JP2019015305A - Pulley device for stepless transmission, stepless transmission and stepless transmission device - Google Patents

Abstract

To suppress occurrence of a power transmission loss by making compact a pulley device for stepless transmission comprising a mechanical pulley moving mechanism for adjusting a change gear ratio by axially moving a movable sheave.SOLUTION: A mechanical pulley moving mechanism comprises: a torque cam mechanism 40 which includes cam members 42 and 44 on a pulley shaft 10, in which the cam member 42 is directly connected to a movable sheave 12 and the cam member 44 is connected to the pulley shaft 10 in relatively rotatable and axially relatively non-movable manners and, when relative rotation phase of both the cam members are changed, which axially moves the movable sheave by changing a full length; an actuator 70 which changes or fixes the relative rotation phases; and first and second planetary gear mechanisms 50 and 60. Carriers of both the planetary gear mechanisms are coupled with each other. A sun gear of the planetary gear mechanism 60 is directly connected to the cam member 42, and a sun gear of the planetary gear mechanism 50 is directly connected to the cam member 44. A ring gear of the planetary gear mechanism 60 is fixed, and a ring gear of the planetary gear mechanism 50 is connected to the actuator 70 in a drivable manner.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a continuously variable transmission pulley device, a continuously variable transmission including the pulley device, and a continuously variable transmission device.

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

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

Japanese Patent Laid-Open No. 2006-1013

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

  The present invention was devised in view of such problems, and in a continuously variable transmission in which a movable sheave is moved in an axial direction using a mechanical actuator, the pulley rotation can be performed while allowing space-efficient installation. It is an object of the present invention to provide a continuously variable transmission pulley device, a continuously variable transmission, and a continuously variable transmission device capable of reducing the friction of the motor and suppressing the occurrence of power transmission loss.

  (1) A pulley device for a continuously variable transmission according to the present invention is applied to either of the pulleys of a continuously variable transmission including a primary pulley and a secondary pulley and a belt spanned between the pulleys, and is movable. A pulley device for a continuously variable transmission having a mechanical pulley moving mechanism that adjusts a gear ratio by moving a sheave in an axial direction, wherein the mechanical pulley moving mechanism is slidably contacted with each other to fix the fixed The first cam member is directly connected to the movable sheave, and the second cam member is connected to the movable sheave. When the relative rotation phase of the second cam member with respect to the first cam member is changed, the overall length is changed so that the movable sheave is axially moved. And move to A torque cam mechanism that adjusts the speed, and the relative rotation phase of the second cam member is changed at the time of shifting, and the first cam member and the second cam member are rotated at the same speed in the same direction when the speed ratio is fixed. Thus, the first planetary gear mechanism includes: an actuator that makes the relative rotational phase constant; and a first planetary gear mechanism and a second planetary gear mechanism each having rotational elements such as a sun gear, a carrier, and a ring gear. And the second planetary gear mechanism is disposed coaxially with the pulley shaft, the first rotating elements of the first and second planetary gear mechanisms are coupled to each other, and the first planetary gear mechanism The second rotating element is directly connected to the first cam member, the second rotating element of the second planetary gear mechanism is directly connected to the second cam member, and the third planetary gear mechanism is third. The rotating element is fixed , The third rotating element of the second planetary gear mechanism is characterized by being drivingly connected to said actuator.

  (2) Preferably, the first rotating element is a carrier, the second rotating element is a sun gear, and the third rotating element is a ring gear.

  (3) It is also preferable that the first rotating element is a ring gear, the second rotating element is a sun gear, and the third rotating element is a carrier.

  (4) The movable sheave is disposed on one side in the axial direction of the pulley shaft across the belt, the fixed sheave is disposed on the other side in the axial direction, and the first cam member is The first planetary gear mechanism is disposed on the outer periphery of the first cam member, and the second cam member is disposed on the one-direction side with respect to the first cam member. And the second planetary gear mechanism is arranged on the outer periphery of the second cam member, and the actuator is arranged in the other direction with respect to the second planetary gear mechanism. It is preferable to arrange on the side.

  (5) The continuously variable transmission of the present invention includes a continuously variable transmission including a primary pulley and a secondary pulley and a belt spanned between the pulleys, and the primary pulley includes the above-described (1) to (4). The pulley device for a continuously variable transmission according to any one of the above is provided.

  (6) A continuously variable transmission device according to the present invention includes a continuously variable transmission described in (5) above, a differential device provided with a final gear, a pulley shaft of the secondary pulley of the continuously variable transmission, A transmission device having an idler gear for drivingly connecting to the differential device, and a transmission device installed in the vehicle, wherein the pulley shaft of the primary pulley is a first shaft when installed in the vehicle. The differential shaft, the pulley shaft of the secondary pulley is on the second axis above the rear portion of the first axis, and the idler gear shaft of the power transmission gear mechanism is on the third axis below the rear portion of the second axis. Are arranged on a fourth axis below the third axis, and the output shaft of the actuator of the pulley device for continuously variable transmission is the first axis. It is arranged above the line and on the fifth axis in the region opposite to the third axis and the fourth axis with respect to the line connecting the first axis and the second axis. It is characterized by.

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

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

  Further, the first rotating elements of the first and second planetary gear mechanisms are coupled to each other, and the second rotating element of the first planetary gear mechanism is directly connected to the first cam member, so that the second planetary gear mechanism is The second rotating element is directly connected to the second cam member, the third rotating element of the first planetary gear mechanism is fixed, and the third rotating element of the second planetary gear mechanism is drivingly connected to the actuator. Therefore, if the actuator is stopped, the relative rotational phase of the second cam member with respect to the first cam member can be made constant.

  Further, a first planetary gear mechanism and a second planetary gear mechanism each having the same number of rotation elements of the sun gear, the carrier, and the ring gear are arranged in series on the same axis as the pulley shaft, and the relative rotational phase is determined. Since it operates, the increase to the radial direction of an apparatus can be suppressed.

1 is a schematic configuration diagram of a continuously variable transmission with a continuously variable transmission pulley device according to a first embodiment of the present invention and a drive system of a vehicle including a continuously variable transmission device. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the first embodiment of the present invention. It is a layout view of each axis of the continuously variable transmission device for explaining the effect of the pulley device for continuously variable transmission according to each embodiment of the present invention. It is a typical block diagram of the drive system of the vehicle provided with the continuously variable transmission with the pulley apparatus for continuously variable transmissions and the continuously variable transmission apparatus which concern on the comparative example of each embodiment of this invention. It is a typical block diagram of the drive system of the vehicle provided with the continuously variable transmission with the pulley apparatus for continuously variable transmission which concerns on 2nd Embodiment of this invention, and a continuously variable transmission apparatus. It is a velocity diagram (collinear diagram) of the planetary gear mechanism of the mechanical pulley moving mechanism according to the second embodiment of the present invention.

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

[First Embodiment]
[Continuously variable transmission]
As shown in FIG. 1, an output shaft 2 </ b> A of a drive source (electric motor in the present embodiment) 2 for running a vehicle has a rotating shaft coupled to a fixed sheave 8 of a primary pulley 6 of a continuously variable transmission 4. (Hereinafter also referred to as a pulley shaft) 10 is connected. A movable sheave 12 having a sheave surface that forms a V-shaped groove of the pulley facing the sheave surface of the fixed sheave 8 is disposed on the pulley shaft 10 so as to be slidable in the axial direction and not relatively rotatable. Yes.

  A drive shaft 28 (hereinafter also referred to as a pulley shaft) 18 coupled to the fixed sheave 16 of the secondary pulley 14 of the continuously variable transmission 4 has a drive wheel 28 via a power transmission gear mechanism 24, a differential device 26, and the like. It is connected. Further, a movable sheave 20 having a sheave surface that forms a V-shaped groove of the pulley facing the sheave surface of the fixed sheave 16 is arranged on the pulley shaft 18 so as to be slidable in the axial direction and not relatively rotatable. Yes.

Further, between the sheaves 16 and 20 of the secondary pulley 14, a thrust adjusting mechanism 22 including a spring (not shown) for applying a biasing force in the direction of narrowing the V-shaped groove and a cam mechanism is interposed.
A belt 23 is wound around the pulleys 6 and 14.
The thrust adjustment mechanism 22 functions as a thrust adjustment mechanism that adjusts the thrust of the secondary pulley 14 to adjust the clamping pressure of the belt 23.

  In the primary pulley 6, the movable sheave 12 is disposed on one side of the pulley shaft 10 in the axial direction (left side in FIG. 1) with the belt 23 interposed therebetween, and the other direction side of the pulley shaft 10 in the axial direction ( A fixed sheave 8 is arranged on the right side in FIG.

  In the present embodiment, as shown in FIG. 3, a continuously variable transmission 4, a power transmission gear mechanism 24 that drives and connects the pulley shaft 18 of the secondary pulley 14 of the continuously variable transmission 4 and the differential device 26, A pulley device for a continuously variable transmission is applied to a continuously variable transmission device in which a differential device 26 is accommodated in a transmission casing 100.

  The power transmission gear mechanism 24 includes an idler gear shaft 24a and idler gears 24b and 24c that rotate integrally with the idler gear shaft 24a. The differential device 26 includes a differential case 26b in which a differential gear (not shown) is built, and a final gear 26a fixed to the differential case 26b.

  The idler gear 24b meshes with the output gear 18a that rotates integrally with the pulley shaft 18, the idler gear 24c meshes with the final gear 26a, and the output rotation of the continuously variable transmission 4 passes through the power transmission gear mechanism 24 and the differential device 26. It is transmitted from the left and right axles 28a to the drive wheels 28.

[Pully device for continuously variable transmission and its mechanical pulley moving mechanism]
As shown in FIG. 1, the movable sheave 12 is moved in the axial direction on the back surface (surface opposite to the sheave surface) 13 side of the movable sheave 12, that is, on one side in the axial direction (left side in the figure). A mechanical pulley moving mechanism 30A for adjusting the gear ratio is provided. The mechanical pulley moving mechanism 30A includes a torque cam mechanism 40, a first planetary gear mechanism 60, a second planetary gear mechanism 50, and an actuator 70. The first planetary gear mechanism 60 and the second planetary gear mechanism 50 are arranged in series on the same axis as the pulley shaft 10. In this embodiment, an electric motor with good controllability is used as the actuator. However, the actuator is not limited to the electric motor as long as necessary controllability can be ensured.

  The torque cam mechanism 40 includes a first cam (first cam member) 42 that is directly connected to the movable sheave 12 and rotates integrally therewith, and an axial direction is one direction of the movable sheave 12 via a thrust bearing (not shown). And a second cam (second cam member) 44 connected to the pulley shaft 10 protruding from the side so as to be relatively rotatable.

  A first cam surface 42 a is formed on one direction side of the first cam 42, and a second cam surface 44 a is formed on the other direction side of the second cam 44. The first cam surface 42a and the second cam surface 44a face each other and are in sliding contact with a ball (rigid ball) 48 as a rolling element interposed therebetween.

  The first cam 42 and the second cam 44 are arranged coaxially with the axis of the pulley shaft 10 on the outer peripheral side of the pulley shaft 10, and the first cam 42 is disposed on the other side in the axial direction. They are arranged on one side in the axial direction. The pulley shaft 10 is rotatably supported by the transmission casing 100 (see FIG. 3) by a bearing (not shown).

  The first cam 42 that rotates integrally with the movable sheave 12 is supported so that it cannot rotate relative to the pulley shaft 10 and can move in the axial direction with the same configuration as the movable sheave 12 (spline mechanism with a ball or roller interposed). Has been. The second cam 44 is supported so as to be relatively rotatable with respect to the pulley shaft 10 via a bearing or the like (not shown), and is held at a certain position with respect to the pulley shaft 10 in the axial direction so as not to move.

  That is, 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 relatively rotatable with respect to the pulley shaft 10 and not to be movable in the axial direction. It is possible to move the movable sheave 12 in the axial direction (change the gear ratio) by the displacement of the relative rotational phase 44.

  The first cam surface 42 a and the second cam surface 44 a are formed on opposite end surfaces of the cylindrical cams 42, 44, and the shape thereof is a spiral inclined surface inclined with respect to the axis of the pulley shaft 10. Is formed. In each embodiment, the inclined surfaces (that is, the first and second cam surfaces 42a and 44a) are inclined so as to approach the back surface 13 of the movable sheave 12 along the rotational direction of the primary pulley 6 when the vehicle is traveling forward. ing.

  When the relative rotation phase between the second cam 44 and the first cam 42 is changed, the total length of the torque cam mechanism 40 is changed. Since the second cam 44 does not move in the axial direction, the first cam 42 moves in the axial direction together with the movable sheave 12. Therefore, the relative rotation phase may be changed at the time of shifting to change the gear ratio. When the relative rotation phase is changed by rotating the second cam 44 relative to the first cam 42, the movable sheave 12 moves in the axial direction, and the gear ratio of the continuously variable transmission 5 is adjusted. Conversely, the relative rotational phase may be kept constant when the transmission ratio is fixed.

  In addition, between the 1st cam 42 and the 1st planetary gear mechanism 60, the slide allowance mechanism which is not shown in figure for permitting the relative movement along both axial directions, and making relative rotation impossible (rotation power can be transmitted). (A spline mechanism or the like interposing a ball or a roller or the like) is interposed. In the slide allowing mechanism, when both planetary gear mechanisms 50 and 60 are formed of helical gears, the relative movement in the axial direction between the respective gears becomes impossible. Therefore, the second planetary gear mechanism 60 and the first cam 42 are not allowed to move. Necessary to allow relative movement between. However, if either one or both of the planetary gear mechanisms 50 and 60 are constituted by spur gears, the relative movement in the axial direction between the spur gears becomes possible, so that the slide allowing mechanism can be omitted.

   The first planetary gear mechanism 60 is disposed on the outer periphery of the first cam 42, and any one of the three rotational elements of the sun gear 60S, the carrier 60C that pivotally supports the planetary gear 60P, and the ring gear 60R (first gear). 1 rotation element) is coupled to rotate integrally with the first rotation element of the second planetary gear mechanism 50, and any one of the remaining rotation elements (second rotation element) rotates integrally with the first cam 42. The remaining rotating elements (third rotating elements) are fixed to the transmission casing 100.

  The second planetary gear mechanism 50 is disposed on the outer periphery of the second cam 44, and any one of the three rotation elements of the sun gear 50S, the carrier 50C that pivotally supports the planetary gear 50P, and the ring gear 50R (the first rotation element) 1 rotation element) is connected to the first rotation element of the first planetary gear mechanism 60 so as to rotate integrally therewith, and any one of the remaining rotation elements (second rotation element) rotates integrally with the second cam 44. The remaining rotating elements (third rotating elements) are connected to the rotating shaft (output shaft) 71 of the actuator 70.

  The first rotating element, the second rotating element, and the third rotating element of the first planetary gear mechanism 60, and the first rotating element, the second rotating element, and the third rotating element of the second planetary gear mechanism 50 are mutually connected. The same rotating element. Further, the first planetary gear mechanism 60 and the second planetary gear mechanism 50 have gears corresponding to each other having the same size and the same number of teeth. That is, the sun gear 60S and the sun gear 50S, the planetary gear 60P and the planetary gear 50P, the ring gear 60R and the ring gear 50P, respectively, have the same size and the same number of teeth. Therefore, the gear ratio (tooth ratio) between the gears is also the same.

In the present embodiment, the first rotating elements are carriers 60C and 50C, the second rotating elements are sun gears 60S and 50S, and the third rotating elements are ring gears 60R and 50R.
Therefore, the carrier 60C of the first planetary gear mechanism 60 and the carrier 50C of the second planetary gear mechanism 50 are coupled so as to rotate integrally, and the sun gear 60S of the first planetary gear mechanism 60 rotates integrally with the first cam 42. The ring gear 60R of the first planetary gear mechanism 60 is fixed to the transmission casing 100.

  In addition, the sun gear 50S of the second planetary gear mechanism 50 is coupled to rotate integrally with the second cam 44, and the ring gear 50R of the second planetary gear mechanism 50 connects the external gears 71a and 71b to the output shaft 71 of the actuator 70. Are connected via a drive. The external gear 71b is fixed so as to rotate integrally with the output shaft 71 of the actuator 70, and the external gear 71a is formed so as to rotate integrally with the ring gear 50R.

  Further, the actuator 70 is located on the other outer side in the axial direction than the second cam 44 and the second planetary gear mechanism 50 on the further outer periphery of the second planetary gear mechanism 50 on the outer periphery of the second cam 44 (right side in FIG. 1). That is, at the axial position where the first cam 42 and the first planetary gear mechanism 60 and the primary pulley 6 are arranged, the second cam 44, the first planetary gear mechanism 60, and the primary pulley 6 are radially outside. It is arranged in the vicinity.

  In the first planetary gear mechanism 60, the third rotating element (in the present embodiment, the ring gear 60R) is fixed in a stopped state, so the remaining first rotating element (in the present embodiment, the carrier 60C) and the second The rotating element (in this embodiment, the sun gear 60S) rotates at a gear ratio (= output rotation speed / input rotation speed, also referred to as a speed ratio) corresponding to the gear ratio.

  In the second planetary gear mechanism 50, since the third rotating element (in this embodiment, the ring gear 50R) is coupled to the actuator 70, if the rotation of the actuator 70 is stopped, the remaining first rotating element (this embodiment) In the embodiment, the carrier 50C) and the second rotation element (in this embodiment, the sun gear 50S) rotate at a gear ratio (= output rotation speed / input rotation speed, also referred to as a speed ratio) corresponding to the gear ratio. .

  Since the first rotating elements of the first planetary gear mechanism 60 and the second planetary gear mechanism 50 (carriers 50C and 60C) are connected and rotate together, the first planetary gear mechanism 60 and the second planetary gear mechanism. Each of the 50 second rotation elements (sun gears 60S, 50S) rotates at a constant speed. The second rotating element (sun gear 60S) of the first planetary gear mechanism 60 is connected to the first cam 42 so as to rotate integrally therewith, and the second rotating element (sun gear 50S) of the second planetary gear mechanism 50 is connected to the second cam 44. Since they are connected so as to rotate integrally, the first cam 42 and the second cam 44 rotate at the same speed.

  On the other hand, if the actuator 70 is rotated, the first cam 42 is directly connected to the movable pulley 12 and thus the rotational speed does not change. Therefore, a differential rotation occurs between the first cam 42 and the second cam 44. The second cam 44 rotates relative to the first cam 42 to change the relative rotation phase between the first cam 42 and the second cam 44. As a result, the movable sheave 12 moves in the axial direction, and the gear ratio of the continuously variable transmission 4 is adjusted.

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

  FIG. 2 is a collinear diagram (velocity diagram) of the first planetary gear mechanism 60 and the second planetary gear mechanism 50. The first planetary gear mechanism 60 always has the characteristics indicated by the solid line L in FIG. When the actuator 70 is stopped, the second planetary gear mechanism 50 has the same characteristics as the first planetary gear mechanism 60 indicated by the solid line L, and the gear ratio of the continuously variable transmission 4 is maintained constant.

  On the other hand, when the actuator 70 is rotated forward in the same direction as the rotation direction of the pulley 6, the characteristic changes as shown by the broken line La, and the speed change a can be performed. That is, the phase ratio of the continuously variable transmission 4 can be adjusted by changing the overall length of the torque cam mechanism 40 by delaying the phase of the second cam 44 relative to the first cam 42. Further, when the actuator 70 is rotated in the reverse direction to the rotation direction of the pulley 6, the characteristic changes as shown by the broken line Lb, and the speed change b can be performed. In other words, the phase of the continuously variable transmission 4 can be adjusted by changing the overall length of the torque cam mechanism 40 by advancing the phase of the second cam 44 relative to the first cam 42.

In the present embodiment, as shown in FIG. 3, a continuously variable transmission pulley device is applied to the continuously variable transmission device. This continuously variable transmission device is equipped with a pulley shaft 10 of a primary pulley 6 in a state where the right side of FIG. 3 is mounted on a vehicle with the vehicle body front (or front part) and the left side of FIG. 3 the vehicle body rear (or rear part). Is on the first axis O ₁ , the pulley shaft 18 of the secondary pulley 14 is on the second axis O ₂ above the rear of the first axis O ₁ , and the idler gear shaft 24 a of the power transmission gear mechanism 24 is on the second axis O ₂ . The output shaft of the differential device 26 is disposed on the third axis O ₃ below the rear portion and on the fourth axis O ₄ below the third axis O ₃ , respectively, so that the actuator 70 of the pulley device for continuously variable transmission is provided. to the output shaft 71 is the first axis O ₁ and the second connecting axis O ₂ line a first upper axis O _1, third opposite side of the region to the axis O ₃ and fourth axis O ₄ 5 is arranged on the axis O ₅ of. Each axis O _{1 to} O ₅ corresponds to the rotation center line of each axis.

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

In the present embodiment, the number of teeth of each rotating element of the first planetary gear mechanism 60 and the second planetary gear mechanism 50 is the same, that is, the tooth number ratio α _{1 of} the first planetary gear mechanism 60 is Since the gear ratio α ₂ of the second planetary gear mechanism 50 is the same (α ₁ = α ₂ ), the gear ratio of the continuously variable transmission 4 is kept constant by stopping the actuator 70. Therefore, the operation frequency of the actuator 70 can be reduced.

  When changing the gear ratio, the actuator 70 is rotated in a predetermined direction to cause the second cam 44 to rotate relative to the first cam 42 (and thus the pulley 6), so that the relative relationship between the first cam 42 and the second cam 44 is increased. Change the rotation phase. At this time, in the thrust bearing interposed between the pulley shaft 10 and the second cam 44, the belt received by the second cam 44 toward the other end side (right side in the drawing) via the first cam 42. 23 thrust is applied and relative rotation occurs. However, since the relative rotation is a short time and the speed of the relative rotation is low, friction due to the relative rotation is generated but suppressed to a small amount.

  Further, the ring gear 50 of the second planetary gear mechanism 50 is connected to the electric motor 70, and the ring gear 50R of the first planetary gear mechanism 60 is fixed to the transmission casing 100, and the ring gears 50R and 60R are mechanisms. Since the electric motor 70 and the transmission casing 100 are easily accessible, the structure can be simplified, which is advantageous in reducing the axial and radial sizes of the apparatus.

  Further, if the actuator 70 is disposed on one axial side (left side in FIG. 1) in the axial direction with respect to the second cam 44 and the second planetary gear mechanism 50, the device is easily expanded in the axial direction. In the embodiment, the actuator 70 includes the second cam 44 and the second planetary gear mechanism 50 in the other axial direction (right side in FIG. 1), that is, the first cam 42 and the first planetary gear mechanism 60 and the primary. Since it is arrange | positioned in the vicinity of the radial direction outer side of the pulley 6, the expansion to the axial direction of an apparatus can be suppressed.

  Further, since the sun gears 50S and 60S, the planetary gears 50P and 60P, and the ring gears 50R and 60R of the second planetary gear mechanism 50 and the first planetary gear mechanism 60 are set to the same number of teeth, It is possible to simplify the overall configuration (axial direction and radial direction) and to simplify the control program for the electric motor 70.

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

The point which can suppress expansion to said radial direction is further demonstrated.
As shown in FIG. 3, the output shaft 71 of the actuator 70 of the continuously variable transmission pulley device is disposed on the fifth axis O ₅ above the first axis O ₁ . As shown in FIG. 1, the actuator 70 is disposed on the outer periphery of the second planetary gear mechanism 50 on the outer periphery of the second cam 44, but the external gear 71 a fixed to the output shaft 71 has a particularly large outer shape. Since it is not necessary, the fifth axis O ₅ can be brought close to the first axis O ₁ in a range where the actuator 70 does not interfere with the first planetary gear mechanism 60 and the primary pulley 6 inside thereof. In addition, the axial projection areas of the actuator 70 and the external gear 71a (see the dashed circle) can be kept small.

  FIG. 3 shows the transmission casing 100 of the continuously variable transmission apparatus that is not equipped with this apparatus, but even if the actuator 70 is equipped, the protrusion of the transmission casing 100 in the radial direction is slightly suppressed. It is done. Accordingly, it is possible to avoid interference of the continuously variable transmission device with a radiator, a crushable zone space for protecting a pedestrian, a pedestrian protection airbag, an air cleaner, or the like provided around the transmission of the vehicle.

Here, the fact that the axial and radial sizes of the apparatus can be made compact will be described with reference to a comparative example shown in FIG.
As shown in FIG. 4, the mechanical pulley moving mechanism 30 ′ of the comparative example is different from the second planetary gear mechanism 50 of the present embodiment in the arrangement and connection state of the second planetary gear mechanism 51 connected to the second cam 44. In addition, a parallel shaft gear mechanism 61 is connected to the second cam 44 instead of the first planetary gear mechanism 60.

  That is, the second planetary gear mechanism 51 is arranged coaxially with the actuator 70, and the sun gear 51 </ b> S of the second planetary gear mechanism 51 is directly connected to the output shaft 71 of the actuator 70. The ring gear 51R of the second planetary gear mechanism 51 is connected to the second cam 44 via an external tooth 52a that rotates integrally with the ring gear 51R and an external gear 52b that rotates integrally with the second cam 44 and meshes with the external gear 52a. It is connected. The carrier 51C of the second planetary gear mechanism 51 is connected to the first cam 42 via an external gear 61a that rotates integrally with the carrier 51C and an external gear 61b that rotates integrally with the first cam 42 and meshes with the external gear 61a. Has been.

If the rotational speed of the carrier 51C is Nc, the rotational speed of the ring gear 51R is Nr, the number of teeth of the sun gear 51S is Zs, and the number of teeth of the ring gear 51R is Zr, the rotational speed ratio (Nc) of the carrier 51C and the ring gear 51R / Nr) is less than 1 (Nc <Nr) as in the following equation (1), and the rotational speed Nc of the carrier 51C is lower than the rotational speed Nr of the ring gear 51R.
Nc / Nr = Zr / (Zs + Zr) <1 (1)

Since the rotational speed Nc of the carrier 51C is lower than the rotational speed Nr of the ring gear 51R, in order to make the rotational speed N _{cam 1} of the first cam 42 coincide with the rotational speed N _{cam 2} of the second cam 44, As in 2), the rotational speed ratio (N _{cam 1} / Nc) between the first cam 42 and the carrier 51C is made larger than the rotational speed ratio (N _{cam 2} / Nr) between the second cam 44 and the ring gear 51R. It will be necessary.
N _{cam 1} / Nc> N _{cam 2} / Nr (2)

When the number of teeth of the external gear 61a is Z _1A and the number of teeth of the external gear 61b is Z _1B , the rotation speed ratio (N _{cam 1} / Nc) can be replaced with the tooth number ratio (Z _1A / Z _1B ). . When the number of teeth of the external gear 52a is Z _2A and the number of teeth of the external gear 52b is Z _2B , the rotation speed ratio (N _{cam 2} / Nr) can be replaced with the tooth number ratio (Z _2A / Z _2B ). . Therefore, the equation (2) can be converted into the following equation (3).
Z _1A / Z _1B > Z _2A / Z _2B (3)

Further, since the external gears 61a and 52a are coaxial with each other and the external gears 61b and 52b are coaxial with each other, it is necessary to satisfy the condition of the following expression (4).
Z _1A + Z _1B = Z _2A + Z _2B (4)
From the formulas (3) and (4), the external gear 61a has a larger number of teeth than the external gear 52a, and therefore the outer shape becomes larger.

Therefore, as shown in FIG. 3, the output shaft 71 of the actuator 70 and the rotation shaft of the second planetary gear mechanism 51 (refer to the fifth axis O ₅ ′) must be arranged far away from the pulley shaft 10. Don't be. Furthermore, since the external gear 61a coaxial with the rotation shaft 71 of the actuator 70 has a large outer shape, the axial projection area (the two-dot chain line circle) of the second planetary gear mechanism 51 and the actuator 70 including the external gear 61a. ) Will become larger.

[Second Embodiment]
(Constitution)
As shown in FIG. 5, in this embodiment, the first planetary gear mechanism 60 and the second planetary gear mechanism 50 of the mechanical pulley moving mechanism 30B are configured in the same manner as in the first embodiment. 1 rotation element and 3rd rotation element differ from 1st Embodiment.
That is, in this embodiment, the first rotating element is the ring gear 60R, 50R, the second rotating element is the sun gear 60S, 50S, and the third rotating element is the carrier 60C, 50C. Other than this, the configuration is the same as in the first embodiment.

  Accordingly, the ring gear 60R of the first planetary gear mechanism 60 and the ring gear 50R of the second planetary gear mechanism 50 are coupled so as to rotate together, and the sun gear 60S of the first planetary gear mechanism 60 rotates together with the first cam 42. The carrier 60C of the first planetary gear mechanism 60 is fixed to the transmission casing 100.

  Further, the sun gear 50S of the second planetary gear mechanism 50 is connected to rotate integrally with the second cam 44, and the carrier 50C of the second planetary gear mechanism 50 is connected to the output shaft 71 of the actuator 70 via the external gears 71a and 71b. Drive coupled. The external gear 71b is fixed so as to rotate integrally with the output shaft 71 of the actuator 70, and the external gear 71a is connected to the carrier 50C so as to rotate integrally.

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

  FIG. 6 is an alignment chart (velocity diagram) of the first planetary gear mechanism 60 and the second planetary gear mechanism 50. The first planetary gear mechanism 60 always has the characteristic indicated by the solid line L in FIG. When the actuator 70 is stopped, the second planetary gear mechanism 50 has the same characteristics as the first planetary gear mechanism 60 indicated by the solid line L, and the gear ratio of the continuously variable transmission 4 is maintained constant.

  On the other hand, when the actuator 70 is rotated forward in the same direction as the rotation direction of the pulley 6, the characteristic changes as shown by the broken line La, and the speed change a can be performed. In other words, the phase of the continuously variable transmission 4 can be adjusted by changing the overall length of the torque cam mechanism 40 by advancing the phase of the second cam 44 relative to the first cam 42. Further, when the actuator 70 is rotated in the reverse direction to the rotation direction of the pulley 6, the characteristic changes as shown by the broken line Lb, and the speed change b can be performed. That is, the phase ratio of the continuously variable transmission 4 can be adjusted by changing the overall length of the torque cam mechanism 40 by delaying the phase of the second cam 44 relative to the first cam 42.

(Function and effect)
Since the pulley device for continuously variable transmission according to the present embodiment is configured as described above, it is possible to obtain substantially the same effects as those of the first embodiment.

  In the present embodiment, the carrier 60C of the first planetary gear mechanism 60 is fixed to the transmission casing 100, and the carrier 50C of the second planetary gear mechanism 50 is connected to the output shaft 71 of the actuator 70. In either case, it is necessary to connect the carrier 60C and the transmission casing 100 and the carrier 50C and the output shaft 71 of the actuator 70 so as not to interfere with the ring gears 60R and 50R. For this reason, although the reduction in size in the axial direction and the radial direction and the simplification of the configuration do not reach the first embodiment, certain effects can be obtained.

[Others]
As mentioned above, although embodiment of this invention was described, this invention can be suitably changed and implemented in the range which does not deviate from the meaning.
In particular, the first rotating element coupled to each other of the first and second planetary gear mechanisms, the second rotating element directly coupled to the first cam of the first planetary gear mechanism, and the second rotating element of the second planetary gear mechanism. The second rotating element directly connected to the two cams, the third rotating element fixed to the first planetary gear mechanism, the third rotating element connected to the actuator of the second planetary gear mechanism, The three rotational elements of the carrier and the ring gear can be appropriately selected and applied.

In each embodiment, the number of teeth of each rotating element of the first planetary gear mechanism 60 and the second planetary gear mechanism 50 is the same, that is, the tooth ratio of the planetary gear mechanism is the same (α ₁ = α ₂ ). However, it is not limited to this. For example, the tooth number ratio α2 of the second planetary gear mechanism 50 in the first embodiment may be set to be smaller than the tooth number ratio α1 of the first planetary gear mechanism 60 (α ₁ > α ₂ ). In this case, when fixing the gear ratio, the actuator 70 is rotated forward at a constant speed of a predetermined rotational speed. Further, by changing the rotational speed in the positive direction or the negative direction with respect to the rotation at the predetermined rotational speed, it is possible to change the speed (change the speed ratio).

2 Drive source 4 Continuously variable transmission 6 Primary pulley 8 Primary sheave 6 fixed sheave 10 Primary pulley 6 rotating shaft 12 Primary pulley 6 movable sheave 14 Secondary pulley 16 Secondary pulley 14 fixed sheave 18 Secondary pulley 14 drive shaft 20 Secondary sheave 14 movable sheave 22 Thrust adjusting mechanism 23 Belt (endless belt-like member)
24 power transmission gear mechanism 26 differential device 28 drive wheel 30A, 30B mechanical pulley moving mechanism 40 torque cam mechanism 42 first cam member (first cam)
44 Second cam member (second cam)
50 Second planetary gear mechanism 60 First planetary gear mechanism 50S, 60S Sun gear 50C, 60C Carrier 50R, 60R Ring gear 50P, 60P Planetary gear 70 Electric motor as actuator

Claims (6)

A mechanical type that is applied to either of the pulleys of a continuously variable transmission that includes a primary pulley and a secondary pulley and a belt that spans the pulleys, and that moves a movable sheave in an axial direction to adjust a gear ratio. A continuously variable transmission pulley apparatus having a pulley moving mechanism,
The mechanical pulley moving mechanism is
The first and second cam members are arranged in series on the same axis as a pulley shaft to which the fixed sheave is coupled by sliding the cam surfaces to each other, and the first cam member is connected to the movable sheave. When the second cam member is provided so as to be relatively rotatable with respect to the pulley shaft and not to be relatively movable in the axial direction, and the relative rotation phase of the second cam member with respect to the first cam member is changed. A torque cam mechanism for changing the total length, moving the movable sheave in the axial direction and adjusting the thrust force;
The relative rotation phase of the second cam member is changed during a shift, and the first cam member and the second cam member are rotated at the same speed in the same direction when the transmission ratio is fixed. A constant actuator;
A first planetary gear mechanism and a second planetary gear mechanism each having rotating elements of a sun gear, a carrier, and a ring gear,
The first planetary gear mechanism and the second planetary gear mechanism are arranged in series on the same axis as the pulley shaft,
The first rotating elements of the first and second planetary gear mechanisms are coupled together;
A second rotating element of the first planetary gear mechanism is directly connected to the first cam member;
The second rotating element of the second planetary gear mechanism is directly connected to the second cam member;
A third rotating element of the first planetary gear mechanism is fixed;
A continuously variable transmission pulley apparatus, wherein the third rotating element of the second planetary gear mechanism is drivingly connected to the actuator. The first rotating element is a carrier;
The second rotating element is a sun gear,
The pulley device for a continuously variable transmission according to claim 1, wherein the third rotating element is a ring gear. The first rotating element is a ring gear;
The second rotating element is a sun gear,
The pulley device for a continuously variable transmission according to claim 1, wherein the third rotating element is a carrier. The movable sheave is disposed on one side in the axial direction of the pulley shaft across the belt, and the fixed sheave is disposed on the other side in the axial direction,
The first cam member is disposed adjacent to the movable sheave, and the first planetary gear mechanism is disposed on an outer periphery of the first cam member,
The second cam member is disposed on the outer periphery of the pulley shaft that protrudes in the one direction side relative to the first cam member, and the second planetary gear mechanism is disposed on the outer periphery of the second cam member. Arranged,
The pulley device for a continuously variable transmission according to any one of claims 1 to 3, wherein the actuator is arranged on the other direction side with respect to the second planetary gear mechanism. A continuously variable transmission including a primary pulley and a secondary pulley and a belt spanned between the two pulleys;
A continuously variable transmission, wherein the primary pulley is equipped with the pulley device for a continuously variable transmission according to any one of claims 1 to 4. A continuously variable transmission according to claim 5;
A differential device with a final gear;
A continuously variable transmission device equipped in a vehicle, comprising a power transmission gear mechanism having an idler gear for drivingly connecting a pulley shaft of the secondary pulley of the continuously variable transmission and the differential device;
The pulley shaft of the primary pulley is on the first axis while the pulley shaft of the secondary pulley is on the second axis above the rear of the first axis in the state where the vehicle is equipped with the idler gear of the power transmission gear mechanism. The shaft is disposed on the third axis below the rear portion of the second axis, and the output shaft of the differential device is disposed on the fourth axis below the third axis.
The output shaft of the actuator of the pulley device for continuously variable transmission is above the first axis, and the third axis and the fourth axis with respect to a line connecting the first axis and the second axis. A continuously variable transmission device, wherein the continuously variable transmission device is disposed on a fifth axis in a region opposite to the first region.

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