JP6690004B2 - Continuously variable transmission - Google Patents

Description

The present invention relates to a continuously variable transmission that axially moves a movable sheave by a mechanical actuator that uses 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 a groove width of the pulley.
For example, in Patent Document 1, a slide cam that slides in the axial direction by a cam mechanism to move the movable sheave when the rotation phase is changed, and a mechanical actuator such as a motor that changes the rotation phase of the slide cam are disclosed. A continuously variable transmission having the same is disclosed.

  When the movable sheave is moved in the axial direction by the actuator, the drive member that is driven by the actuator like the slide cam and moves the movable sheave in the axial direction is basically non-rotation except when the rotation phase is changed. On the other hand, since the movable sheave rotates at a high speed, a thrust bearing which allows relative rotation and transmits an 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 in response to the differential rotation between the two while always receiving the axial load due to the belt tension. For this reason, the thrust bearing becomes a friction of the pulley rotation, which 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 the belt tension also increases, and the friction of the pulley rotation due to the thrust bearing also increases, so that the increase in power transmission loss becomes more remarkable.

  The present invention has been devised in view of such problems, and in a continuously variable transmission that axially moves a movable sheave using a mechanical actuator, it is possible to reduce the friction of pulley rotation and to reduce power transmission loss. An object of the present invention is to provide a continuously variable transmission capable of suppressing the occurrence of

( 1 ) In order to achieve the above object, a first continuously variable transmission according to the present invention includes a primary pulley and a secondary pulley, a belt spanned by the pulleys, and at least one of the pulleys. And a mechanical pulley moving mechanism that adjusts a gear ratio by moving the movable sheave in the axial direction, the mechanical pulley moving mechanism slidingly contacting the cam surfaces of the mechanical pulley moving mechanism with each other. It has first and second cam members arranged coaxially in series with the sheave, the first cam member being directly connected to the movable sheave, and the second cam member with respect to the first cam member. When the relative rotation phase is changed, the overall length is changed to move the movable sheave in the axial direction, a torque cam mechanism that changes or makes the relative rotation phase of the second cam member constant, a sun gear, and a cap. A, 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 the first rotating member. A first planetary gear mechanism connected to the second cam member and the remaining rotary element connected to the actuator, wherein the power transmission mechanism uses the actuator to move the first and second cam members relative to each other. The speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction when the gear ratio is fixed such that the rotation phase is constant, and the power transmission mechanism is the same as the first planetary gear mechanism. A second planetary gear mechanism arranged coaxially in series and having three rotating elements of a sun gear, a carrier, and a ring gear, and rotating elements of the first planetary gear mechanism and the second planetary gear mechanism corresponding to each other In one Has become integral rotation element rotating the sun gear of the second planetary gear mechanism, the carrier, a ring gear, the sun gear of the first planetary gear mechanism, the carrier is set to the ring gear and the number of teeth equal respectively, of the integral rotation element The speed transmission ratio of the power transmission mechanism, which is defined as the ratio of the rotation speed and the rotation speed of the first cam member , is the ratio of the rotation speed of the integral rotation element and the rotation speed of the second cam member. Is preferably set to a value equal to.

( 2 ) A second continuously variable transmission according to the present invention axially moves a primary pulley and a secondary pulley, a belt spanning both pulleys, and a movable sheave of at least one of the pulleys. And a mechanical pulley moving mechanism that adjusts a gear ratio by means of a mechanical pulley moving mechanism. The mechanical pulley moving mechanism is arranged in series on the same axis as the movable sheave by sliding their cam surfaces into contact with each other. And a first cam member, the first cam member is directly connected to the movable sheave, and the total length is changed when the relative rotation phase of the second cam member with respect to the first cam member is changed. Is changed to move the movable sheave in the axial direction, a torque cam mechanism that changes or maintains the relative rotation phase of the second cam member, and three rotations of a sun gear, a carrier, and a ring gear. 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 connected to the second cam member. A first planetary gear mechanism in which the remaining rotary elements are connected to the actuator, and the power transmission mechanism uses the actuator to shift the relative rotational phase of the first and second cam members to be constant. When the ratio is fixed, the speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction, and the power transmission mechanism is arranged coaxially with the first planetary gear mechanism in series. , A sun gear, a carrier, and a ring gear, and a second planetary gear mechanism having three rotating elements, and the rotating elements corresponding to each other of the first planetary gear mechanism and the second planetary gear mechanism are integrally rotated. Become an element Cage, the sun gear of the second planetary gear mechanism, the carrier, a ring gear, the sun gear of the first planetary gear mechanism, the carrier is set to a different number of teeth, respectively and the ring gear, wherein the rotational speed of the integrated rotation element first cam The speed transmission ratio of the power transmission mechanism, which is defined as the ratio of the rotational speed of the member , is set to a value different from the ratio of the rotational speed of the integral rotating element and the rotational speed of the second cam member . It is preferable.
( 3 ) A third continuously variable transmission according to the present invention axially moves a primary pulley and a secondary pulley, a belt spanned by the pulleys, and a movable sheave of at least one of the pulleys. And a mechanical pulley moving mechanism that adjusts a gear ratio by means of a mechanical pulley moving mechanism. The mechanical pulley moving mechanism is arranged in series on the same axis as the movable sheave by sliding their cam surfaces into contact with each other. And a first cam member, the first cam member is directly connected to the movable sheave, and the total length is changed when the relative rotation phase of the second cam member with respect to the first cam member is changed. Is changed to move the movable sheave in the axial direction, a torque cam mechanism that changes or maintains the relative rotation phase of the second cam member, and three rotations of a sun gear, a carrier, and a ring gear. 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 connected to the second cam member. A first planetary gear mechanism in which the remaining rotary elements are connected to the actuator, and the power transmission mechanism uses the actuator to shift the relative rotational phase of the first and second cam members to be constant. When the ratio is fixed, the speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction, and the power transmission mechanism is arranged coaxially with the first planetary gear mechanism in series. , A sun gear, a carrier, and a ring gear, and a second planetary gear mechanism having three rotating elements, and the rotating elements corresponding to each other of the first planetary gear mechanism and the second planetary gear mechanism are integrally rotated. Become an element 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 rotation axis of the movable sheave, a first counter gear and a second counter gear connected to the counter shaft, and connected to the first cam member and meshed with the first counter gear. It is preferable that the parallel gear mechanism includes a first external gear and a second external gear that is coupled to the carrier and meshes with the second counter gear.
( 4 ) A fourth continuously variable transmission according to the present invention axially moves a primary pulley and a secondary pulley, a belt spanning the pulleys, and a movable sheave of at least one of the pulleys. And a mechanical pulley moving mechanism that adjusts a gear ratio by means of a mechanical pulley moving mechanism. The mechanical pulley moving mechanism is arranged in series on the same axis as the movable sheave by sliding their cam surfaces into contact with each other. And a first cam member, the first cam member is directly connected to the movable sheave, and the total length is changed when the relative rotation phase of the second cam member with respect to the first cam member is changed. Is changed to move the movable sheave in the axial direction, a torque cam mechanism that changes or maintains the relative rotation phase of the second cam member, and three rotations of a sun gear, a carrier, and a ring gear. 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 connected to the second cam member. A first planetary gear mechanism in which the remaining rotary elements are connected to the actuator, and the power transmission mechanism uses the actuator to shift the relative rotational phase of the first and second cam members to be constant. When the ratio is fixed, the speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction, and the power transmission mechanism is arranged coaxially with the first planetary gear mechanism in series. , A sun gear, a carrier, and a ring gear, and a second planetary gear mechanism having three rotating elements, and the rotating elements corresponding to each other of the first planetary gear mechanism and the second planetary gear mechanism are integrally rotated. Become an element Cage, wherein the first planetary gear mechanism, the disposed parallel rotation axis and the rotation axis of the movable sheave in the first planetary gear mechanism, the sun gear is coupled to the actuator, the ring gear is the second The carrier is drivingly connected to the power transmission mechanism, and the power transmission mechanism is coupled to the cam member, and the power transmission mechanism is coupled to the first cam member, and is meshed with the outer gear coupled to the carrier. It is preferable that the counter gear is a parallel gear mechanism.
( 5 ) A fifth continuously variable transmission according to the present invention axially moves a primary pulley and a secondary pulley, a belt spanning the pulleys, and a movable sheave of at least one of the pulleys. And a mechanical pulley moving mechanism that adjusts a gear ratio by means of a mechanical pulley moving mechanism. The mechanical pulley moving mechanism is arranged in series on the same axis as the movable sheave by sliding their cam surfaces into contact with each other. And a first cam member, the first cam member is directly connected to the movable sheave, and the total length is changed when the relative rotation phase of the second cam member with respect to the first cam member is changed. Is changed to move the movable sheave in the axial direction, an actuator that changes or maintains the relative rotation phase of the second cam member, and three rotations of a sun gear, a carrier, and a ring gear. 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 connected to the second cam member. A first planetary gear mechanism in which the remaining rotary elements are connected to the actuator, and the power transmission mechanism uses the actuator to shift the relative rotational phase of the first and second cam members to be constant. When the ratio is fixed, the speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction, and the power transmission mechanism is arranged coaxially with the first planetary gear mechanism in series. , A sun gear, a carrier, and a ring gear, and a second planetary gear mechanism having three rotating elements, and the rotating elements corresponding to each other of the first planetary gear mechanism and the second planetary gear mechanism are integrally rotated. Become an element Cage, wherein the first planetary gear mechanism, the disposed parallel rotation axis and the rotation axis of the movable sheave in the first planetary gear mechanism, the sun gear is coupled to the actuator, the ring gear is the second The carrier is drivingly connected to the power transmission mechanism, and the power transmission mechanism is coaxially arranged in series with the first planetary gear mechanism and includes three rotating elements of a sun gear, a carrier, and a ring gear. A second planetary gear mechanism that has, a first external gear that is integrally provided on the outer periphery of the ring gear of the second planetary gear mechanism, and an outer that is coupled to the first cam member and meshes with the first external gear. And a tooth gear.

( 6 ) It is preferable that a slide allowance mechanism that allows the axial movement of the first cam member and transmits the rotation is interposed between the power transmission mechanism and the first cam member. .

  According to the present invention, when the relative rotation phases of the first and second cam members are made constant by the actuator, the total length of the torque cam mechanism is maintained at a constant value according to the relative rotation phases of the first and second cam members. Power is transmitted between the primary pulley and the secondary pulley at a fixed gear ratio corresponding to this. Since the first cam member is directly connected to the movable sheave, friction due to rotation does not occur between the first cam member and the pulley, and the first and second cam members also rotate at the same speed in the same direction. Since there is no relative rotation, friction due to rotation does not occur. Therefore, the occurrence 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 overall 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 to this. . When the relative rotation phase is changed, the first cam member and the second cam member rotate relative to each other, but the speed change is short and the speed of this relative rotation is low, so friction occurs due to relative rotation. It can be suppressed to a slight amount.

It is a typical block diagram of the continuously variable transmission which concerns on each embodiment of this invention. It is a typical block diagram of the pulley which concerns on each embodiment of this 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. FIG. 3 is a velocity diagram (collinear chart) 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 2nd Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 3rd Embodiment of this 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 which concerns on 4th Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 5th Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 6th Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 7th Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 8th Embodiment of this 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 chart) of the planetary gear mechanism of the mechanical pulley moving mechanism which concerns on 9th Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the embodiments described below are merely examples, and there is no intention to exclude various modifications and application of techniques that are not explicitly shown in the following embodiments. The configurations of the following embodiments can be variously modified and implemented without departing from the spirit thereof, and can be appropriately selected or combined as needed.

[Castless 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 including an internal combustion engine, an electric motor, and the like for running a vehicle is provided with a continuously variable transmission 5 through a forward / reverse switching mechanism 4 including a planetary gear mechanism and the like. A rotary shaft 10 connected to a fixed sheave 8 of the primary pulley 6 is connected. A movable sheave 12 having a sheave surface that faces the sheave surface of the fixed sheave 8 and forms the V-shaped groove of the pulley is disposed on the rotary shaft 10 so as to be slidable in the axial direction and not relatively rotatable. There is.

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

Further, between the sheaves 16 and 20 of the secondary pulley 14, a spring 22 and a cam mechanism 24, which 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 adjusting mechanism that adjusts the thrust of the secondary pulley 14 to adjust the clamping force of the belt 26.

  It should be noted that FIG. 1 shows the primary pulley 6, the secondary pulley 14, and the belt 26 in a state in which the gear ratio is on the low side and on the high side. The outer half of each of the primary pulley 6 and the secondary pulley 14 shows the low-side state, and the inner half of each shows the high-side state. Regarding the belt 26, the low side state is shown by a solid line, and the high side state is shown 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 for adjusting the gear ratio by moving the movable sheave 12 in the axial direction is disposed on the rear surface (the surface opposite to the sheave surface) 13 side of the movable sheave 12 of the primary pulley 6. . In FIG. 1, the mechanical pulley moving mechanism 30 is illustrated 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 gear mechanism). A planetary gear mechanism or other gear mechanism) 60 and an electric motor 70 as an actuator are provided.

[Mechanical pulley moving mechanism according to each embodiment]
As shown in FIG. 2, the torque cam mechanism 40 is directly connected to the movable sheave 12 (fixedly fixed so as to be incapable of relative rotation and axially immovable) and rotates integrally with the movable sheave 12 (first cam). Cam member 42 and a second cam surface 44a facing the first cam surface 42a formed on the first cam 42 are formed at one end (left in the drawing) and the other end (right in the drawing) is a thrust bearing. The rotary shaft 10 is provided with a second cam (second cam member) 44 whose axial position is regulated via 46.

  The first cam 42 and the second cam 44 are arranged on the outer peripheral side of the rotary shaft 10 coaxially with the shaft center of the rotary shaft 10 (same shaft center). 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 has a structure similar to that of the movable sheave 12 (a spline mechanism in which balls or rollers are interposed) to the rotating shaft 10 and is supported so as not to be rotatable and movable in the axial direction. Has been done. The second cam 44 is supported so as to be rotatable relative to the rotating shaft 10 via a bearing or the like (not shown), and is axially immovable so as to maintain a fixed position with respect to the rotating 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 to be immovable in the axial direction with respect to the rotating shaft 10, so that the cams 42, 44 are relatively opposed to each other. It is possible to move the movable sheave 12 in the axial direction (change the gear ratio) by the displacement of the rotation phase.

  The first cam surface 42a and the second cam surface 44a are formed on end surfaces of the cylindrical cams 42, 44 that face each other, and are arranged so as to be in sliding contact with each other. The cam surfaces 42a, 44a are formed in a spiral slope inclined with respect to the axis SC of the rotary shaft 10. In each embodiment, this slope (that is, the first and second cam surfaces 42a, 44a) is inclined so as to approach the back surface 13 of the movable sheave 12 along the rotation 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 second cam 44 is rotated relative to the first cam 42 to change the relative rotation phase, the movable sheave 12 moves in the axial direction, and the gear ratio of the continuously variable transmission 5 is adjusted.

  In addition, between the first cam 42 and the power transmission mechanism 60, a slide permitting mechanism (ball or roller) for permitting relative movement along the axial direction of both and for making relative rotation impossible (rotational power can be transmitted). A spline mechanism or the like 80, etc. is interposed. When the gears of the planetary gear mechanism 50, the power transmission mechanism 60, etc. are helical gears, the slide allowance mechanism 80 cannot perform relative movement in the axial direction between the gears. It is necessary to allow relative movement between the power transmission mechanism 60 and the first cam 42. However, if either or both of the planetary gear mechanism 50 and the power transmission mechanism 60 are configured by spur gears, relative movement between the spur gears is possible, and thus the slide allowance mechanism 80 can be omitted. .

The first planetary gear mechanism 50 is arranged on the outer circumference of the second cam 44, and has _one of the three rotation elements (first rotation element) of the sun gear S ₁ , the carrier C ₁ , and the ring gear R ₁ as a rotation element (first rotation element). The first cam 42 is connected 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 element) is connected to the second cam 44, The remaining rotary element (third rotary element) is connected to the electric motor 70 as an actuator.

  In addition, in the following first to fourth, eighth, and ninth embodiments, the second planetary gear mechanism 60 is exemplified as the power transmission mechanism, but 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. Further, although an electric motor is suitable as the actuator, it is not limited to the electric motor as long as the controllability required as the actuator can be secured.

The first planetary gear mechanism 50 restrains the rotation of any one of the three rotating elements (the sun gear S ₁ , the carrier C ₁ , and the ring gear R ₁ ) to rotate one of the remaining two rotating elements. The element serves as a reaction force element, and the other rotary element rotates at a gear ratio (= output rotation speed / input rotation speed, also referred to as a speed ratio) according to the gear ratio. The constraint of rotation in this case means that the rotation speed is set to a predetermined speed (constant speed, including rotation stop). The rotation is restrained 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 corresponding to the gear ratio.

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

  When the rotation restraint state of the third rotating element by the actuator 70 is changed, that is, the rotation speed of the third rotating element is changed (if the third rotating element is in a stopped state, it is rotated, or the third rotating element has a predetermined rotating speed). In this case, the rotation speed does not change because the first cam 42 is directly connected to the movable pulley 12, and therefore the rotation speed does not change between the first cam 42 and the second cam 44. The differential rotation occurs, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase between the first cam 42 and the second cam 44 is changed. As a result, 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 with reference to the first to fourth, eighth, and ninth embodiments. .
Incidentally, 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 Are indicated by R ₁ and the second planetary gear mechanisms 60A to 60D, 60H, 60I are indicated by S ₂ for the sun gear, C ₂ for the carrier, P ₂ for the planetary gear, and R ₂ for the ring gear. The rotating elements do not necessarily have to have the same standard between the respective embodiments, and have the standard (for example, the number of teeth and the tooth width of the gear) required in the configuration of each embodiment.
In addition, in the drawings (FIGS. 3, 6, 8, 10, 12, 14, 16, 18) showing the configurations of the respective embodiments, the second planetary gear mechanism 60 and the first cam 42 are interposed in the connecting portion. The slide allowance mechanism 80 is omitted (not shown).

[First Embodiment]
As shown in FIG. 3, in the mechanical pulley moving mechanism 30A according to the first embodiment, in the first planetary gear mechanism 50A, the carrier C ₁ corresponds to the first rotating element and is the power transmission mechanism. It is connected to the first cam 42 via the 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 corresponds to the third rotating element, and the electric motor 70, which is an actuator, has an external gear 71 a formed on the outer periphery of the ring gear R ₁ and a gear 71 b fixed to the rotating shaft of the electric motor 70 mesh with each other. Is connected to the first planetary gear mechanism 50A via the gear mechanism 71.

Regarding 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, the sun gear S ₂ is connected to the first cam 42, and the ring gear R ₂ is fixed to a transmission casing (not shown). Has been done. 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.

Further, 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 speed transmission ratio by the second planetary gear mechanism 60A, which is the power transmission mechanism, is obtained by comparing the rotation speed N _C2 of the carrier C _{2 and} the rotation speed of the first cam 42 (that is, the rotation speed of the sun gear S ₂ ) that are the integral rotation elements. Defined as the ratio N _S2 . Since the ring gear R _{1 of} the second planetary gear mechanism 60A is in the fixed state, the collinear diagram (velocity diagram) thereof is as shown by the solid line L in FIG.
In addition, in FIG. 4, FIG. 5, FIG. 7, FIG. 9, FIG. 11, FIG. 13, FIG. 17, FIG. 19 according to other embodiments described later, the vertical axis represents the rotation speed, and in the drawings, the rotation speed 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.

Here, the speed transmission ratio is a ratio of the rotation speed N _S2 of the sun gear S ₂ that rotates integrally with the second cam 44 to the rotation speed N _C2 of the carrier C ₂ of the second planetary gear mechanism 60A that is an integral rotation element. Specified as N _S2 / N _C2 . This ratio N _S2 / N _C2 is equal to (1 + α ₂ ) / α ₂ .

When the rotation speed of the electric motor 70 is maintained at zero and the ring gear R ₁ of the first planetary gear mechanism 50A is fixed, the sun gear S ₁ of the first planetary gear mechanism 50A rotates integrally with the first cam 42. It rotates at the same speed as the sun gear S ₂ of the 2nd planetary gear mechanism 60A. The collinear diagram of the first planetary gear mechanism 50A at this time is shown by a solid line L in FIG. 4 similarly to the second planetary gear mechanism 60A, and the sun gear S ₁ of the first planetary gear mechanism 50A is the second planetary gear mechanism. It rotates at a constant speed with the sun gear S _{2 of} 60A.

Therefore, at this time, the second cam 44 to which the sun gear S ₁ is connected does not rotate relative to the first cam 42 to which the sun gear S ₂ is connected, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio remains constant.
Further, 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 ), so the above-mentioned sun gear S ₂ and the carrier C ₂ are The speed transmission ratio N _S2 / N _C2 , which is the rotation speed ratio of the sun gear S ₁ that rotates integrally with the second cam 44 and the rotation speed N _S1 that rotates integrally with the second cam 44 in the fixed gear ratio state in which the gear ratio remains constant. 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 that is an element.

On the other hand, when the electric motor 70 is rotated in the same direction (forward direction) as the carriers C ₁ and C ₂ (see the arrow of the speed change a), the collinear diagram of the first planetary gear mechanism 50A is shown by the broken line in FIG. As indicated by La, the sun gear S ₁ of the first planetary gear mechanism 50A becomes slower than the sun gear S ₂ of the second planetary gear mechanism 60A. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

On the contrary, 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 shift b), the alignment chart of the first planetary gear mechanism 50A is shown in FIG. As indicated by the broken line Lb, the sun gear S ₁ of the first planetary gear mechanism 50A becomes faster than the sun gear S ₂ of the second planetary gear mechanism 60A. That is, the second cam 44 becomes faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

  Therefore, when the gear ratio is changed (that is, gear shift is performed), the electric motor 70 is rotated from zero rotation speed in a predetermined direction, and when the gear ratio is fixed, the rotation speed of the electric motor 70 is zero. maintain.

  The mechanical pulley moving mechanism 30A according to the present embodiment is configured as described above, and since the first cam 42 is directly connected to the movable sheave 12, there is no rotation between the first cam 42 and the pulley 6. Friction does not occur. Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  At the time of changing the gear ratio, the electric motor 70 is rotated in a predetermined direction to relatively rotate the second cam 44 with respect to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 are separated from each other. 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 drawing) via the first cam 42 is applied to the thrust bearing 46, and relative rotation occurs, but for a short time. In addition, since the speed of the relative rotation is low, the friction caused by the relative rotation is generated but is suppressed to a slight level.

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 on the outer periphery of the device, the structure can be simplified, which is advantageous in making the axial and radial sizes of the device 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 the control program of the electric motor 70.

Further, since the gears of the planetary gear mechanisms 50A and 60A are arranged on the outer periphery of the rotary shaft 10, the sun gears S ₁ and S ₂ have a relatively large diameter in the layout (that is, the number of teeth Zs is relatively large). In addition, each of the ring gears R ₁ and R ₂ can have a relatively small 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 value 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, in addition to the configuration of the first embodiment shown in FIG. 3, 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, respectively. However, the only difference is that different numbers of teeth are set. Since the other points are the same as the configuration of the first embodiment, the configuration and reference numerals of FIG. 3 will be used for description. That is, the numbers of teeth Zs ₁ and Zs ₂ of the sun gears S ₁ and S ₂ are set to Zs ₁ <Zs ₂ , and the numbers of teeth Zr ₁ and Zr ₂ of the ring gears R ₁ and R ₂ are set to Zr ₁ > Zr ₂ , respectively. There is.

Therefore, regarding the tooth number ratio α (= Zs / Zr) between the tooth number Zs of the sun gear and the tooth number Zr of the ring gear, the tooth number ratio α ₁ (= Zs ₁ / Zr ₁ ) of the first planetary gear mechanism 50 and the tooth number ratio α ₁ The two planetary gear mechanism 60A has a different tooth number ratio α ₂ (= Zs ₂ / Zr ₂ ), 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, which is the power transmission mechanism, is the rotation speed of the first cam 42 (that is, the rotation speed N _S2 of the sun gear S ₂ ) and the carrier C that is an integral rotation element. It is defined as the ratio N _S2 / N _C2 with the rotational speed N _{C2 of 2} . Since the ring gear R _{1 of} the second planetary gear mechanism 60A is in the fixed state, the alignment chart thereof is as shown by the solid line L in FIG. The ratio N _S2 / N _C2 between the rotation speed of the carrier C _{2 and} the rotation speed of the sun gear S ₂ , which is the speed transmission ratio, is equal to (1 + α ₂ ) / α ₂ .

On the other hand, since the tooth number ratios α ₁ and α ₂ are 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 line indicated by the solid line L in FIG. Rotating the sun gear S _{1 of} the first planetary gear mechanism 50A that integrally rotates with the second cam 44 and the sun gear S _{2 of} the second planetary gear mechanism 60A that integrally rotates with the first cam 42 at a constant speed. Can be made.

In the rotational speed state indicated by the black circles in FIG. 5, the electric motor 70 causes the ring gear R ₁ of the first planetary gear mechanism 50A to rotate in the same direction as the rotations of both carriers C ₁ and C ₂ (the same direction as the rotation of 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 ).

In addition, if the magnitude relationship between the tooth number ratios α ₁ and α ₂ is opposite (that is, α ₁ > α ₂ , the tooth number ratio α ₁ in this case is shown as α ₁ ′ in FIG. 5), the motor is driven. The motor 70 may rotate the ring gear R ₁ of the first planetary gear mechanism 50A in the opposite direction (negative direction) to the rotation of the carriers C ₁ and C _{2 at} the rotation speed indicated by the double circle in FIG. That is, when the tooth number ratio α ₁ of the first planetary gear mechanism 50 is larger than the tooth number ratio α ₂ of the second planetary gear mechanism 60A, as indicated by a chain double-dashed line on the extension line of the solid line L in FIG. The alignment chart is changed from the position of R1 to the position of R1 ′, and the sun gear S ₁ of the first planetary gear mechanism 50A that rotates integrally with the second cam 44 moves to the second position that rotates integrally with the first cam 42. In order to rotate the sun gear S ₂ of the planetary gear mechanism 60A at the same speed, the ring gear R ₁ of the first planetary gear mechanism 50A is doubled in the direction opposite to the rotation of both carriers C ₁ and C ₂ (negative direction) in FIG. It will be rotated at a predetermined speed indicated by a circle.

In other words, the gear ratio alpha _{1 <In} the case of the relationship of alpha _2, the ring gear R ₁ is rotated in the forward direction at a predetermined speed, gear ratio alpha _1> if the relationship alpha ₂ is the ring gear R ₁ Rotates in the negative direction at a predetermined speed.
Then, when the rotational speed of the electric motor 70 is increased from each state to increase the speed in the positive direction from each predetermined speed, the alignment chart of the first planetary gear mechanism 50A is as shown by the broken line La in FIG. Therefore, the sun gear S ₁ of the first planetary gear mechanism 50A becomes slower than the sun gear S ₂ of the second planetary gear mechanism 60A. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. After that, when the continuously variable transmission 5 has a desired gear ratio, the rotation speed of the electric motor 70 is set so that the ring gear R ₁ has a predetermined rotation speed indicated by a black circle.

On the contrary, when the gear ratio α ₁ <α ₂ , the ring gear R ₁ rotates in the positive direction, and when the gear ratio α ₁ > α ₂ , the ring gear R ₁ moves in the negative direction. When the rotation speed of the electric motor 70 is decelerated from the rotating state to increase the speed in the positive direction from each predetermined speed, a collinear diagram of the first planetary gear mechanism 50A is shown by a broken line Lb in FIG. Thus, the sun gear S ₁ of the first planetary gear mechanism 50A becomes faster than the sun gear S ₂ of the second planetary gear mechanism 60A. That is, the second cam 44 becomes faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. After that, when the continuously variable transmission 5 has a desired gear ratio, the rotation speed of the electric motor 70 is set so that the ring gear R ₁ has a predetermined rotation speed indicated by a black circle.

Therefore, when changing the gear ratio of the continuously variable transmission 5 (that is, changing gears), the rotation 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 (accelerated or decelerated), 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 the gap between the first cam 42 and the pulley 6 is the same as in the first embodiment. Does not generate friction due to rotation. Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

Further, as in the first embodiment, the ring gear R ₁ of the first planetary gear mechanism 50A is connected to the electric motor 70, and the ring gear R ₂ of the second planetary gear mechanism 60A is fixed to the transmission casing. The structure can be simply configured, which is advantageous in making the axial and radial sizes of the device compact.

Further, in the present embodiment, when the gear ratios α ₁ and α ₂ of the planetary gear mechanisms 50A and 60A are different (α ₁ ≠ α ₂ ) and the gear ratio is kept constant, the sun gears S _{1 and} S ₂ are kept. Is achieved by rotating the electric motor 70 at a predetermined speed so that the rotation speed of the ring gear R ₁ rotates at a constant speed. According to the 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, control in a region where the motor efficiency is low can be avoided.

  Further, as in the first embodiment, the gear ratio α is set to a value close to 1 in order to make the layout compact, so that the torque required for the electric motor 70 for changing the gear ratio is set. Can be suppressed.

[Third Embodiment]
As shown in FIG. 6, in the mechanical pulley moving mechanism 30C according to the third embodiment, in the first planetary gear mechanism 50C, the sun gear S ₁ corresponds to the first rotating element and is the power transmission mechanism. It is connected to the first cam 42 via the 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 It is connected to the first planetary gear mechanism 50C via a gear mechanism 73 in which the gear 73b meshes.

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 addition, 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 the power transmission mechanism, is the rotation speed of the first cam 42 (that is, the rotation speed N _R2 of the ring gear R ₂ ) and the rotation speed N of the sun gear S ₂ that is an integral rotation element. is defined as the ratio _N R2 _{/ N S2} and _S2. Since the carrier C _{2 of} the second planetary gear mechanism 60C is in the fixed state, the alignment chart thereof is as shown by the solid line L in FIG. 7. The ratio N _R2 / N _S2 between the rotation speed of the sun gear S _{2 and} the rotation 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 is fixed while maintaining the rotation speed of the electric motor 70 at zero, the ring gear R ₁ of the first planetary gear mechanism 50C rotates integrally with the first cam 42. It rotates at the same speed as the ring gear R _{2 of} the second planetary gear mechanism 60C. The collinear diagram of the first planetary gear mechanism 50C at this time is as shown by the solid line L in FIG. 7 similarly to the second planetary gear mechanism 60C, and the ring gear R ₁ of the first planetary gear mechanism 50C is the second planetary gear mechanism. It rotates at a constant speed with the ring gear R _{2 of} 60C.

Therefore, at this time, the second cam 44 to which the ring gear R ₁ is connected does not rotate relative to the first cam 42 to which the ring gear R ₂ is connected, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.
Further, 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 ), so that the ring gear R ₂ and the sun gear S ₂ are The transmission speed ratio N _R2 / N _S2 , which is the rotation speed ratio of the ring gear R ₁ that rotates integrally with the second cam 44 in the fixed gear ratio state in which the gear ratio remains constant, and the integral rotation element. It becomes a value equal to the ratio N _R1 / N _S1 (= −α ₂ ) of the rotation 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 (forward direction) as the ring gears R ₁ and R ₂ (see the arrow of the shift a), the collinear diagram of the first planetary gear mechanism 50C is shown by the broken line in FIG. As indicated by La, the ring gear R ₁ of the first planetary gear mechanism 50C becomes faster than the ring gear R ₂ of the second planetary gear mechanism 60C. That is, the second cam 44 becomes faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

On the contrary, 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 shift b), the alignment chart of the first planetary gear mechanism 50C is indicated by the broken line Lb in FIG. 7. As shown, the ring gear R ₁ of the first planetary gear mechanism 50C becomes slower than the ring gear R ₂ of the second planetary gear mechanism 60C. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

Therefore, the electric motor 70 is rotated in the positive direction or the negative direction when the gear ratio is changed (that is, the gear is changed), and the electric motor 70 is stopped when the gear ratio is fixed.
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 friction between the first cam 42 and the pulley 6 due to rotation does not occur. . Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

Further, as in 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 number of teeth is set to be the same, it is possible to simplify the overall configuration and the control program of 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, respectively, the first planetary gear mechanism 50C and the second planetary gear mechanism 50C The torque load on the planetary gear mechanism 60C is reduced, and the gear width of each of the planetary gear mechanisms 50C and 60C can be reduced.

[Fourth Embodiment]
As shown in FIG. 8, in the mechanical pulley movement mechanism 30D according to the fourth embodiment, in the first planetary gear mechanism 50D, the ring gear R ₁ corresponds to the first rotating element and is the power transmission mechanism. It is connected to the first cam 42 via the 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 rotating element, and the electric motor 70, which is an actuator, is meshed 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 fixed to the rotating shaft of the electric motor 70. The first planetary gear mechanism 50D is connected to the first planetary gear mechanism 50D via the 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.

Further, 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 that is the power transmission mechanism is determined by the rotation speed of the first cam 42 (that is, the rotation speed N _S2 of the sun gear S ₂ ) and the rotation speed N of the ring gear R ₂ that is an integral rotation element. is defined as the ratio _N S2 _{/ N R2} with _R2. Since the carrier C _{2 of} the second planetary gear mechanism 60D is in a fixed state, the alignment chart thereof is as shown by the solid line L in FIG. Is the transmission ratio, the ratio _N S2 _{/ N R2} between the rotational speed and the rotational speed of the sun gear _{S 2} of the ring gear _{R 2} is equal to -1 / alpha _2.

On the other hand, when the rotation of the electric motor 70 is stopped and the carrier C ₁ of the first planetary gear mechanism 50D is fixed, the sun gear S ₁ of the first planetary gear mechanism 50D rotates integrally with the first cam 42. It rotates at the same speed as the sun gear S ₂ of the planetary gear mechanism 60D. The collinear diagram of the first planetary gear mechanism 50D at this time is shown by a solid line L in FIG. 9 similarly to the second planetary gear mechanism 60D, and the sun gear S ₁ of the first planetary gear mechanism 50D is the second planetary gear mechanism. It rotates at the same speed as the 60D sun gear S ₂ .

Therefore, at this time, the second cam 44 to which the sun gear S ₁ is connected does not rotate relative to the first cam 42 to which the sun gear S ₂ is connected, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.
Further, 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 ), so that the sun gear S ₂ and the ring gear R ₂ are The speed transmission ratio N _S2 / N _R2 , which is the rotation speed ratio of the two gears of the planetary gears, is equal to α ₁ = α _2. Therefore, in the fixed gear ratio state where the gear ratio remains constant, A speed transmission ratio N _S1 / N _R1 (= rotation speed N _S1 of the sun gear S ₁ that rotates integrally with the second cam 44 and rotation speed N _R1 of the ring gear R ₁ of the first planetary gear mechanism 50D that is an integral rotation element. It becomes a value equal to −1 / α ₁ ).

On the other hand, when the electric motor 70 is rotated in the same direction (forward direction) as the sun gears S ₁ and S ₂ to increase the rotation speed of the carrier C ₁ (see the arrow of the shift a), the first planetary gear mechanism is generated. The alignment chart of 50D is shown by the broken line La in FIG. 9, and the sun gear S ₁ of the first planetary gear mechanism 50D becomes faster than the sun gear S ₂ of the second planetary gear mechanism 60D. That is, the second cam 44 becomes faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

On the contrary, 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 shift b), the alignment chart of the first planetary gear mechanism 50D is indicated by the broken line Lb in FIG. 9. As shown, the sun gear S ₁ of the first planetary gear mechanism 50D becomes slower than the sun gear S ₂ of the second planetary gear mechanism 60D. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

Therefore, the electric motor 70 is rotated in a predetermined direction when the gear ratio is changed (that is, the gear is changed), and the rotation speed of the electric motor 70 is set to zero when the gear ratio is fixed.
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 friction due to rotation does not occur between the first cam 42 and the pulley 6. . Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

Further, 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 number of teeth is set to be the same, it is possible to simplify the overall configuration and the control program of the electric motor 70.

[Fifth Embodiment]
As shown in FIG. 10, in the mechanical pulley moving mechanism 30E according to the fifth embodiment, in the first planetary gear mechanism 50E, the carrier C ₁ corresponds to the first rotating element and is 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 The gear 75b is connected to the first planetary gear mechanism 50E via a gear mechanism 75 formed by meshing with each other.

The power transmission mechanism 60E is composed of a parallel gear mechanism.
The parallel gear mechanism includes a counter shaft 61, a first gear mechanism formed by meshing a first external gear 61a and a first counter gear 61b, a second external gear 61d, and a second counter gear 61c. And a second gear mechanism formed by

That is, the counter shaft 61 is installed parallel to 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 integrally. 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 form a first gear mechanism. Further, the second external gear 61d is coupled to the carrier C ₁ of the first planetary gear mechanism 50E so as to rotate integrally, and the second external gear 61d and the second counter gear 61c mesh with each other to form a second gear. 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 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 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 the speed transmission ratio of the power transmission mechanism 60E to the rotation speed (Nc1) of the carrier C ₁ which is the first rotation element of the first planetary gear mechanism 50. It rotates at a rotation speed corresponding to (N _{cam 1} / Nc ₁ ).

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 When the number of teeth is Z _D , the speed transmission ratio by the parallel gear mechanism 60E, which is a power transmission mechanism, is the ratio of the rotation speed N _{A of} the first external gear 61a and the rotation speed N _{D of} the second external gear 61d ( 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 nomographic chart of the first planetary gear mechanism 50E is as shown by the solid line L in FIG. In FIG. 11, α is the tooth number ratio of the first planetary gear mechanism 50E.
When the gear ratio is fixed such that the relative rotation phase of the first cam 42 and the second cam 44 is constant, the speed transmission ratio of the parallel gear mechanism 60E is set so that the first cam 42 and the second cam 44 rotate at the same speed in the same direction. When N _A / N _D is set, the speed transmission ratio N _A / N _D becomes equal to (1 + α) / α, as shown in FIG.

When the rotation of the electric motor 70 is stopped and the ring gear R ₁ of the first planetary gear mechanism 50E is fixed, in the first planetary gear mechanism 50E, the sun gear S ₁ that rotates integrally with the second cam 44 is the carrier C _1. The rotation speed is (1 + α) / α times. At this time, the first external gear 61a that rotates integrally with the first cam 42 also rotates at (1 + α) / α times the speed of the second external gear 61d that rotates integrally with the carrier C ₁ .

Therefore, at this time, the second cam 44 to which the sun gear S ₁ is connected does not rotate relative to the first cam 42 to which the carrier C ₁ is connected, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.

On the other hand, when the electric motor 70 is operated so that the ring gear R ₁ rotates in the same direction (forward direction) as the carrier C ₁ and the sun gear S ₁ (see the arrow of the gear shift a), the first planetary gear mechanism 50E 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 becomes slower than before the electric motor 70 is actuated, The 2nd cam 44 rotates relative to the 1st cam 42, and a relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

On the contrary, when the electric motor 70 is operated so that the ring gear R ₁ rotates in the opposite direction (negative direction) to the carrier C ₁ and the sun gear S ₁ (see the arrow of the shift b), the first planetary gear mechanism 50E operates The diagram is as shown by the broken line Lb in FIG. 11, and the sun gear S ₁ (that is, the second cam 44) of the first planetary gear mechanism 50E becomes faster than before the operation of the electric motor 70, and the second cam Reference numeral 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

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

  In the mechanical pulley moving mechanism 30E according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and friction between the first cam 42 and the pulley 6 due to rotation does not occur. . Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight 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) and is parallel to the rotation axis of the first planetary gear mechanism 51. It is located on another axis of rotation.
In the first planetary gear mechanism 51, the sun gear S ₃ is coupled to the rotary shaft of the electric motor 70 as an actuator, the ring gear R ₃ is coupled to the second cam 44, and the carrier C ₃ is drivingly coupled to the power transmission mechanism 60F. ing.

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

The power transmission mechanism 60F is composed of 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 ,,.

The parallel gear mechanism 60F, which is a power transmission mechanism, allows the first cam 42 and the second cam 44 to operate 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 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 the speed transmission ratio of the power transmission mechanism 60F with respect to the rotation speed (Nc3) of the carrier C ₃ which is the first rotation element of the first planetary gear mechanism 51. It rotates at a rotation speed corresponding to (N _{cam 1} / Nc 3).

In the parallel gear mechanism 60F, if the number of teeth of the external gear 62a coupled to the first cam 42 is Z _B and the number of the external gear 62b coupled to the carrier C ₃ is Z _C , it is a power transmission mechanism. The speed transmission ratio by the parallel gear mechanism 60F is the ratio of the rotation speed of the external gear 62a (the rotation speed of the first cam 42) N _B to the rotation speed of the external gear 62b (the rotation speed of the carrier C ₃ ) N _C ( N _B / N _C ), which is determined by the number of teeth Z _B , Z _C of each gear 62a, 62b.
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 nomographic chart of the first planetary gear mechanism 51 is as shown by the solid line L in FIG. In FIG. 13, α is the tooth number ratio of the first planetary gear mechanism 51. As shown in FIG. 13, the ratio of the rotation speed of the ring gear R _{3 and} the rotation 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)} each gear 62a, 62b teeth _Z a of determined by _{Z R,} 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, set the speed transmission ratio of the parallel gear mechanism 60F (the ratio of the numbers of teeth Z _B and Z _C of the gears 62a and 62b) so as to satisfy 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 alignment 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 It does not rotate relative to the cam 42 and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.

On the other hand, when the electric motor 70 is operated so that the sun gear S ₃ rotates in the same direction (forward direction) as the carrier C ₃ and the ring gear R ₃ (see the arrow of the shift a), the first planetary gear mechanism 50F 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 becomes slower than before the electric motor 70 is rotated, The second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

On the contrary, when the electric motor 70 is operated so that the sun gear S ₃ rotates in the opposite direction (negative direction) to the carrier C ₃ or the ring gear R ₃ (see the arrow of the gear shift b), the first planetary gear mechanism 50F operates in common. The diagram is as shown 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 becomes faster than before the rotation operation of the electric motor 70 and becomes the second The cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

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

  In the mechanical pulley moving mechanism 30F according to the present embodiment, as described above, 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 connected to each other. Does not generate friction due to rotation. Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  Similarly to the first embodiment, when the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6), and the first cam 42 is rotated. And the relative rotational phase of the second cam 44 is changed. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

[Seventh Embodiment]
As shown in FIG. 14, in the mechanical pulley moving mechanism 30G according to the seventh embodiment, as with the sixth embodiment, the first planetary gear mechanism 51 has a rotation axis of the primary pulley 6 (movable sheave 12). It is spaced apart and arranged on another axis of rotation parallel to this axis of rotation, and is configured similarly to that of the sixth embodiment.
That is, in the first planetary gear mechanism 51, the sun gear S ₃ is coupled to the rotary shaft of the electric motor 70 as an actuator, the ring gear R ₃ is coupled to the second cam 44, and the carrier C ₃ is drive coupled to the power transmission mechanism 60G. Has been done.

The carrier C ₃ corresponds to the first rotating element and is connected to the first cam 42 via a power transmission mechanism 60G that is a power transmission mechanism. The ring gear R ₃ corresponds to the second rotating element, and has an external gear (also referred to as a gear R 1) 51 a formed outside the ring gear R ₃ and an external gear (gear R 2) formed outside the second cam 44. 51b also referred to as A). The sun gear S ₃ corresponds to the third rotating element and is coupled to the rotating shaft of the electric motor 70 that is an actuator.

  On the other hand, a planetary gear mechanism (second planetary gear mechanism) 63 is used for the power transmission mechanism 60G. The second planetary gear mechanism 63 is arranged 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 this rotation axis. It is composed of a rotary element similar to 51.

In other words, the second planetary gear mechanism 63 has the sun gear S ₄ arranged coaxially with the sun gear S _{3 of} the first planetary gear mechanism 51 and the 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. The carrier C ₄ has a planetary gear P ₃ 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. It is made up 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 causes the first cam 42 and the second cam 44 to move at the same speed in the same direction when the gear ratio is fixed by the electric motor 70, which is an actuator, so that the relative rotation phase of the first cam 42 and the second cam 44 is constant. The transmission ratio is set to rotate.

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

Here, the number of teeth of the external gear (gear A) 62a coupled to the second cam 44 is Z _A , the number of teeth of the external gear (gear R1) 51a formed outside the ring gear R ₃ is Z _R1 , Let Z _{R2 be} the number of teeth of the external gear (gear R2) 63b formed outside the ring gear R ₄ , and let Z _B be the number of teeth of the external gear (gear B) 62a coupled to the first cam 42. Assuming that the tooth number ratio (= Zs / Zr) of the planetary gear mechanism 51 is α ₁ and the tooth number ratio (= Zs / Zr) of the second planetary gear mechanism 63 is α ₂ , 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} / Nc 3) = (1 + α ₂ ) · (Z _R2 / Z _B ).
(N _cam 2 / Nc3) = (1 + α 1) · (Z R1 / Z A)

When the gear ratio is fixed such that the relative rotation phase of the first cam 42 and the second cam 44 is constant, the speed transmission ratio of the power transmission mechanism 60G (so that the first cam 42 and the second cam 44 rotate at the same speed in the same direction) ( To set N _{cam 1} / Nc 3), the speed transmission ratio (N _{cam 1} / Nc 3) and the speed transmission ratio (N _{cam 2} / Nc 3) may be set to be equal, as shown in the following equation. .
(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 as shown by the solid line L in FIG. In FIG. 15, α ₁ is the tooth number ratio of the first planetary gear mechanism 51, and α ₂ is the tooth number ratio of the second planetary gear mechanism 63. As shown in FIG. 15, the ratio between the rotation speeds of the ring gears R ₃ and R _{4 and} the rotation speeds 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 It does not rotate relative to the cam 42 and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.

On the other hand, when the electric motor 70 is operated so that the sun gear S ₃ rotates in the same direction (forward direction) as the carrier C ₃ and the ring gear R ₃ (see the arrow of the shift a), the first planetary gear mechanism 50F The collinear diagram of is as shown by the 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 slower than before the rotation operation of the electric motor 70, The second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

On the contrary, when the electric motor 70 is operated so that the sun gear S ₃ rotates in the opposite direction (negative direction) to the carrier C ₃ or the ring gear R ₃ (see the arrow of the gear shift b), the first planetary gear mechanism 50F operates in common. The diagram is as shown 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 becomes faster than before the rotation operation of the electric motor 70. The cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed.

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

  In the mechanical pulley moving mechanism 30G according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12 and the gap between the first cam 42 and the pulley 6 is the same as in the first embodiment. Does not generate friction due to rotation. Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  Similarly to the first embodiment, when the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6), and the first cam 42 is rotated. And the relative rotational phase of the second cam 44 is changed. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

[Eighth Embodiment]
As shown in FIG. 16, in the mechanical pulley movement mechanism 30H according to the eighth embodiment, in the first planetary gear mechanism 50H, the sun gear S ₁ corresponds to the first rotating element and is the power transmission mechanism. It is connected to the first cam 42 via the 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 It is connected to the first planetary gear mechanism 50H via a gear mechanism 76 in which the gear 76b meshes.

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 addition, 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 determined by the rotation speed of the first cam 42 (that is, the rotation speed N _C2 of the carrier C ₂ ) and the rotation speed N of the sun gear S ₂ that is an integral rotation element. is defined as the ratio _N C2 _{/ N S2} and _S2. Since the ring gear R _{2 of} the second planetary gear mechanism 60H is in the fixed state, the alignment chart thereof is as shown by the solid line L in FIG. The ratio N _C2 / N _S2 between the rotation speed of the sun gear S _{2 and} the rotation 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 rotation speed of the electric motor 70 is maintained at zero and the ring gear R ₁ of the first planetary gear mechanism 50H is fixed, the carrier C ₁ of the first planetary gear mechanism 50H rotates integrally with the first cam 42. It rotates at the same speed as the carrier C _{2 of} the second planetary gear mechanism 60H. The collinear diagram of the first planetary gear mechanism 50H at this time is as shown by the solid line L in FIG. 17 similarly to the second planetary gear mechanism 60H, and the carrier C ₁ of the first planetary gear mechanism 50H is the second planetary gear mechanism. It rotates at the same speed as the carrier C _{2 of} 60H.

Therefore, at this time, the second cam 44 to which the carrier C ₁ is coupled does not rotate relative to the first cam 42 to which the carrier C ₂ is coupled, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.
Further, 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 ), so that the ring gear R ₂ and the sun gear S ₂ are The speed transmission ratio N _R2 / N _S2 that is the rotation speed ratio of the carrier C ₁ that rotates integrally with the second cam 44 in the fixed speed ratio state in which the speed ratio remains constant, and The value is equal to the ratio N _C1 / N _S1 (= α ₂ / (1 + α ₂ )) of the rotation 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 shift a), the collinear diagram of the first planetary gear mechanism 50H is shown by the broken line in FIG. As indicated by La, the ring gear R ₁ of the first planetary gear mechanism 50H becomes faster than the ring gear R ₂ of the second planetary gear mechanism 60H. That is, the second cam 44 becomes faster than the first cam 42, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

On the contrary, 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 shift b), the collinear diagram of the first planetary gear mechanism 50H is indicated by the broken line Lb in FIG. As shown, the ring gear R ₁ of the first planetary gear mechanism 50H becomes slower than the ring gear R ₂ of the second planetary gear mechanism 60H. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

Therefore, the electric motor 70 is rotated in the positive direction or the negative direction when the gear ratio is changed (that is, the gear is changed), and the electric motor 70 is stopped when the gear ratio is fixed.
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 between the first cam 42 and the pulley 6 due to rotation does not occur. . Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

Further, 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 number of teeth is set to be the same, it is possible to simplify the overall configuration and the control program of the electric motor 70.

Further, the ring gear R ₁ of the first planetary gear mechanism 50H is connected to the electric motor 70, and the ring gear R ₂ of the second planetary gear mechanism 60H is fixed to the transmission casing. The ring gears R ₁ and R ₂ are the mechanism. Since the electric motor 70 and the transmission casing are easily accessible on the outer periphery of the device, the structure can be simplified, which is advantageous in making the axial and radial sizes of the device compact.

[Ninth Embodiment]
As shown in FIG. 18, in the mechanical pulley movement mechanism 30I according to the ninth embodiment, in the first planetary gear mechanism 50I, the ring gear R ₁ corresponds to the first rotating element and is the power transmission mechanism. Two
It is connected to the first cam 42 via the 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 The gear 77b is connected to the first planetary gear mechanism 50I via a gear mechanism 77 formed by meshing with each other.

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.

Further, 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, which is the power transmission mechanism, is the rotation speed of the first cam 42 (that is, the rotation speed N _C2 of the carrier C ₂ ) and the rotation speed N of the ring gear R ₂ that is an integral rotation element. is defined as the ratio _N C2 _{/ N R2} with _R2. In the second planetary gear mechanism 60I, since the sun gear S ₂ is in a fixed state, the alignment chart thereof is as shown by the solid line L in FIG. The ratio N _C2 / N _R2 between the rotation speed of the ring gear R _{2 and} the rotation 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 rotation speed of the electric motor 70 is maintained at zero and the sun gear S ₁ of the first planetary gear mechanism 50I is fixed, the carrier C ₁ of the first planetary gear mechanism 50I rotates integrally with the first cam 42. It rotates at the same speed as the carrier C _{2 of} the second planetary gear mechanism 60I. The collinear diagram of the first planetary gear mechanism 50I at this time is as shown by the solid line L in FIG. 19 similarly to the second planetary gear mechanism 60I, and the carrier C ₁ of the first planetary gear mechanism 50I is the second planetary gear mechanism. It rotates at the same speed as the carrier C _{2 of} 60I.

Therefore, at this time, the second cam 44 to which the carrier C ₁ is coupled does not rotate relative to the first cam 42 to which the carrier C ₂ is coupled, and maintains a constant rotation phase. That is, the total length of the torque cam mechanism 40 is not changed, and the gear ratio of the continuously variable transmission 5 is maintained constant.
Further, 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 ), so that the ring gear R ₂ and the sun gear S ₂ are The speed transmission ratio N _R2 / N _S2 that is the rotation speed ratio of the carrier C ₁ that rotates integrally with the second cam 44 in the fixed speed ratio state in which the speed ratio remains constant, and The value is equal to the ratio N _C1 / N _R1 (= 1 / (1 + α ₂ )) of the rotation 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 (forward direction) as the sun gears S ₁ and S ₂ (see the arrow of the gear shift a), the collinear diagram of the first planetary gear mechanism 50I is a broken line in FIG. As indicated by La, the sun gear S ₁ of the first planetary gear mechanism 50I becomes faster than the sun gear S ₂ of the second planetary gear mechanism 60I. That is, the second cam 44 to which the carrier C ₁ is connected becomes faster than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

On the contrary, 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 shift b), the collinear diagram of the first planetary gear mechanism 50I is the broken line Lb in FIG. As shown, the sun gear S ₁ of the first planetary gear mechanism 50I becomes slower than the sun gear S ₂ of the second planetary gear mechanism 60I. That is, the second cam 44 becomes slower than the first cam 42, the second cam 44 relatively rotates with respect to the first cam 42, and the relative rotation phase is changed. As a result, the total length of the torque cam mechanism 40 is changed and the gear ratio is changed. Then, when the continuously variable transmission 5 reaches a desired gear ratio, the rotation speed of the electric motor 70 is returned to zero.

Therefore, the electric motor 70 is rotated in the positive direction or the negative direction when the gear ratio is changed (that is, the gear is changed), and the electric motor 70 is stopped when the gear ratio is fixed.
In the mechanical pulley moving mechanism 30I according to the present embodiment, as described above, the first cam 42 is directly connected to the movable sheave 12, and friction between the first cam 42 and the pulley 6 due to rotation does not occur. . Further, when the 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. Therefore, the occurrence of power transmission loss is suppressed.

  When the gear ratio is changed, the rotation speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (hence, the pulley 6) so that the first cam 42 and the second cam 44 move. Change the relative rotation phase. At this time, the thrust bearing 46 receives the thrust of the belt 26 which the second cam 44 receives toward the other end side (right side in the drawing) via the first cam 42, and friction due to relative rotation is generated. As in the first embodiment, the gear shift is performed for a short time, and the speed of the relative rotation is low. Therefore, although the friction due to the relative rotation is generated, it is suppressed to a slight amount.

Further, 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 number of teeth is set to be the same, it is possible to simplify the overall configuration and the control program of the electric motor 70.

Furthermore, assuming that the torque (carrier torque) of the carrier C ₁ connected to the 1 + α ₂ second cam 44 is T _C1 , the torque of the sun gear S ₁ connected to the electric motor 70 (sun gear torque) T _S1 is α ₁ Is used, 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 tooth number ratio α ₁ . Therefore, the torque (= sun gear torque T _S1 ) input by the electric motor 70 from the sun gear S ₁ can be reduced regardless of the tooth number ratio α ₁ .

[Other]
In the above third, fourth, eighth and ninth embodiments, the sun gears S ₁ and S ₂ and the ring gears of the first planetary gear mechanism 50C, 50D, 50H and 50I and the second planetary gear mechanism 60C, 60D, 60H and 60I, respectively. R ₁ and R ₂ are set to have the same number of teeth, but as in the second embodiment, 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 are the same 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, since the electric motor 70 is controlled while rotating even when the gear ratio is fixed, it is possible to avoid control in a region where the motor efficiency is low.

  In the fifth to seventh embodiments described above, the gear ratio is set to be constant by setting the electric motor 70, which is an actuator, in a rotation stopped state at a rotation speed of zero. However, like the second embodiment, Even when the gear ratio is fixed, the electric motor 70 may be controlled while being rotated. In this case, control in a region where the motor efficiency is low can be avoided.

In each of the above embodiments, the carrier or the sun gear is used as the integral rotary element that rotates integrally with each other in the first planetary gear mechanism and the second planetary gear mechanism for the sake of structural ease. It may be a ring gear.
Further, 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 may be provided on both the primary pulley 6 and the secondary pulley 14.

2 drive source 5 continuously variable transmission 6 primary pulley 8 fixed sheave of primary pulley 6 10 rotary shaft of primary pulley 6 12 movable sheave of primary pulley 6 secondary pulley 16 fixed sheave of secondary pulley 14 18 drive shaft of secondary pulley 14 Movable sheave 22 of secondary pulley 14 Spring which constitutes thrust adjustment mechanism 24 Cam mechanism which constitutes thrust adjustment mechanism 26 Belt (endless belt-shaped member)
30, 30A to 30I Mechanical pulley moving mechanism 40 Torque cam mechanism 50, 50A to 50E, 50H, 50I, 51 First planetary gear mechanism 60, 60A to 60D, 60H, 60I Second planetary gear mechanism 60E to as power transmission mechanism 60G Power transmission mechanism 63 Second planetary gear mechanism 70 Electric motor as actuator 80 Slide allowance mechanism S _{1 to} S ₄ Sun gear C _{1 to} C ₄ Carrier R _{1 to} R ₄ Ring gear P _{1 to} P ₄ Planetary gear

Claims (6)

A primary pulley and a secondary pulley; a belt spanning the pulleys; and a mechanical pulley moving mechanism that axially moves a movable sheave of at least one of the pulleys to adjust a gear ratio. In a continuously variable transmission,
The mechanical pulley moving mechanism,
The first and second cam members are arranged in series coaxially with the movable sheave so that their cam surfaces are in sliding contact with each other, and the first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. A torque cam mechanism for moving the movable sheave in the axial direction by changing the relative rotation phase of the cam member with respect to the first cam member.
An actuator for changing or keeping the relative rotation phase of the second cam member constant;
It has three rotating elements of a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member through a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism connected to the second cam member, and the remaining rotating elements connected 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 by the actuator so that the relative rotation phases of the first and second cam members are constant. The transmission ratio is set ,
The power transmission mechanism includes a second planetary gear mechanism that is arranged coaxially in series with the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the second planetary gear mechanism. The rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements that integrally rotate,
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.
The speed transmission ratio of the power transmission mechanism, which is defined as the ratio of the rotation speed of the integral rotation element and the rotation speed of the first cam member, is equal to the rotation speed of the integral rotation element and that of the second cam member. A continuously variable transmission characterized by being set to a value equal to a ratio with a rotation speed . A primary pulley and a secondary pulley; a belt spanning the pulleys; and a mechanical pulley moving mechanism that axially moves a movable sheave of at least one of the pulleys to adjust a gear ratio. In a continuously variable transmission,
The mechanical pulley moving mechanism,
The first and second cam members are arranged in series coaxially with the movable sheave so that their cam surfaces are in sliding contact with each other, and the first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. A torque cam mechanism for moving the movable sheave in the axial direction by changing the relative rotation phase of the cam member with respect to the first cam member.
An actuator for changing or keeping the relative rotation phase of the second cam member constant;
It has three rotating elements of a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member through a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism connected to the second cam member, and the remaining rotating elements connected 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 by the actuator so that the relative rotation phases of the first and second cam members are constant. The transmission ratio is set ,
The power transmission mechanism includes a second planetary gear mechanism that is arranged coaxially in series with the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the second planetary gear mechanism. The rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements that integrally rotate,
The sun gear, carrier, and ring gear of the second planetary gear mechanism are set to have different numbers of teeth from the sun gear, carrier, and ring gear of the first planetary gear mechanism, respectively.
The speed transmission ratio of the power transmission mechanism, which is defined as the ratio of the rotation speed of the integral rotation element and the rotation speed of the first cam member, is equal to the rotation speed of the integral rotation element and that of the second cam member. A continuously variable transmission characterized by being set to a value different from a ratio with a rotation speed . A primary pulley and a secondary pulley; a belt spanning the pulleys; and a mechanical pulley moving mechanism that axially moves a movable sheave of at least one of the pulleys to adjust a gear ratio. In a continuously variable transmission,
The mechanical pulley moving mechanism,
The first and second cam members are arranged in series coaxially with the movable sheave so that their cam surfaces are in sliding contact with each other, and the first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. A torque cam mechanism for moving the movable sheave in the axial direction by changing the relative rotation phase of the cam member with respect to the first cam member.
An actuator for changing or keeping the relative rotation phase of the second cam member constant;
It has three rotating elements of a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member through a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism connected to the second cam member, and the remaining rotating elements connected 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 by the actuator so that the relative rotation phases of the first and second cam members are constant. The transmission ratio is set ,
The power transmission mechanism includes a second planetary gear mechanism that is arranged coaxially in series with the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the second planetary gear mechanism. The rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements that integrally rotate,
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 includes a counter shaft installed parallel to the rotation axis of the movable sheave, first and second counter gears connected to the counter shaft, and the first cam member connected to the first cam member. A parallel gear mechanism including 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. And continuously variable transmission. A primary pulley and a secondary pulley; a belt spanning the pulleys; and a mechanical pulley moving mechanism that axially moves a movable sheave of at least one of the pulleys to adjust a gear ratio. In a continuously variable transmission,
The mechanical pulley moving mechanism,
The first and second cam members are arranged in series coaxially with the movable sheave so that their cam surfaces are in sliding contact with each other, and the first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. A torque cam mechanism for moving the movable sheave in the axial direction by changing the relative rotation phase of the cam member with respect to the first cam member.
An actuator for changing or keeping the relative rotation phase of the second cam member constant;
It has three rotating elements of a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member through a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism connected to the second cam member, and the remaining rotating elements connected 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 by the actuator so that the relative rotation phases of the first and second cam members are constant. The transmission ratio is set ,
The power transmission mechanism includes a second planetary gear mechanism that is arranged coaxially in series with the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the second planetary gear mechanism. The rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements that integrally rotate,
The first planetary gear mechanism is arranged 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, 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 configured by a parallel gear mechanism including an external gear that is coupled to the first cam member and a counter gear that is coupled to the carrier and meshes with the external gear. > A continuously variable transmission characterized by the following. A primary pulley and a secondary pulley; a belt spanning the pulleys; and a mechanical pulley moving mechanism that axially moves a movable sheave of at least one of the pulleys to adjust a gear ratio. In a continuously variable transmission,
The mechanical pulley moving mechanism,
The first and second cam members are arranged in series coaxially with the movable sheave so that their cam surfaces are in sliding contact with each other, and the first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. A torque cam mechanism for moving the movable sheave in the axial direction by changing the relative rotation phase of the cam member with respect to the first cam member.
An actuator for changing or keeping the relative rotation phase of the second cam member constant;
It has three rotating elements of a sun gear, a carrier, and a ring gear, and any one of these rotating elements is connected to the first cam member through a power transmission mechanism, and any one of the remaining rotating elements is A first planetary gear mechanism connected to the second cam member, and the remaining rotating elements connected 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 by the actuator so that the relative rotation phases of the first and second cam members are constant. The transmission ratio is set ,
The power transmission mechanism includes a second planetary gear mechanism that is arranged coaxially in series with the first planetary gear mechanism and has three rotating elements of a sun gear, a carrier, and a ring gear, and the first planetary gear mechanism and the second planetary gear mechanism. The rotating elements corresponding to each other with the second planetary gear mechanism are integrally rotating elements that integrally rotate,
The first planetary gear mechanism is arranged 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, 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 coaxially arranged in series with the first planetary gear mechanism, and has a second planetary gear mechanism having three rotating elements of a sun gear, a carrier, and a ring gear, and an outer circumference of a ring gear of the second planetary gear mechanism. A first externally toothed gear integrally provided with the first cam gear, and an externally toothed gear that is coupled to the first cam member and meshes with the first externally toothed gear. , Continuously variable transmission. A slide permitting mechanism that allows axial movement and transmits rotation of the first cam member is interposed between the power transmission mechanism and the first cam member . continuously variable transmission according to any one of claims 1-5.

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