WO2018066488A1 - Continuously variable transmission - Google Patents

Abstract

In order to reduce the friction of pulley rotation in a continuously variable transmission in which a mechanical actuator is used to move a moveable sheave in the axial direction, this continuously variable transmission is equipped with a primary and a secondary pulley, a belt, and a mechanical pulley movement mechanism (30) for adjusting the transmission ratio. The mechanical pulley movement mechanism (30) is equipped with: a torque cam mechanism (40) that has a first and a second cam (42, 44), in which the first cam is directly connected to a moveable sheave (12), and the overall length of which changes when the rotational phase of the second cam with respect to the first cam is changed, thereby moving the moveable sheave in the axial direction; an actuator (70) for changing or fixing the rotational phase; and a first planetary gear mechanism (50) in which one of three rotary elements is coupled to the first cam (42) via a power transmission mechanism (60), one of the remaining rotary elements is coupled to the second cam (44), and the final rotary element is coupled to the actuator. The transmission ratio of the power transmission mechanism is set such that when the transmission ratio is fixed the first and second cams rotate in the same direction at the same speed.

Description

Continuously variable transmission

The present invention relates to a continuously variable transmission in which a movable sheave is moved in an axial direction by a mechanical actuator using a torque cam mechanism.

In a belt-type continuously variable transmission, a technique has been developed in which a movable sheave of a primary pulley or a secondary pulley is axially moved by an actuator to change the groove width of the pulley.
For example, Patent Document 1 discloses a slide cam that slides in the axial direction by a cam mechanism when the rotational phase is changed and moves the movable sheave in the axial direction, and a mechanical actuator such as a motor that changes the rotational phase of the slide cam. A continuously variable transmission is disclosed.

When the movable sheave is moved in the axial direction by the actuator, the drive member that is driven by the actuator and moves the movable sheave in the axial direction like the above slide cam is basically non-rotated except when the rotational phase is changed. On the other hand, since the movable sheave rotates at high speed, a thrust bearing that allows relative rotation and transmits axial force is interposed between the drive member and the movable sheave.

JP 2016-1013 A

However, the thrust bearing between the drive member such as the slide cam and the movable sheave rotates according to the differential rotation between the two while constantly receiving the axial load due to the belt tension. For this reason, the thrust bearing causes friction of pulley rotation, and causes an increase in power transmission loss of the continuously variable transmission. In particular, when the transmission torque by the continuously variable transmission is large, the axial load due to belt tension also increases, and the friction of pulley rotation by the thrust bearing also increases, so the increase in power transmission loss becomes more significant.

The present invention was devised in view of such problems, and in a continuously variable transmission that moves a movable sheave in an axial direction by using a mechanical actuator, it is possible to reduce friction of pulley rotation and reduce power transmission loss. It is an object of the present invention to provide a continuously variable transmission capable of suppressing the occurrence of the above.

(1) In order to achieve the above object, a continuously variable transmission according to the present invention includes a primary pulley and a secondary pulley, a belt spanned between the pulleys, and a movable sheave of at least one of the pulleys. A mechanical pulley moving mechanism that adjusts the gear ratio by moving the shaft in the axial direction;
The mechanical pulley moving mechanism includes first and second cam members that are slidably in contact with each other and arranged in series on the same axis, and the first cam A torque cam mechanism that is directly connected to the movable sheave, and whose total length is changed when the relative rotational phase of the second cam member with respect to the first cam member is changed, and the movable sheave moves in the axial direction; An actuator for changing or maintaining the relative rotational phase of the second cam member, and three rotational elements of a sun gear, a carrier, and a ring gear, and any one of these rotational elements provides power to the first cam member. A first planetary gear mechanism coupled via a transmission mechanism, wherein any one of the remaining rotating elements is coupled to the second cam member, and the remaining rotating elements are coupled to the actuator. The above The force transmission mechanism is configured so that the first and second cam members rotate at a constant speed in the same direction when the gear ratio is fixed by the actuator so that the relative rotation phase of the first and second cam members is constant. A transmission ratio is set.

(2) It is preferable that the power transmission mechanism has a second planetary gear mechanism that is arranged in series on the same axis as the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear.

(3) In the second planetary gear mechanism, the sun gear is coupled to the first cam member and the ring gear is fixed, and in the first planetary gear mechanism, the sun gear is coupled to the second cam member. Preferably, the carrier is connected to the carrier of the second planetary gear mechanism, and the ring gear is connected to the actuator.

(4) In the second planetary gear mechanism, the ring gear is connected to the first cam member, the carrier is fixed, and in the first planetary gear mechanism, the sun gear is the sun gear of the second planetary gear mechanism. It is preferable that the ring gear is connected to the second cam member, and the carrier is connected to the actuator.

(5) In the second planetary gear mechanism, the sun gear is coupled to the first cam member and the carrier is fixed, and in the first planetary gear mechanism, the sun gear is coupled to the second cam member. Preferably, the carrier is connected to the actuator, and the ring gear is connected to the ring gear of the second planetary gear mechanism.

(6) The sun gear, carrier, and ring gear of the second planetary gear mechanism are set to have the same number of teeth as the sun gear, carrier, and ring gear of the first planetary gear mechanism, respectively, and the rotational speed of the integral rotating element and the first cam It is preferable that the speed transmission ratio of the power transmission mechanism, which is defined as a ratio with the rotational speed, is set to a value equal to the ratio between the rotational speed of the integral rotating element and the rotational speed of the second cam. .

(7) The sun gear, the carrier, and the ring gear of the second planetary gear mechanism are set to have different numbers of teeth from the sun gear, the carrier, and the ring gear of the first planetary gear mechanism, and the rotational speed of the integral rotating element and the first cam It is preferable that the speed transmission ratio of the power transmission mechanism defined as a ratio with the rotational speed of the motor is set to a value different from the ratio between the rotational speed of the integral rotating element and the rotational speed of the second cam. .
(8) In the first planetary gear mechanism, the sun gear is coupled to the second cam member, the ring gear is coupled to the actuator, the carrier is drivingly coupled to the power transmission mechanism, and the power transmission mechanism is A counter shaft installed in parallel with the rotational axis of the movable sheave; a first counter gear and a second counter gear coupled to the counter shaft; and coupled to the first cam member and meshed with the first counter gear. Preferably, the first external gear is configured by a parallel gear mechanism including a first external gear and a second external gear coupled to the carrier and meshing with the second counter gear.
(9) The first planetary gear mechanism is disposed on a rotation axis parallel to the rotation axis of the movable sheave. In the first planetary gear mechanism, the sun gear is connected to the actuator, and the ring gear is the second gear. And the carrier is drivingly connected to the power transmission mechanism, and the power transmission mechanism is connected to the first cam member, and the external gear is connected to the carrier. It is preferable to be constituted by a parallel gear mechanism including a counter gear that meshes.
(10) The first planetary gear mechanism is disposed on a rotation axis parallel to the rotation axis of the movable sheave. In the first planetary gear mechanism, the sun gear is connected to the actuator, and the ring gear is the second gear. And the carrier is drivingly connected to the power transmission mechanism. The power transmission mechanism is coaxially arranged in series with the first planetary gear mechanism, and includes three rotating elements, a sun gear, a carrier, and a ring gear. A second planetary gear mechanism having the first planetary gear mechanism, a first external gear integrally provided on an outer periphery of a ring gear of the second planetary gear mechanism, and a first cam member coupled to the first external gear. It is preferable that it comprises an external gear.

(11) It is preferable that a slide allowing mechanism for allowing the axial movement of the first cam member and transmitting the rotation is interposed between the power transmission mechanism and the first cam.

According to the present invention, when the relative rotational phase of the first and second cam members is made constant by the actuator, the total length of the torque cam mechanism is held at a constant value corresponding to the relative rotational phase of the first and second cam members. Power is transmitted between the primary pulley and the secondary pulley at a fixed gear ratio corresponding thereto. The first cam member is directly connected to the movable sheave, no friction is generated between the first cam member and the pulley, and the first and second cam members rotate at the same speed in the same direction. Since there is no relative rotation, friction due to rotation does not occur. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When the relative rotation phase of the second cam member with respect to the first cam member is changed by the actuator, the total length of the torque cam mechanism is changed, and power is transmitted between the primary pulley and the secondary pulley at a gear ratio corresponding thereto. . At the time of changing the relative rotation phase, the first cam member and the second cam member rotate relative to each other. However, since the speed change is short and the speed of the relative rotation is low, friction due to the relative rotation occurs. It is suppressed to a few things.

It is a typical lineblock diagram of a continuously variable transmission concerning each embodiment of the present invention. It is a typical lineblock diagram of the pulley concerning each embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 1st, 2nd embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the first embodiment of the present invention. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the second embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 3rd Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the third embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 4th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the fourth embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 5th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the fifth embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 6th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the sixth embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 7th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the seventh embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 8th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the eighth embodiment of the present invention. It is a typical block diagram which shows the mechanical pulley moving mechanism which concerns on 9th Embodiment of this invention with a pulley. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the ninth embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the embodiment described below is merely an example, and there is no intention to exclude various modifications and technical applications that are not explicitly described in the following embodiment. Each configuration of the following embodiments can be implemented with various modifications without departing from the spirit thereof, and can be selected or combined as appropriate.

[Continuously variable transmission according to each embodiment]
FIG. 1 is a configuration diagram schematically showing a continuously variable transmission according to each embodiment. As shown in FIG. 1, a drive source 2 composed of an internal combustion engine, an electric motor or the like for running a vehicle is connected to a continuously variable transmission 5 via a forward / reverse switching mechanism 4 composed of a planetary gear mechanism or the like. A rotary shaft 10 coupled to the fixed sheave 8 of the primary pulley 6 is connected. A movable sheave 12 having a sheave surface that forms a V-shaped groove of a pulley facing the sheave surface of the fixed sheave 8 is disposed on the rotary shaft 10 so as to be slidable in the axial direction and not relatively rotatable. Yes.

A drive wheel (not shown) is connected to the drive shaft 18 coupled to the fixed sheave 16 of the secondary pulley 14 of the continuously variable transmission 5 via a differential mechanism or the like, and the drive shaft 18 is connected to the fixed sheave 16. A movable sheave 20 having a sheave surface that forms a V-shaped groove of a pulley opposite to the sheave surface of the pulley is disposed so as to be slidable in the axial direction and not relatively rotatable.

Further, between the sheaves 16 and 20 of the secondary pulley 14, a spring 22 and a cam mechanism 24 that apply a biasing force in the direction of narrowing the V-shaped groove are interposed.
A belt 26 is wound around the pulleys 6 and 14.
Further, the spring 22 and the cam mechanism 24 function as a thrust adjustment mechanism that adjusts the thrust of the secondary pulley 14 to adjust the clamping force of the belt 26.

FIG. 1 shows a state where the gear ratio of the primary pulley 6, the secondary pulley 14 and the belt 26 is low and high. A low-side state is shown in each outer half of the primary pulley 6 and the secondary pulley 14, and a high-side state is shown in each inner half. Regarding the belt 26, the low-side state is indicated by a solid line, and the high-side state is indicated by a broken line. However, the high state indicated by the broken line only indicates the positional relationship between the pulley and the belt in the radial direction, and the actual belt position does not appear in the inner half of the pulley.

A mechanical pulley moving mechanism 30 that moves the movable sheave 12 in the axial direction and adjusts the gear ratio is disposed on the back side (surface opposite to the sheave surface) 13 of the movable sheave 12 of the primary pulley 6. . In FIG. 1, the mechanical pulley moving mechanism 30 is described in a very simplified manner. However, the mechanical pulley moving mechanism 30 includes a torque cam mechanism 40, a first planetary gear mechanism 50, and a power transmission mechanism (for example, a second transmission mechanism). A planetary gear mechanism or other gear mechanism) 60 and an electric motor 70 as an actuator.

[Mechanical pulley moving mechanism according to each embodiment]
As shown in FIG. 2, the torque cam mechanism 40 is directly coupled to the movable sheave 12 (fixedly connected so that relative rotation is impossible and axial relative movement is impossible), and rotates with the movable sheave 12 as a first cam (first (Cam member) 42 and a second cam surface 44a opposite to the first cam surface 42a formed on the first cam 42 are formed at one end (left side in the figure), and the other end (right side in the figure) is a thrust bearing. And a second cam (second cam member) 44 whose axial position is regulated by the rotary shaft 10 via 46.

The first cam 42 and the second cam 44 are arranged on the outer peripheral side of the rotary shaft 10 so as to be coaxial (same axis) as the axis of the rotary shaft 10. The rotary shaft 10 is rotatably supported by a transmission casing (not shown) via bearings 32 and 34. The first cam 42 that rotates integrally with the movable sheave 12 is supported so as to be non-rotatable relative to the rotary shaft 10 and movable in the axial direction by the same configuration as the movable sheave 12 (spline mechanism with a ball or a roller interposed). Has been. The second cam 44 is supported so as to be relatively rotatable with respect to the rotary shaft 10 via a bearing (not shown) and the like, and the axial direction of the second cam 44 is not movable so as to keep a fixed position relative to the rotary shaft 10 and not move. It has become.

In this way, the first cam 42 is directly connected (fixedly connected) to the movable sheave 12 and the second cam 44 is supported so as not to move in the axial direction with respect to the rotary shaft 10, thereby allowing the relative relationship between the two cams 42, 44. It is possible to move the movable sheave 12 in the axial direction (change the gear ratio) by the displacement of the rotational phase.

The first cam surface 42a and the second cam surface 44a are formed on the end surfaces of the cylindrical cams 42, 44 facing each other, and are arranged so as to be in sliding contact with each other. The shapes of these cam surfaces 42 a and 44 a are formed in a spiral slope inclined with respect to the axis SC of the rotary shaft 10. In each embodiment, the inclined surfaces (that is, the first and second cam surfaces 42a and 44a) are inclined so as to approach the back surface 13 of the movable sheave 12 along the rotational direction of the primary pulley 6 when the vehicle is traveling forward. ing.

When the relative rotation phase between the second cam 44 and the first cam 42 is changed, the total length of the torque cam mechanism 40 is changed. Since the second cam 44 does not move in the axial direction, the first cam 42 moves in the axial direction together with the movable sheave 12. Therefore, when the relative rotation phase is changed by rotating the second cam 44 relative to the first cam 42, the movable sheave 12 moves in the axial direction, and the transmission ratio of the continuously variable transmission 5 is adjusted.

In addition, between the 1st cam 42 and the power transmission mechanism 60, the slide permissive mechanism (a ball | bowl or roller) for allowing the relative movement along the axial direction of both and making a relative rotation impossibility (rotational power can be transmitted). Etc.) is interposed. In the slide allowance mechanism 80, when the gears such as the planetary gear mechanism 50 and the power transmission mechanism 60 are constituted by helical gears, the relative movement in the axial direction between the gears becomes impossible. This is necessary to allow relative movement between the power transmission mechanism 60 and the first cam 42. However, if one or both of the planetary gear mechanism 50 and the power transmission mechanism 60 are made of spur gears, relative movement between the spur gears becomes possible, so that the slide allowing mechanism 80 can be omitted. .

The first planetary gear mechanism 50 is arranged on the outer periphery of the second cam 44, and any one of the three rotation elements of the sun gear S ₁ , the carrier C ₁ , and the ring gear R ₁ (first rotation element) is provided. It is connected to the first cam 42 via a power transmission mechanism (for example, a planetary gear mechanism or other gear mechanism) 60, and any one of the remaining rotating elements (second rotating elements) is connected to the second cam 44. The remaining rotating elements (third rotating elements) are connected to an electric motor 70 as an actuator.

In the following first to fourth, eighth, and ninth embodiments, the second planetary gear mechanism 60 is exemplified as the power transmission mechanism. However, the power transmission mechanism is not limited to the planetary gear mechanism. As illustrated in the fifth to seventh embodiments, a parallel gear mechanism or the like may be used. An electric motor is suitable as the actuator, but the actuator is not limited to the electric motor as long as the controllability necessary for the actuator can be ensured.

If the rotation of any one of the three rotating elements (sun gear S ₁ , carrier C ₁ , ring gear R ₁ ) is restricted, the first planetary gear mechanism 50 rotates one of the remaining two rotating elements. The element becomes a reaction force element, and the other rotation element rotates at a gear ratio (= output rotation speed / input rotation speed, also referred to as speed ratio) corresponding to the gear ratio. The rotation restriction in this case is to set the rotation speed to a predetermined speed (including a constant speed and a rotation stop). The rotation is restricted by the electric motor 70. That is, by controlling and restraining the rotation of the third rotating element by the motor 70, the first rotating element and the second rotating element rotate at a gear ratio according to the gear ratio.

Since the first rotating element of the first planetary gear mechanism 50 is coupled to the first cam 42 via the power transmission mechanism 60, the rotational speed (N _{cam 1} ) of the first cam 42 is the first planetary gear mechanism. With respect to the rotation speed (N ₁ ) of 50 first rotation elements, the first rotation element rotates at a rotation speed corresponding to the speed transmission ratio (N _{cam 1} / N ₁ ) of the power transmission mechanism 60. The power transmission mechanism 60 is connected to the first cam 42 and the first cam 42 when the actuator 70 is at a predetermined rotation restraint of the third rotation element, that is, when the third rotation element is rotated or stopped at a predetermined speed (a constant speed). The speed transmission ratio is set so that the two cams 44 rotate at a constant speed.
Assuming that the rotational speed Nin of the input element, the number of teeth Zin, the rotational speed Nout of the output element, and the number of teeth Zout, the speed transmission ratio is defined by the reciprocal of the gear ratio (speed ratio) as shown in the following equation. .
Speed transmission ratio = Nout / Nin = Zin / Zout = 1 / Gear ratio (speed ratio)

When the rotation constraint state of the third rotation element by the actuator 70 is changed, that is, the rotation speed of the third rotation element is changed (if the third rotation element is in the stopped state, it is rotated, or the third rotation element is at a predetermined rotation speed). In this case, since the first cam 42 is directly connected to the movable pulley 12, the rotation speed does not change. Therefore, the first cam 42 is changed between the first cam 42 and the second cam 44. The second cam 44 rotates relative to the first cam 42 and the relative rotation phase between the first cam 42 and the second cam 44 is changed. Thereby, the movable sheave 12 moves in the axial direction, and the gear ratio of the continuously variable transmission 5 is adjusted.

Hereinafter, specific configurations of the first planetary gear mechanism 50 of the mechanical pulley moving mechanism 30 and the second planetary gear mechanism 60 as a power transmission mechanism will be described according to the first to fourth, eighth, and ninth embodiments. .
The first to fourth, eighth, the ninth embodiment, the first planetary gear mechanism 50A-50D, 50H, for 50I, the sun gear in _{S 1,} the carrier _{C 1,} the planetary gear in _{P 1,} the ring gear the respectively in _{R 1,} the second planetary gear mechanism 60A ~ 60D, 60H, for 60I, the sun gear in _{S 2,} the carrier _{C 2,} the planetary gears at _{P 2,} show respectively the ring gear in _{R 2,} of Each rotating element does not necessarily have the same standard among the embodiments, but has a standard (for example, the number of gear teeth and the tooth width) required in the configuration of each embodiment.
In the drawings showing the configuration of each embodiment (FIGS. 3, 6, 8, 10, 12, 14, 16, 18), the second planetary gear mechanism 60 and the first cam 42 are interposed. The slide allowance mechanism 80 is omitted (not shown).

[First Embodiment]
As shown in FIG. 3, first the mechanical pulley moving mechanism 30A according to the first embodiment, the first planetary gear mechanism 50A, the carrier C ₁ is equivalent to the first rotary element, a power transmission mechanism It is connected to the first cam 42 via a two planetary gear mechanism 60A. The sun gear S ₁ corresponds to the second rotating element and is connected to the second cam 44. The ring gear R ₁ is equivalent to the third rotating element, the electric motor 70 is an actuator, and a gear 71b fixed to the rotary shaft of the external gear 71a and the electric motor 70, which is formed on the outer periphery of the ring gear R1 meshing The first planetary gear mechanism 50A is connected through a gear mechanism 71.

The second planetary gear mechanism 60A, the carrier _{C 2} is directly connected to the carrier _{C 1} of the first planetary gear mechanism 50A, a sun gear _{S 2} is connected to the first cam 42, fixed to the transmission casing ring gear _{R 2} is not shown Has been. Accordingly, the carrier C ₁ of the first planetary gear mechanism 50A and the carrier C ₂ of the second planetary gear mechanism 60A has an integral rotating element that rotates integrally with one another.

In the present embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50A and the second planetary gear mechanism 60A have the same number of teeth. Is set to Thus, for the gear ratio between the tooth number Zr of teeth Zs and the ring gear of the sun gear alpha (= Zs / Zr), the number of teeth of the gear ratio of the first planetary gear mechanism 50A alpha ₁ and the second planetary gear mechanism 60A The ratio α ₂ is the same (α ₁ = α ₂ ).

The transmission ratio of the second planetary gear mechanism 60A which is a power transmission mechanism, and the rotational speed N _C2 of the carrier C ₂ is an integral rotating element rotation speed of the first cam 42 (i.e., the rotational speed of the sun gear S ₂₎ It is defined as the ratio _NS2 . Since the second planetary gear mechanism 60A ring gear R ₁ is fixed state, the nomogram (velocity diagram) is as shown by the solid line L in FIG.
4, FIG. 5, FIG. 7, FIG. 9, FIG. 11, FIG. 15, FIG. 15, FIG. 17, FIG. The upward direction with respect to zero is defined as positive rotation, and the downward direction with respect to zero rotation speed is defined as negative direction.

The ratio of the speed transmission ratio, the rotational speed N _S2 of the sun gear S ₂ which rotates integrally with the second cam 44, and the rotational speed N _C2 of the carrier C ₂ of the second planetary gear mechanism 60A is rotated integrally element Defined as _NS2 / _NC2 . This ratio _NS2 / _NC2 is equal to (1+ [alpha] ₂ ) / [alpha] ₂ .

If the ring gear R ₁ of the first planetary gear mechanism 50A to maintain the rotational speed to zero of the electric motor 70 in a fixed state, the sun gear S ₁ of the first planetary gear mechanism 50A includes a first rotates integrally with the first cam 42 2 rotates the sun gear _{S 2} and a constant velocity of the planetary gear mechanism 60A. Alignment chart of first planetary gear mechanism 50A at this time is as shown by the solid line L in FIG. 4 as in the second planetary gear mechanism 60A, a sun gear S ₁ of the first planetary gear mechanism 50A and the second planetary gear mechanism 60A rotates the sun gear _{S 2} and a constant velocity of.

Therefore, at this time, the second cam 44 to the sun gear S ₁ is connected, without relative rotation and the first cam 42 the sun gear S ₂ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio is kept constant.
In the present embodiment, the carrier C ₁ is an integral rotating element, and the tooth number ratio α ₂ and the tooth number ratio α ₁ are the same (α ₁ = α ₂ ). Therefore, the sun gear S ₂ , the carrier C ₂ , the transmission ratio N _{S2 /} N _C2 is the rotational speed ratio is in the fixed gear ratio state transmission ratio remains constant, the rotational speed N _S1 of the sun gear S ₁ that rotates integrally with the second cam 44, integral rotation It becomes a value equal to the ratio N _S1 / N _C1 [= (1 + α ₁ ) / α ₁ ] with the rotational speed N _C1 of the carrier C ₁ of the first planetary gear mechanism 50A as an element.

On the other hand, when the electric motor 70 is rotated in the same direction (positive direction) as the carriers C ₁ and C ₂ (see the arrow of the speed change a), the alignment chart of the first planetary gear mechanism 50A is a broken line in FIG. is as shown by la, the sun gear _{S 1} of the first planetary gear mechanism 50A is slower than that of the sun gear _{S 2} of the second planetary gear mechanism 60A. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Conversely, when the electric motor 70 is rotated in the opposite direction (negative direction) to the rotation direction of the carriers C ₁ and C ₂ (see the arrow of the speed change b), the collinear diagram of the first planetary gear mechanism 50A is shown in FIG. is as shown by the broken line Lb, the sun gear _{S 1} of the first planetary gear mechanism 50A is faster than the sun gear _{S 2} of the second planetary gear mechanism 60A. That is, the second cam 44 is faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Therefore, when changing the gear ratio (that is, when shifting), the electric motor 70 is rotated in a predetermined direction from the rotational speed zero, and when the gear ratio is fixed, the rotational speed of the electric motor 70 is reduced to zero. maintain.

The mechanical pulley moving mechanism 30A according to the present embodiment is configured as described above, and the first cam 42 is directly connected to the movable sheave 12, so that the first cam 42 and the pulley 6 are rotated. Friction due to will not occur. Further, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that no friction due to rotation occurs between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the electric motor 70 is rotated in a predetermined direction to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 that the second cam 44 receives toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and relative rotation occurs. Moreover, since the speed of the relative rotation is low, friction due to the relative rotation is generated but suppressed to a small amount.

Further, the ring gear _{R 1} of the first planetary gear mechanism 50A is connected to the electric motor 70, also have to fix the ring gear _{R 2} of the second planetary gear mechanism 60A to the transmission casing, the ring gear _R 1, _{R 2} mechanisms Since the electric motor 70 and the transmission casing are easily accessible, the structure can be simplified, which is advantageous in making the axial and radial sizes of the apparatus compact.

Further, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50A and the second planetary gear mechanism 60A are set to have the same number of teeth. Therefore, it is possible to simplify the overall configuration and simplify the control program for the electric motor 70.

Further, since the gears of the planetary gear mechanisms 50A and 60A are arranged on the outer periphery of the rotating shaft 10, the sun gears S ₁ and S ₂ have a relatively large diameter (that is, the number of teeth Zs is relatively large) in view of the layout. In addition, the ring gears R ₁ and R ₂ can be made relatively small in diameter (that is, the number of teeth Zs is relatively small), in other words, the tooth number ratio α (= Zs / Zr) is set to a size close to 1. Therefore, the torque required for the electric motor 70 for changing the gear ratio can be suppressed.

[Second Embodiment]
In the present embodiment, the sun gears S ₁ and S ₂ and the ring gears R ₁ and R ₂ of the first planetary gear mechanism 50A and the second planetary gear mechanism 60A are respectively compared to the configuration of the first embodiment shown in FIG. However, the only difference is that it is set to a different number of teeth. Since the other points are the same as the configuration of the first embodiment, description will be made using the configuration and reference numerals of FIG. That is, the number of teeth Zs ₁ and Zs ₂ of the sun gears S ₁ and S ₂ is set to Zs ₁ <Zs ₂ , and the number of teeth Zr ₁ and Zr ₂ of the ring gears R ₁ and R ₂ are set to Zr ₁ > Zr ₂ , respectively. Yes.

Therefore, the tooth number ratio α (= Zs / Zr) between the number of teeth Zs of the sun gear and the number of teeth Zr of the ring gear is the same as the number ratio α ₁ (= Zs ₁ / Zr ₁ ) of the first planetary gear mechanism 50. With the tooth number ratio α ₂ (= Zs ₂ / Zr ₂ ) of the two planetary gear mechanism 60A, the different size, that is, the tooth number ratio α ₁ is smaller than the tooth number ratio α ₂ (α ₁ <α ₂ ).

Also in this embodiment, the speed transmission ratio by the second planetary gear mechanism 60A that is a power transmission mechanism is such that the rotational speed of the first cam 42 (that is, the rotational speed N _S2 of the sun gear S ₂ ) and the carrier C that is an integral rotational element. _Is defined as a ratio NS ₂ / N _{C2 to} a rotational speed N _{C2 of 2} . Since the second planetary gear mechanism 60A ring gear R ₁ is fixed state, the nomogram is as shown by the solid line L in FIG. The ratio _N S2 _{/ N C2} of the rotation speed and the rotation speed of the sun gear _{S 2} of the carrier _{C 2} is the transmission ratio is equal to _{(1 + α 2) / α} 2.

On the other hand, since the gear ratio α ₁ , α ₂ is α ₁ <α ₂ , the electric motor 70 is set so that the ring gear R1 of the first planetary gear mechanism 50A is in the rotational speed state of the black circle on the straight line shown by the solid line L in FIG. by rotating a sun gear S ₁ of the first planetary gear mechanism 50A which rotates integrally with the second cam 44, rotated by the sun gear S ₂ and the constant velocity of the second planetary gear mechanism 60A which rotates integrally with the first cam 42 Can be made.

Rpm state indicated by a black circle in FIG. 5, the electric motor 70, rotating in the same direction of the first planetary gear mechanism 50A of the ring gear R ₁ both carrier C _1, C ₂ of rotation and the same direction (the movable sheave 12: positive Direction) and a non-zero predetermined speed (a constant speed having a magnitude corresponding to the ratio of the tooth number ratios α ₁ and α ₂ ).

If the relationship between the tooth number ratios α ₁ and α ₂ is reversed (that is, α ₁ > α ₂ , the tooth number ratio α ₁ in this case is indicated by α ₁ ′ in FIG. 5), the electric motor The ring gear R ₁ of the first planetary gear mechanism 50A may be rotated by the motor 70 in the opposite direction (negative direction) to the rotation of the carriers C ₁ and C _{2 at} the rotation speed indicated by a double circle in FIG. That is, when the gear ratio alpha ₁ of first planetary gear mechanism 50 is greater than the gear ratio alpha ₂ of second planetary gear mechanism 60A, as shown by the two-dot chain line on the extension of the solid line L in FIG. 5 will be the position of R1 is collinear diagram is changed to the position of the R1', second to the sun gear S ₁ of the first planetary gear mechanism 50A which rotates integrally with the second cam 44 rotates integrally with the first cam 42 to rotate with the sun gear S ₂ and a constant velocity of the planetary gear mechanism 60A is doubly Figure 5 to the ring gear of the R ₁ both carriers C ₁ of the first planetary gear mechanism _50A, C ₂ of rotation and reverse direction (negative direction) It is rotated at a predetermined speed indicated by a circle.

That is, in the case of the relationship of the tooth number ratio α ₁ <α ₂ , the ring gear R ₁ rotates at a predetermined speed in the positive direction, and in the case of the relationship of the tooth number ratio α ₁ > α ₂ , the ring gear R _1. Is rotating in the negative direction at a predetermined speed.
Then, when the rotational speed of the electric motor 70 is increased from each state and the speed is increased in the forward direction from each predetermined speed, the alignment chart of the first planetary gear mechanism 50A is as shown by a broken line La in FIG. to become, the sun gear _{S 1} of the first planetary gear mechanism 50A is slower than that of the sun gear _{S 2} of the second planetary gear mechanism 60A. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. Then, when the continuously variable transmission 5 becomes a desired transmission ratio, the rotational speed of the electric motor 70 is a ring gear R ₁ to be a predetermined rotational speed indicated by a black circle.

On the other hand, when the tooth number ratio α ₁ <α ₂ , the ring gear R ₁ rotates in the positive direction, and when the tooth number ratio α ₁ > α ₂ , the ring gear R ₁ moves in the negative direction. When the rotational speed of the electric motor 70 is decelerated from the rotating state and the speed is increased in the positive direction from each predetermined speed, the collinear diagram of the first planetary gear mechanism 50A is indicated by a broken line Lb in FIG. as becomes, the sun gear _{S 1} of the first planetary gear mechanism 50A is faster than the sun gear _{S 2} of the second planetary gear mechanism 60A. That is, the second cam 44 is faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. Then, when the continuously variable transmission 5 becomes a desired transmission ratio, the rotational speed of the electric motor 70 is a ring gear R ₁ to be a predetermined rotational speed indicated by a black circle.

Therefore, when changing the gear ratio of the continuously variable transmission 5 (that is, when shifting), the rotational speed of the electric motor 70 is changed from a predetermined speed at which the sun gears S _{1 and} S ₂ rotate at a constant speed to a predetermined direction ( When the gear ratio is fixed, the ring gear R ₁ is rotated by the electric motor 70 at a predetermined speed so that the sun gears S _{1 and} S ₂ rotate at a constant speed.

As described above, in the mechanical pulley moving mechanism 30A according to the present embodiment, the first cam 42 is directly connected to the movable sheave 12 and between the first cam 42 and the pulley 6 as in the first embodiment. There is no friction due to rotation. In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between the two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

Similarly to the first embodiment, the ring gear R ₁ of the first planetary gear mechanism 50A is connected to the electric motor 70, also have to fix the ring gear R ₂ of the second planetary gear mechanism 60A to the transmission casing, The structure can be configured simply, which is advantageous in reducing the axial and radial sizes of the apparatus.

In the present embodiment, the gear ratios α ₁ and α ₂ of the planetary gear mechanisms 50A and 60A are different (α ₁ ≠ α ₂ ), and the sun gears S _{1 and} S ₂ are maintained when the gear ratio is kept constant. There is achieved by rotating the electric motor 70 so that the rotational speed of the ring gear R ₁ which rotates at a constant speed at a predetermined speed. In general characteristics of the electric motor 70 (for example, a motor efficiency map of torque and rotation), a large torque is required to control at zero motor rotation, and control is performed in a region where the motor efficiency is relatively low. Since the control is performed while rotating the electric motor 70, it is possible to avoid control in a region where the motor efficiency is low.

Further, as in the first embodiment, since the number of teeth ratio α is set to a value close to 1 in order to make the layout compact, the torque required for the electric motor 70 for changing the speed ratio is set. Can be suppressed.

[Third Embodiment]
As shown in FIG. 6, the mechanical pulley moving mechanism 30C according to the third embodiment, the first planetary gear mechanism 50C, the sun gear S ₁ is equivalent to the first rotating element, first a power transmission mechanism It is connected to the first cam 42 via a two planetary gear mechanism 60C. The ring gear R ₁ corresponds to the second rotating element and is directly connected to the second cam 44. Carrier C ₁ is equivalent to the third rotating element, the electric motor 70 is an actuator is fixed to the rotating shaft of the gear 73a and the electric motor 70 which rotates integrally with the carrier C ₁ are formed on the outer periphery of the carrier C ₁ The first planetary gear mechanism 50C is connected via a gear mechanism 73 in which a gear 73b is engaged.

Also, the second planetary gear mechanism 60C, the sun gear _{S 2} is directly connected to the sun gear _{S 1} of the first planetary gear mechanism 50C, the ring gear _{R 2} is connected to the first cam 42, the transmission casing carrier _{C 2} is not shown It is fixed to. Accordingly, the sun gear S ₁ of the first planetary gear mechanism 50C and the sun gear S ₂ of the second planetary gear mechanism 60C has integrally rotating element that rotates integrally with one another.

In the present embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50C and the second planetary gear mechanism 60C have the same number of teeth. Is set to Thus, for the gear ratio between the tooth number Zr of teeth Zs and the ring gear of the sun gear alpha (= Zs / Zr), the number of teeth of the gear ratio of the first planetary gear mechanism 50C alpha ₁ and the second planetary gear mechanism 60C The ratio α ₂ is the same (α ₁ = α ₂ ).

The speed transmission ratio by the second planetary gear mechanism 60C, which is a power transmission mechanism, is the rotational speed of the first cam 42 (that is, the rotational speed N _R2 of the ring gear R ₂ ) and the rotational speed N of the sun gear S ₂ that is an integral rotating element. is defined as the ratio _N R2 _{/ N S2} and _S2. Since the second planetary gear mechanism 60C is the carrier C ₂ is fixed state, the nomogram is as shown by the solid line L in FIG. The ratio N _R2 / N _S2 between the rotational speed of the sun gear S _{2 and} the rotational speed of the ring gear R ₂ , which is the speed transmission ratio, is equal to −α ₂ .

On the other hand, if the carrier C ₁ of the first planetary gear mechanism 50C to maintain the rotational speed of the electric motor 70 to zero in a fixed state, the ring gear R ₁ of the first planetary gear mechanism 50C is integrally rotated with the first cam 42 rotates the ring gear R ₂ and constant speed of the second planetary gear mechanism 60C for. Alignment chart of first planetary gear mechanism 50C at this time is as shown by the solid line L in FIG. 7 as in the second planetary gear mechanism 60C, a ring gear R ₁ of the first planetary gear mechanism 50C and the second planetary gear mechanism to the ring gear rotation _{R 2} and constant speed of 60C.

Therefore, at this time, the second cam 44 to the ring gear R ₁ is connected is not relatively rotate the first cam 42 the ring gear R ₂ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.
In the present embodiment, the sun gear S ₁ is an integral rotating element, and the tooth number ratio α ₂ and the tooth number ratio α ₁ are the same (α ₁ = α ₂ ). Therefore, the ring gear R ₂ and the sun gear S ₂ are The speed transmission ratio N _R2 / N _S2 is a rotational speed ratio of the ring gear R ₁ that rotates integrally with the second cam 44 in a fixed speed ratio state in which the speed ratio remains constant, and an integral rotating element. This value is equal to the ratio N _R1 / N _S1 (= −α ₂ ) with the rotational speed of the sun gear S ₁ of a certain first planetary gear mechanism 50C.

On the other hand, when the electric motor 70 is rotated in the same direction (positive direction) as the ring gears R ₁ and R ₂ (see the arrow of the speed change a), the collinear diagram of the first planetary gear mechanism 50C is a broken line in FIG. is as shown by la, the ring gear _{R 1} of the first planetary gear mechanism 50C is faster than the ring gear _{R 2} of the second planetary gear mechanism 60C. That is, the second cam 44 is faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Conversely, when the electric motor 70 is rotated in the opposite direction (negative direction) to the ring gears R ₁ and R ₂ (see the arrow of the speed change b), the alignment chart of the first planetary gear mechanism 50C is indicated by a broken line Lb in FIG. is as shown, the ring gear _{R 1} of the first planetary gear mechanism 50C is slower than the ring gear _{R 2} of the second planetary gear mechanism 60C. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Therefore, when changing the gear ratio (that is, when changing gears), the electric motor 70 is rotated in the positive or negative direction, and when the gear ratio is fixed, the electric motor 70 is stopped.
In the mechanical pulley moving mechanism 30C according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and no friction due to rotation occurs between the first cam 42 and the pulley 6. . Further, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that no friction is generated between the two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

Similarly to the first embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50C and the second planetary gear mechanism 60C are mutually connected. Since the same number of teeth is set, it is possible to simplify the overall configuration and to simplify the control program for the electric motor 70.

Further, since the cam torques of the first cam 42 and the second cam 44 are input from the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50C and the second planetary gear mechanism 60C, the first planetary gear mechanism 50C and second The torque load of the planetary gear mechanism 60C is reduced, and the gear width of each planetary gear mechanism 50C, 60C can be reduced.

[Fourth Embodiment]
As shown in FIG. 8, the mechanical pulley moving mechanism 30D according to the fourth embodiment, the first planetary gear mechanism 50D, the ring gear R ₁ is equivalent to the first rotary element, a power transmission mechanism first It is connected to the first cam 42 via a two planetary gear mechanism 60D. The sun gear S ₁ corresponds to the second rotating element and is directly connected to the second cam 44. The carrier C ₁ corresponds to the third rotation element, and the electric motor 70 that is an actuator meshes with a gear 74 a that is formed on the outer periphery of the electric motor 70 and rotates integrally with the carrier C _1, and 74 b that is fixed to the rotation shaft of the electric motor 70. The first planetary gear mechanism 50D is connected through a gear mechanism 74.

Also, the second planetary gear mechanism 60D, the ring gear _{R 2} is directly connected to the ring gear _{R 1} of the first planetary gear mechanism 50D, the sun gear _{S 2} is connected to the first cam 42, the transmission casing carrier _{C 2} is not shown It is fixed to. Therefore, the ring gear R ₁ of the first planetary gear mechanism 50D and the ring gear R ₂ of the second planetary gear mechanism 60D has an integral rotating element that rotates integrally with one another.

In the present embodiment, the sun gears S ₁ and S ₂ and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50D and the second planetary gear mechanism 60D are set to have the same number of teeth. Thus, for the gear ratio between the tooth number Zr of teeth Zs and the ring gear of the sun gear alpha (= Zs / Zr), the number of teeth of the gear ratio of the first planetary gear mechanism 50D alpha ₁ and the second planetary gear mechanism 60D The ratio α ₂ is the same (α ₁ = α ₂ ).

The speed transmission ratio by the second planetary gear mechanism 60D, which is a power transmission mechanism, is such that the rotational speed of the first cam 42 (ie, the rotational speed N _S2 of the sun gear S ₂ ) and the rotational speed N of the ring gear R ₂ that is an integral rotating element. is defined as the ratio _N S2 _{/ N R2} with _R2. Since the second planetary gear mechanism 60D is the carrier C ₂ is fixed state, the nomogram is as shown by the solid line L in FIG. The ratio N _S2 / N _R2 between the rotational speed of the ring gear R _{2 and} the rotational speed of the sun gear S ₂ , which is the speed transmission ratio, is equal to −1 / α ₂ .

On the other hand, if the carrier C ₁ of the first planetary gear mechanism 50D to stop the rotation of the electric motor 70 in a fixed state, the sun gear S ₁ of the first planetary gear mechanism 50D is first rotated integrally with the first cam 42 2 It rotates the sun gear _{S 2} and a constant velocity of the planetary gear mechanism 60D. Alignment chart of first planetary gear mechanism 50D at this time is as shown by the solid line L in FIG. 9 as in the second planetary gear mechanism 60D, the sun gear S ₁ of the first planetary gear mechanism 50D is a second planetary gear mechanism rotating the sun gear _{S 2} and a constant speed of 60D.

Therefore, at this time, the second cam 44 to the sun gear S ₁ is connected is not relatively rotate the first cam 42 the sun gear S ₂ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.
In the present embodiment, the sun gear S ₁ is an integral rotating element, and the tooth number ratio α ₂ and the tooth number ratio α ₁ are the same (α ₁ = α ₂ ). Therefore, the sun gear S ₂ and the ring gear R ₂ are The speed transmission ratio N _S2 / N _R2 is the rotation speed ratio of the two planetary gears because the gear ratio of the two planetary gears is equal to α ₁ = α ₂ . Speed transmission ratio N _S1 / N _R1 (= rotation speed N _S1 of sun gear S ₁ that rotates integrally with second cam 44 and rotation speed N _R1 of ring gear R ₁ of first planetary gear mechanism 50D that is an integral rotation element) −1 / α ₁ ).

On the other hand, when the electric motor 70 is rotated in the same direction (positive direction) as the sun gears S ₁ and S ₂ to increase the rotational speed of the carrier C ₁ (see the arrow of the speed change a), the first planetary gear mechanism. 50D collinear diagram is as shown by the broken line La in FIG. 9, the sun gear _{S 1} of the first planetary gear mechanism 50D is faster than the sun gear _{S 2} of the second planetary gear mechanism 60D. That is, the second cam 44 is faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Conversely, when the electric motor 70 is rotated in the opposite direction (negative direction) to the sun gears S ₁ and S ₂ (see the arrow of the speed change b), the collinear diagram of the first planetary gear mechanism 50D is indicated by a broken line Lb in FIG. is as shown, the sun gear _{S 1} of the first planetary gear mechanism 50D is slower than that of the sun gear _{S 2} of the second planetary gear mechanism 60D. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Therefore, when changing the gear ratio (that is, when shifting), the electric motor 70 is rotated in a predetermined direction, and when the gear ratio is fixed, the rotational speed of the electric motor 70 is set to zero.
In the mechanical pulley moving mechanism 30D according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and no friction due to rotation occurs between the first cam 42 and the pulley 6. . In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

Similarly to the first embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50D and the second planetary gear mechanism 60D are mutually connected. Since the same number of teeth is set, it is possible to simplify the overall configuration and to simplify the control program for the electric motor 70.

[Fifth Embodiment]
As shown in FIG. 10, the power mechanical pulley moving mechanism 30E according to the fifth embodiment, the first planetary gear mechanism 50E, the carrier C ₁ is equivalent to the first rotary element, a power transmission mechanism It is connected to the first cam 42 via the transmission mechanism 60E. The sun gear S ₁ corresponds to the second rotating element and is directly connected to the second cam 44. The ring gear R ₁ is equivalent to the third rotating element, the electric motor 70 is an actuator, fixed to the rotating shaft of the gear 75a and the electric motor 70 which rotates integrally with the ring gear R ₁ is formed on the outer periphery of the ring gear R ₁ It is connected to the first planetary gear mechanism 50E via a gear mechanism 75 in which a gear 75b is engaged.

Further, the power transmission mechanism 60E is constituted by a parallel gear mechanism.
In this parallel gear mechanism, the counter shaft 61, the first gear mechanism formed by meshing the first external gear 61a and the first counter gear 61b, and the second external gear 61d and the second counter gear 61c are meshed. And a second gear mechanism.

That is, the counter shaft 61 is installed in parallel with the rotation axis of the movable sheave 12, and the first counter gear 61b and the second counter gear 61c are coupled to the counter shaft 61 so as to rotate together. A first external gear 61a is coupled to the first cam 42 so as to rotate integrally, and the first external gear 61a and the first counter gear 61b mesh with each other to constitute a first gear mechanism. Also, the carrier C ₁ of the first planetary gear mechanism 50E, the second external gear 61d is coupled to rotate integrally, the first and the second external gear 61d and the second counter gear 61c is in mesh 2 It constitutes a gear mechanism.

The parallel gear mechanism 60E, which is a power transmission mechanism, causes the first cam 42 and the second cam 44 to move when the gear ratio is fixed so that the relative rotational phase of the first cam 42 and the second cam 44 is constant by the electric motor 70 which is an actuator. The speed transmission ratio is set so as to rotate at the same speed in the same direction. That is, the rotational speed (N _{cam 1} ) of the first cam 42 is the speed transmission ratio of the power transmission mechanism 60E with respect to the rotational speed (Nc1) of the carrier C ₁ that is the first rotational element of the first planetary gear mechanism 50. It rotates at a rotation speed according to (N _{cam 1} / Nc1).

In the parallel gear mechanism 60E, the number of teeth of the first external gear 61a is Z _A , the number of teeth of the first counter gear 61b is Z _B , the number of teeth of the second counter gear 61c is Z _C , and the number of teeth of the second external gear 61 is the ratio of the number of teeth and Z _D, the transmission ratio according to a parallel gear mechanism 60E is a power transmission mechanism, the rotational speed N _a and the rotational speed N _D of the second external gear 61d of the first external gear 61a ( N _A / N _D ) and is determined by the number of teeth Z _A to Z _D of each gear 61a to 61d.
Transmission ratio _{= N A / N D = (} N A / N B) · (N C / N D)
= (Z _B / Z _A ) · (Z _D / Z _C ) = (Z _B · Z _D ) / (Z _A · Z _C )

Here, assuming that the gear ratio is fixed when the electric motor 70 is stopped, the alignment chart of the first planetary gear mechanism 50E is as shown by a solid line L in FIG. In FIG. 11, α is the gear ratio of the first planetary gear mechanism 50E.
The speed transmission ratio of the parallel gear mechanism 60E is such that the first cam 42 and the second cam 44 rotate at the same speed in the same direction when the gear ratio is fixed so that the relative rotation phase of the first cam 42 and the second cam 44 is constant. setting N _a / _{N D,} as shown in FIG. 11, the transmission ratio _N a / _{N D} is equal to (1 + α) / α.

If the ring gear R ₁ of the first planetary gear mechanism 50E to stop the rotation of the electric motor 70 in a fixed state, the first planetary gear mechanism 50E, the sun gear S ₁ that rotates integrally with the second cam 44, the carrier C ₁ Rotate at a speed of (1 + α) / α times. In this case, the first external gear 61a that rotates integrally with the first cam 42 also rotates relative to the second external gear 61d to rotate integrally with the carrier C ₁ at (1 + α) / α times the speed.

Therefore, at this time, the second cam 44 to the sun gear S ₁ is connected is not relatively rotate the first cam 42 carrier C ₁ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.

In contrast, (see arrows in shifting a) is actuated so that the electric motor 70 the ring gear R ₁ is rotated in the carrier C ₁ and the sun gear S ₁ and the same direction (positive direction), the first planetary gear mechanism 50E The nomographic chart of FIG. 11 is indicated by a broken line La in FIG. 11, and the sun gear S ₁ (that is, the second cam 44) of the first planetary gear mechanism 50E is at a lower speed than before the operation of the electric motor 70. The two cams 44 rotate relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Conversely, (see arrows in shift b) is actuated so that the electric motor 70 the ring gear R ₁ is rotated in the carrier C ₁ and the sun gear S ₁ and a reverse direction (negative direction), co of the first planetary gear mechanism 50E The diagram is as indicated by the broken line Lb in FIG. 11, and the sun gear S ₁ (ie, the second cam 44) of the first planetary gear mechanism 50E is faster than before the operation of the electric motor 70, and the second cam 44 rotates relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Therefore, when changing the gear ratio (that is, when shifting), the electric motor 70 is rotated in a predetermined direction, and when the gear ratio is fixed, the rotation speed of the electric motor 70 is made zero.

In the mechanical pulley moving mechanism 30E according to this embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and no friction due to rotation is generated between the first cam 42 and the pulley 6. . In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

[Sixth Embodiment]
As shown in FIG. 12, the mechanical pulley moving mechanism 30F according to the sixth embodiment is separated from the rotation axis of the primary pulley 6 (movable sheave 12) with respect to the first planetary gear mechanism 51 and is parallel to the rotation axis. It is arranged on another axis of rotation.
In the first planetary gear mechanism 51, the sun gear S ₃ is coupled to the rotating shaft of the electric motor 70 as an actuator, is the ring gear R ₃ connected to the second cam 44, the carrier C ₃ is drivingly connected to the power transmission mechanism 60F ing.

Carrier C ₃ is equivalent to the first rotating element is connected to the first cam 42 via a power transmission mechanism 60F is a power transmission mechanism. The ring gear R ₃ corresponds to the second rotation element, and an external gear (also referred to as a gear R) 51 a formed on the outside of the ring gear R ₃ and an external gear (gear) formed on the outside of the second cam 44. (Also referred to as A) 51b. The sun gear S ₃ is equivalent to the third rotating element is coupled to a rotating shaft of the electric motor 70 is an actuator.

Further, the power transmission mechanism 60F is configured by a parallel gear mechanism. The parallel gear mechanism (also referred to as a gear B) external gear that is coupled to the first cam 42 and 62a (also referred to as a gear C) external gear that combined external gear 62a and meshing with the carrier C ₃ 62b and , Is composed of.

The parallel gear mechanism 60F, which is a power transmission mechanism, causes the first cam 42 and the second cam 44 to move when the gear ratio is fixed by the electric motor 70, which is an actuator, so that the relative rotation phases of the first cam 42 and the second cam 44 are constant. The speed transmission ratio is set so as to rotate at the same speed in the same direction. That is, the rotation speed of the first cam 42 (N _{cam 1)} is first with respect to the rotational speed of the carrier _{C 3} is a rotary element (Nc3), the transmission ratio of the power transmission mechanism 60F of the first planetary gear mechanism 51 It rotates at a rotation speed according to (N _{cam 1} / Nc3).

In the parallel gear mechanism 60F, when the number of teeth of the external gear 62a coupled to the first cam 42 is Z _B and the number of teeth of the external gear 62b coupled to the carrier C ₃ is Z _C , this is a power transmission mechanism. the transmission ratio by parallel gear mechanism 60F is, _{N B} and the rotational speed of the external gear 62b (the rotational speed of the carrier _{C 3)} ratio of _{N C} (rotational speed of the first cam 42) external teeth rotational speed of the gear 62a ( N _B / N _C ) and is determined by the number of teeth Z _B and Z _C of each gear 62a and 62b.
Speed transmission ratio = N _B / N _C = Z _C / Z _B

Here, assuming that the gear ratio is fixed when the electric motor 70 is stopped, the alignment chart of the first planetary gear mechanism 51 is as shown by a solid line L in FIG. In FIG. 13, α is the gear ratio of the first planetary gear mechanism 51. As shown in FIG. 13, the ratio between the rotational speed of the ring gear R _{3 and} the rotational speed of the carrier C ₃ is 1 + α.

Further, the rotational speed ratio between _{N R} [rotation speed of the external gear (gear R) 51a] Carrier _{C 3} rotational speed rotational speed of _{N A} and the ring gear _{R 3} [external gear (gear A) the rotational speed of 51b] (N _A / N _ROUT ) is determined by the number of teeth Z _A and Z _R of each gear 62a and 62b, and is as follows.
N _A / N _R = Z _R / Z _A

Here, in consideration of the rotational speed ratio _(N A / N _R), the first cam 42, when the fixed gear ratio of the relative rotational phase of the second cam 44 is constant, the first cam 42, second cam 44 To set to rotate at the same speed in the same direction, the speed transmission ratio of the parallel gear mechanism 60F (ratio of the number of teeth Z _B and Z _C of each gear 62a and 62b) is set so as to satisfy the relationship of the following equation: do it.
N _B / N _C = Z _C / Z _B = (1 + α) · (N _A / N _R ) = (1 + α) · (Z _R / Z _A )
In the collinear chart of FIG. 13, Z _R / Z _A = 1 is set for easy understanding.

By setting the transmission ratio of the parallel gear mechanism 60F Thus, if the sun gear S ₃ of the first planetary gear mechanism 51 to stop the rotation of the electric motor 70 in a fixed state, the second cam 44 first A constant rotational phase is maintained without rotating relative to the cam 42. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.

In contrast, (see arrows in shifting a) is actuated so that the electric motor 70 is the sun gear S ₃ rotates in the same direction as the carrier C ₃ and the ring gear R ₃ (positive direction), the first planetary gear mechanism 50F The nomographic chart of FIG. 13 is indicated by a broken line La in FIG. 13, and the ring gear R ₃ (that is, the second cam 44) of the first planetary gear mechanism 50F is at a lower speed than before the rotation of the electric motor 70, The second cam 44 rotates relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Conversely, (see arrows in shift b) is actuated so that the electric motor 70 is the sun gear S ₃ is rotated in the reverse direction (negative direction) and the carrier C ₃ and the ring gear R _3, co of the first planetary gear mechanism 50F The diagram is as indicated by the broken line Lb in FIG. 13, and the ring gear R ₃ (that is, the second cam 44) of the first planetary gear mechanism 50F is at a higher speed than before the electric motor 70 is rotated, The cam 44 rotates relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Therefore, when changing the gear ratio (that is, when shifting), the electric motor 70 is rotated in a predetermined direction, and when the gear ratio is fixed, the rotation speed of the electric motor 70 is made zero.

As described above, in the mechanical pulley moving mechanism 30F according to the present embodiment, the first cam 42 is directly connected to the movable sheave 12 as in the first embodiment, and the first cam 42 and the pulley 6 are interposed between them. No friction caused by rotation. In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

As in the first embodiment, when changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 And the relative rotational phase of the second cam 44 are changed. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

[Seventh Embodiment]
As shown in FIG. 14, the mechanical pulley moving mechanism 30G according to the seventh embodiment is similar to the sixth embodiment in that the first planetary gear mechanism 51 includes the rotation axis of the primary pulley 6 (movable sheave 12). It is separated and arranged on another rotation axis parallel to the rotation axis, and is configured in the same manner as in the sixth embodiment.
That is, in the first planetary gear mechanism 51, the sun gear S ₃ is coupled to the rotating shaft of the electric motor 70 as an actuator, it is the ring gear R ₃ connected to the second cam 44, drive coupling carrier C ₃ is in the power transmission mechanism 60G Has been.

Carrier C ₃ is equivalent to the first rotating element is connected to the first cam 42 via a power transmission mechanism 60G is a power transmission mechanism. The ring gear R ₃ corresponds to the second rotation element, and an external gear (also referred to as gear R 1) 51 a formed on the outside of the ring gear R ₃ and an external gear (gear on the outside of the second cam 44). (Also referred to as A) 51b. The sun gear S ₃ is corresponds to the third rotary element is coupled to a rotating shaft of the electric motor 70 is an actuator.

Meanwhile, a planetary gear mechanism (second planetary gear mechanism) 63 is used for the power transmission mechanism 60G. The second planetary gear mechanism 63 is disposed coaxially with the rotation axis of the first planetary gear mechanism 51 that is separated from the rotation axis of the primary pulley 6 (movable sheave 12) and is parallel to the rotation axis. It is comprised by the rotation element similar to 51. FIG.

In other words, the second planetary gear mechanism 63 includes a sun gear S ₄ arranged coaxially with the sun gear S _{3 of} the first planetary gear mechanism 51 and a carrier arranged coaxially with the carrier C _{3 of} the first planetary gear mechanism 51. C ₄ and a ring gear R ₄ arranged coaxially with the ring gear R _{3 of} the first planetary gear mechanism 51, and the carrier C ₄ has a planetary gear P similar to the planetary gear P _{3 of} the first planetary gear mechanism 51. ₄ is equipped.

In the present embodiment, the sun gear S ₄ , the ring gear R ₄ , and the planetary gear P ₄ of the second planetary gear mechanism 63 have the same teeth as the corresponding sun gear S ₃ , ring gear R ₃ , and planetary gear P _{3 of} the first planetary gear mechanism 51, respectively. Consists of numbers. Then, the carrier C ₄ of the second planetary gear mechanism 63 and the carrier C ₃ of the first planetary gear mechanism 51 is coupled so as to rotate integrally. Then, (also referred to as a gear R2) external gear formed on the outer side of the ring gear R ₄ and 63 b, (also referred to as a gear B) external gear formed on the outer side of the first cam 42 63a and is engaged.

The power transmission mechanism 60G is configured so that the first cam 42 and the second cam 44 have the same speed in the same direction when the gear ratio is fixed so that the relative rotation phase of the first cam 42 and the second cam 44 is constant by the electric motor 70 as an actuator. The speed transmission ratio is set to rotate.

The rotational speed (N _{cam 2} ) of the second cam 44 is the speed transmission ratio of the first planetary gear mechanism 51 to the rotational speed (Nc 3) of the carrier C ₃ that is the first rotational element of the first planetary gear mechanism 51. It rotates at a rotation speed corresponding to (N _{cam 2} / Nc 3).
On the other hand, the rotational speed of the first cam 42 (N _{cam 1)} is first with respect to the rotational speed of the carrier _{C 3} is a rotary element (Nc3), the transmission ratio of the power transmission mechanism 60G of the first planetary gear mechanism 51 It rotates at a rotation speed according to (N _{cam 1} / Nc3).

Here, the number of teeth of the external gear (gear A) 62a coupled to the second cam 44 is Z _A , and the number of teeth of the external gear (gear R1) 51a formed outside the ring gear R ₃ is Z _R1 , the ring gear _{R 4} of the external gear formed on the outer side (gear R2) 63 b the number of teeth _Z of _R2, the number of teeth of the first external gear that is coupled to the cam 42 (gear B) 62a and _{Z B,} first gear ratio of the planetary gear mechanism 51 (= Zs / Zr) of alpha _1, the gear ratio of the second planetary gear mechanism 63 when (= Zs / Zr) is referred to as alpha _2, the power transmission mechanism 60G for the first cam 42 The speed transmission ratio (N _{cam 1} / Nc 3) and the speed transmission ratio (N _{cam 2} / Nc 3) of the first planetary gear mechanism 51 with respect to the second cam 44 are as follows.
(N _{cam 1} / Nc3) = (1 + α ₂ ) · (Z _R2 / Z _B )
(N _{cam 2} / Nc 3) = (1 + α ₁ ) · (Z _R1 / Z _A )

When the transmission ratio is fixed so that the relative rotational phase of the first cam 42 and the second cam 44 is fixed, the speed transmission ratio (60G) of the power transmission mechanism 60G is set so that the first cam 42 and the second cam 44 rotate at the same speed in the same direction. to set the N _cam 1 / Nc3), as shown in the following equation, the transmission ratio (N _cam 1 / Nc3) and the transmission ratio (N _cam 2 / Nc3) and may be set to be equal .
(1 + α ₂ ) · (Z _R2 / Z _B ) = (1 + α ₁ ) · (Z _R1 / Z _A )

In the present embodiment, the collinear diagram of the first planetary gear mechanism 51 and the second planetary gear mechanism 63 is shown by a solid line L in FIG. In FIG. 15, α ₁ is the gear ratio of the first planetary gear mechanism 51, and α ₂ is the gear ratio of the second planetary gear mechanism 63. As shown in FIG. 15, the ratio between the rotational speed of the ring gears R ₃ and R _{4 and} the rotational speed of the carriers C ₃ and C ₄ is 1 + α ₁ and 1 + α ₂ .
Thus, in the present embodiment, since the gear ratio of the first planetary gear mechanism 51 alpha ₁ and the gear ratio alpha ₂ of second planetary gear mechanism 63 is set equal, it should satisfy the following relation .
Z _R2 / Z _B = Z _R1 / Z _A

By setting the transmission ratio of the power transmission mechanism 60G Thus, if the sun gear R ₃ of the first planetary gear mechanism 51 to stop the rotation of the electric motor 70 in a fixed state, the second cam 44 first A constant rotational phase is maintained without rotating relative to the cam 42. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.

In contrast, (see arrows in shifting a) is actuated so that the electric motor 70 is the sun gear S ₃ rotates in the same direction as the carrier C ₃ and the ring gear R ₃ (positive direction), the first planetary gear mechanism 50F 15 is indicated by a broken line La in FIG. 15, and the ring gear R ₃ (that is, the second cam 44) of the first planetary gear mechanism 50F becomes lower than before the rotation operation of the electric motor 70, The second cam 44 rotates relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Conversely, (see arrows in shift b) is actuated so that the electric motor 70 is the sun gear S ₃ is rotated in the reverse direction (negative direction) and the carrier C ₃ and the ring gear R _3, co of the first planetary gear mechanism 50F The diagram is as indicated by the broken line Lb in FIG. 15, and the ring gear R ₃ (that is, the second cam 44) of the first planetary gear mechanism 50F is at a higher speed than before the electric motor 70 is rotated, The cam 44 rotates relative to the first cam 42 to change the relative rotation phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

Therefore, when changing the gear ratio (that is, when shifting), the electric motor 70 is rotated in a predetermined direction, and when the gear ratio is fixed, the rotation speed of the electric motor 70 is made zero.

As described above, in the mechanical pulley moving mechanism 30G according to this embodiment, the first cam 42 is directly connected to the movable sheave 12 as in the first embodiment, and the first cam 42 and the pulley 6 are interposed between them. No friction caused by rotation. In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

As in the first embodiment, when changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 And the relative rotational phase of the second cam 44 are changed. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

[Eighth Embodiment]
As shown in FIG. 16, the mechanical pulley moving mechanism 30H according to the eighth embodiment, for the first planetary gear mechanism 50H, the sun gear S ₁ is equivalent to the first rotating element, first a power transmission mechanism It is connected to the first cam 42 via a two planetary gear mechanism 60H. The carrier C ₁ corresponds to the second rotating element and is directly connected to the second cam 44. The ring gear R ₁ is equivalent to the third rotating element, the electric motor 70 is an actuator, fixed to the rotating shaft of the gear 76a and the electric motor 70 which rotates integrally with the ring gear R ₁ is formed on the outer periphery of the ring gear R ₁ The first planetary gear mechanism 50H is connected through a gear mechanism 76 in which a gear 76b is engaged.

Also, the second planetary gear mechanism 60H, the sun gear _{S 2} is directly connected to the sun gear _{S 1} of the first planetary gear mechanism 50H, carrier _{C 2} is connected to the first cam 42, the transmission casing ring gear _{R 2} is not shown It is fixed to. Accordingly, the sun gear S ₁ of the first planetary gear mechanism 50H and the sun gear S ₂ of the second planetary gear mechanism 60H has an integral rotating element that rotates integrally with one another.

In the present embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50H and the second planetary gear mechanism 60H have the same number of teeth. Is set to Thus, for the gear ratio between the tooth number Zr of teeth Zs and the ring gear of the sun gear alpha (= Zs / Zr), the number of teeth of the gear ratio of the first planetary gear mechanism 50H alpha ₁ and the second planetary gear mechanism 60H The ratio α ₂ is the same (α ₁ = α ₂ ).

The speed transmission ratio by the second planetary gear mechanism 60H, which is a power transmission mechanism, is the rotational speed of the first cam 42 (that is, the rotational speed N _C2 of the carrier C ₂ ) and the rotational speed N of the sun gear S ₂ that is an integral rotating element. It is defined as the ratio _N C2 _{/ N S2} and _S2. Since the second planetary gear mechanism 60H ring gear R ₂ is fixed state, the nomogram is as shown by the solid line L in FIG. 17. The ratio N _C2 / N _S2 between the rotational speed of the sun gear S _{2 and} the rotational speed of the carrier C ₂ , which is the speed transmission ratio, is equal to α ₂ / (1 + α ₂ ).

On the other hand, if the ring gear R ₁ of the first planetary gear mechanism 50H maintains the rotational speed of the electric motor 70 to zero in a fixed state, the carrier C ₁ of the first planetary gear mechanism 50H is rotated integrally with the first cam 42 rotating the carrier C ₂ and a constant velocity of the second planetary gear mechanism 60H for. Alignment chart of first planetary gear mechanism 50H of this time is as shown by the solid line L in FIG. 17 as in the second planetary gear mechanism 60H, carrier C ₁ of the first planetary gear mechanism 50H second planetary gear mechanism rotating the carrier _{C 2} and a constant velocity of 60H.

Therefore, at this time, the second cam 44 to the carrier C ₁ is connected is not relatively rotate the first cam 42 carrier C ₂ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.
In the present embodiment, the sun gear S ₁ is an integral rotating element, and the tooth number ratio α ₂ and the tooth number ratio α ₁ are the same (α ₁ = α ₂ ). Therefore, the ring gear R ₂ and the sun gear S ₂ are The speed transmission ratio N _R2 / N _S2 is the rotational speed ratio of the carrier C ₁ that rotates integrally with the second cam 44 and the integral rotation element in the fixed speed ratio state in which the speed ratio remains constant. It becomes a value equal to the ratio N _C1 / N _S1 (= α ₂ / (1 + α ₂ )) with the rotational speed of the sun gear S ₁ of a certain first planetary gear mechanism 50H.

On the other hand, when the electric motor 70 is rotated in the same direction (forward direction) as the ring gears R ₁ and R ₂ (see the arrow of the speed change a), the alignment chart of the first planetary gear mechanism 50H is a broken line in FIG. is as shown by la, the ring gear _{R 1} of the first planetary gear mechanism 50H is faster than the ring gear _{R 2} of the second planetary gear mechanism 60H. That is, the second cam 44 is faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Conversely, when the electric motor 70 is rotated in the opposite direction (negative direction) to the ring gears R ₁ and R ₂ (see the arrow of the speed change b), the collinear diagram of the first planetary gear mechanism 50H is indicated by a broken line Lb in FIG. is as shown, the ring gear _{R 1} of the first planetary gear mechanism 50H is slower than the ring gear _{R 2} of the second planetary gear mechanism 60H. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Therefore, when changing the gear ratio (that is, when changing gears), the electric motor 70 is rotated in the positive or negative direction, and when the gear ratio is fixed, the electric motor 70 is stopped.
In the mechanical pulley moving mechanism 30H according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and friction due to rotation does not occur between the first cam 42 and the pulley 6. . Further, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that no friction is generated between the two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

Similarly to the first embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50H and the second planetary gear mechanism 60H are mutually connected. Since the same number of teeth is set, it is possible to simplify the overall configuration and to simplify the control program for the electric motor 70.

Further, the ring gear _{R 1} of the first planetary gear mechanism 50H coupled to the electric motor 70, also have to fix the ring gear _{R 2} of the second planetary gear mechanism 60H to the transmission casing, the ring gear _R 1, _{R 2} mechanisms Since the electric motor 70 and the transmission casing are easily accessible, the structure can be simplified, which is advantageous in reducing the axial and radial sizes of the device.

[Ninth Embodiment]
As shown in FIG. 18, the mechanical pulley moving mechanism 30I according to a ninth embodiment, the first planetary gear mechanism 50I, the ring gear R ₁ is equivalent to the first rotating element, first a power transmission mechanism 2
It is connected to the first cam 42 via a planetary gear mechanism 60I. The carrier C ₁ corresponds to the second rotating element and is directly connected to the second cam 44. The sun gear S ₁ is equivalent to the third rotating element, the electric motor 70 is an actuator, fixed to the rotating shaft of the gear 77a and the electric motor 70 which rotates integrally with the sun gear S ₁ formed on the outer periphery of the sun gear S ₁ It is connected to the first planetary gear mechanism 50I through a gear mechanism 77 in which a gear 77b is engaged.

Also, the second planetary gear mechanism 60I, the ring gear _{R 2} is directly connected to the ring gear _{R 1} of the first planetary gear mechanism 50I, the carrier _{C 2} is connected to the first cam 42, the transmission casing sun gear _{S 2} is not shown It is fixed to. Therefore, the ring gear R ₁ of the first planetary gear mechanism 50I and the ring gear R ₂ of the second planetary gear mechanism 60I has an integral rotating element that rotates integrally with one another.

In the present embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50I and the second planetary gear mechanism 60I have the same number of teeth. Is set to Thus, for the gear ratio between the tooth number Zr of teeth Zs and the ring gear of the sun gear alpha (= Zs / Zr), the number of teeth of the gear ratio of the first planetary gear mechanism 50I alpha ₁ and the second planetary gear mechanism 60I The ratio α ₂ is the same (α ₁ = α ₂ ).

The speed transmission ratio by the second planetary gear mechanism 60I that is a power transmission mechanism is such that the rotational speed of the first cam 42 (ie, the rotational speed N _C2 of the carrier C ₂ ) and the rotational speed N of the ring gear R ₂ that is an integral rotating element. is defined as the ratio _N C2 _{/ N R2} with _R2. Since the second planetary gear mechanism 60I of the sun gear S ₂ is fixed state, the nomogram is as shown by the solid line L in FIG. 19. The ratio N _C2 / N _R2 between the rotational speed of the ring gear R _{2 and} the rotational speed of the carrier C ₂ , which is the speed transmission ratio, is equal to 1 / (1 + α ₂ ).

On the other hand, if the sun gear S ₁ of the first planetary gear mechanism 50I to maintain the rotational speed of the electric motor 70 to zero in a fixed state, the carrier C ₁ of the first planetary gear mechanism 50I is integrally rotated with the first cam 42 rotating the carrier C ₂ and a constant velocity of the second planetary gear mechanism 60I that. Alignment chart of first planetary gear mechanism 50I of this time is as shown by the solid line L in FIG. 19 as in the second planetary gear mechanism 60I, the carrier C ₁ of the first planetary gear mechanism 50I second planetary gear mechanism rotating the carrier _{C 2} and a constant speed of 60I.

Therefore, at this time, the second cam 44 to the carrier C ₁ is connected is not relatively rotate the first cam 42 carrier C ₂ is connected, to maintain a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.
In the present embodiment, the sun gear S ₁ is an integral rotating element, and the tooth number ratio α ₂ and the tooth number ratio α ₁ are the same (α ₁ = α ₂ ). Therefore, the ring gear R ₂ and the sun gear S ₂ are The speed transmission ratio N _R2 / N _S2 is the rotational speed ratio of the carrier C ₁ that rotates integrally with the second cam 44 and the integral rotation element in the fixed speed ratio state in which the speed ratio remains constant. It becomes a value equal to the ratio N _C1 / N _R1 (= 1 / (1 + α ₂ )) with the rotational speed of the ring gear R ₁ of a certain first planetary gear mechanism 50I.

On the other hand, when the electric motor 70 is rotated in the same direction (positive direction) as the sun gears S ₁ and S ₂ (see the arrow of the speed change a), the collinear diagram of the first planetary gear mechanism 50I is a broken line in FIG. is as shown by la, the sun gear _{S 1} of the first planetary gear mechanism 50I is faster than the sun gear _{S 2} of the second planetary gear mechanism 60I. That is, the second cam 44 to the carrier C ₁ is connected is turned faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, the relative rotational phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Conversely, when the electric motor 70 is rotated in the opposite direction (negative direction) to the sun gears S ₁ and S ₂₂ (see the arrow of the speed change b), the alignment chart of the first planetary gear mechanism 50I is indicated by a broken line Lb in FIG. is as shown, the sun gear _{S 1} of the first planetary gear mechanism 50I is slower than that of the sun gear _{S 2} of the second planetary gear mechanism 60I. That is, the second cam 44 is slower than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed. When the continuously variable transmission 5 has a desired gear ratio, the rotational speed of the electric motor 70 is returned to zero.

Therefore, when changing the gear ratio (that is, when changing gears), the electric motor 70 is rotated in the positive or negative direction, and when the gear ratio is fixed, the electric motor 70 is stopped.
In the mechanical pulley moving mechanism 30I according to this embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and no friction due to rotation is generated between the first cam 42 and the pulley 6. . Further, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that no friction is generated between the two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

When changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the pulley 6), so that the first cam 42 and the second cam 44 Change the relative rotation phase. At this time, the thrust of the belt 26 received by the second cam 44 toward the other end side (right side in the figure) via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. As in the first embodiment, the speed change is short and the speed of the relative rotation is low, so that friction due to the relative rotation is generated but suppressed to a small amount.

Similarly to the first embodiment, the sun gears S ₁ and S ₂ , the planetary gears P ₁ and P ₂ , and the ring gears R ₁ and R _{2 of} the first planetary gear mechanism 50I and the second planetary gear mechanism 60I are mutually connected. Since the same number of teeth is set, it is possible to simplify the overall configuration and to simplify the control program for the electric motor 70.

Further, the sun gear _{S 1} of the torque (sun gear _{torque) T S1} for connecting to the electric motor 70, 1 + alpha ₂ when the second torque of the carrier _{C 1} that connects the cam 44 (carrier torque) and _{T C1,} gear ratio alpha ₁ , T _S1 = [α ₁ / (1 + α ₁ )] T _C1 , and the sun gear torque T _S1 is always smaller than the carrier torque T _C1 regardless of the gear ratio α ₁ . Therefore, the torque (= sun gear torque T _S1 ) input from the sun gear S ₁ by the electric motor 70 can be reduced regardless of the gear ratio α ₁ .

[Others]
In the third, fourth, eighth, and ninth embodiments, the sun gears S ₁ and S _{2 of} the first planetary gear mechanisms 50C, 50D, 50H, and 50I and the second planetary gear mechanisms 60C, 60D, 60H, and 60I, and the ring gears. Although R ₁ and R ₂ are set to the same number of teeth, the sun gears S ₁ and S ₂ and the ring gears of the first planetary gear mechanism 50A and the second planetary gear mechanism 60A as in the second embodiment. Each of R ₁ and R ₂ may be set to a different number of teeth.
In this case, similarly to the second embodiment, the control is performed while rotating the electric motor 70 even when the gear ratio is fixed, and therefore, control in a region where the motor efficiency is low can be avoided.

In the fifth to seventh embodiments, the speed ratio is set to be constant by setting the electric motor 70 as an actuator to a rotation stop state at a rotation speed of zero, but as in the second embodiment, Even when the gear ratio is fixed, the electric motor 70 may be controlled to rotate, and in this case, control in a region where the motor efficiency is low can be avoided.

In each of the embodiments described above, from the viewpoint of ease of construction, the integrally rotating element that rotates integrally with the first planetary gear mechanism and the second planetary gear mechanism is a carrier or sun gear. A ring gear may be used.
Furthermore, in each of the above embodiments, the primary pulley 6 is equipped with a mechanical pulley moving mechanism, but the secondary pulley 14 may be equipped with a mechanical pulley moving mechanism. Further, a mechanical pulley moving mechanism can be provided on both the primary pulley 6 and the secondary pulley 14.

2 Drive source 5 Continuously variable transmission 6 Primary pulley 8 Primary sheave 6 fixed sheave 10 Primary pulley 6 rotation shaft 12 Primary pulley 6 movable sheave 14 Secondary pulley 16 Secondary pulley 14 fixed sheave 18 Secondary pulley 14 drive shaft 20 Movable sheave of secondary pulley 14 22 Spring constituting thrust adjusting mechanism 24 Cam mechanism constituting thrust adjusting mechanism 26 Belt (endless belt-like member)
30, 30A-30I Mechanical pulley moving mechanism 40 Torque cam mechanism 50, 50A-50E, 50H, 50I, 51 First planetary gear mechanism 60, 60A-60D, 60H, 60I Second planetary gear mechanism 60E- as a power transmission mechanism 60G power transmission mechanism 63 second electric motor 80 slide permitting mechanism S ₁ ~ _{S 4} sun gears C ₁ ~ _{C 4} carrier R ₁ ~ _{R 4} ring gear P ₁ ~ _{P 4} planetary gear as planetary gear mechanism 70 actuator

Claims (11)

A primary pulley and a secondary pulley, a belt spanned between the two pulleys, and a mechanical pulley moving mechanism that adjusts a gear ratio by moving a movable sheave of at least one of the pulleys in the axial direction. In a continuously variable transmission,
The mechanical pulley moving mechanism is
The first cam member is directly connected to the movable sheave, the first cam member being directly connected to the movable sheave, the first and second cam members being arranged in series on the same axis as the movable sheave. A torque cam mechanism that changes a total length when the relative rotation phase of the cam member with respect to the first cam member is changed, and moves the movable sheave in an axial direction;
An actuator for changing or maintaining the relative rotational phase of the second cam member;
It has three rotating elements, a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member via a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism coupled to the second cam member and the remaining rotating elements coupled to the actuator;
The power transmission mechanism causes the first and second cam members to rotate at the same speed in the same direction when the gear ratio is fixed so that the relative rotation phase of the first and second cam members is constant by the actuator. A continuously variable transmission, characterized in that a speed transmission ratio is set. The power transmission mechanism includes a second planetary gear mechanism that is arranged in series on the same axis as the first planetary gear mechanism, and includes three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the The continuously variable transmission according to claim 1, wherein rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements. In the second planetary gear mechanism, the sun gear is coupled to the first cam member, and the ring gear is fixed,
In the first planetary gear mechanism, the sun gear is coupled to the second cam member,
The continuously variable transmission according to claim 2, wherein the carrier is coupled to the carrier of the second planetary gear mechanism, and the ring gear is coupled to the actuator. In the second planetary gear mechanism, the ring gear is coupled to the first cam member, and the carrier is fixed.
In the first planetary gear mechanism, the sun gear is coupled to the sun gear of the second planetary gear mechanism, the ring gear is coupled to the second cam member, and the carrier is coupled to the actuator. The continuously variable transmission according to claim 2. In the second planetary gear mechanism, the sun gear is coupled to the first cam member, and the carrier is fixed.
In the first planetary gear mechanism, the sun gear is coupled to the second cam member, the carrier is coupled to the actuator, and the ring gear is coupled to the ring gear of the second planetary gear mechanism. The continuously variable transmission according to claim 2. The sun gear, carrier and ring gear of the second planetary gear mechanism are set to the same number of teeth as the sun gear, carrier and ring gear of the first planetary gear mechanism,
The speed transmission ratio of the power transmission mechanism defined as the ratio of the rotation speed of the integral rotation element and the rotation speed of the first cam is the rotation speed of the integral rotation element and the rotation speed of the second cam. The continuously variable transmission according to any one of claims 2 to 5, wherein the continuously variable transmission is set to a value equal to the ratio. The sun gear, carrier and ring gear of the second planetary gear mechanism are set to different numbers of teeth from the sun gear, carrier and ring gear of the first planetary gear mechanism,
The speed transmission ratio of the power transmission mechanism defined as the ratio of the rotation speed of the integral rotation element and the rotation speed of the first cam is the rotation speed of the integral rotation element and the rotation speed of the second cam. The continuously variable transmission according to any one of claims 2 to 5, wherein the continuously variable transmission is set to a value different from the ratio. In the first planetary gear mechanism, the sun gear is coupled to the second cam member, the ring gear is coupled to the actuator, and the carrier is drivingly coupled to the power transmission mechanism,
The power transmission mechanism is coupled to a counter shaft installed in parallel with a rotation axis of the movable sheave, a first counter gear and a second counter gear coupled to the counter shaft, and the first cam member. A parallel gear mechanism comprising: a first external gear that meshes with one counter gear; and a second external gear that is coupled to the carrier and meshes with the second counter gear. The continuously variable transmission according to Item 2. The first planetary gear mechanism is disposed on a rotation axis parallel to a rotation axis of the movable sheave;
In the first planetary gear mechanism, the sun gear is connected to the actuator, the ring gear is connected to the second cam member, and the carrier is drivingly connected to the power transmission mechanism,
The power transmission mechanism includes a parallel gear mechanism including an external gear coupled to the first cam member and a counter gear coupled to the carrier and meshing with the external gear. The continuously variable transmission according to claim 2. The first planetary gear mechanism is disposed on a rotation axis parallel to a rotation axis of the movable sheave;
In the first planetary gear mechanism, the sun gear is connected to the actuator, the ring gear is connected to the second cam member, and the carrier is drivingly connected to the power transmission mechanism,
The power transmission mechanism is arranged in series on the same axis as the first planetary gear mechanism, and includes a second planetary gear mechanism having three rotating elements of a sun gear, a carrier, and a ring gear, and an outer periphery of a ring gear of the second planetary gear mechanism. And a first external gear integrally provided with the first cam member and an external gear coupled to the first cam member and meshing with the first external gear. The continuously variable transmission described. The slide allowing mechanism for allowing the axial movement of the first cam member and transmitting the rotation is interposed between the power transmission mechanism and the first cam. The continuously variable transmission according to any one of 1 to 10.

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