rotation speed of the first motor is higher than the maximum rotation speed of the second motor,
   The continuously variable transmission according to claim 1, wherein a maximum output torque of the second motor is higher than a maximum output torque of the first motor.
3. The continuously variable transmission according to claim 1 or 2, further comprising a control unit configured to vary a torque of the second motor so as to increase a speed of the variator during a shift of the variator by the first motor.
4. Connected to both the first motor and the second motor;
   The transmission according to any one of claims 1 to 3, further comprising: a transmission mechanism that shifts the variator based on the torque of the first motor and fixes the speed ratio of the variator based on the torque of the second motor. Step transmission
5. The transmission mechanism is
   A torque transmission mechanism having a first element, a second element, and a third element in the order of arrangement on the alignment chart;
   A first conversion mechanism that converts torque into thrust of the first pulley;
   A second conversion mechanism that converts torque into thrust of the second pulley;
   The torque of the first motor is transmitted to the first element,
   The torque of the second motor is transmitted to the third element;
   The torque of the second element is transmitted to the first conversion mechanism,
   The continuously variable transmission according to claim 4, wherein the torque of the first element is transmitted to the second conversion mechanism.
6. 6. The torque transmission mechanism comprises a single pinion type planetary gear mechanism having a ring gear as the first element, a pinion carrier as the second element, and a sun gear as the third element. The continuously variable transmission described in 1.

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