JP2019002538A - Pulley device for stepless transmission and assembly method therefor - Google Patents

Abstract

To reduce rotational friction when axially moving a movable sheave of a stepless transmission while using a mechanical actuator.SOLUTION: A pulley device for stepless transmission comprises: a torque cam mechanism 40 in which a first cam 42 is directly connected with a movable sheave 12, of which the full length is changed by changing a rotational phase of a second cam 44 relative to the first cam 42 and which is axially moved in the movable sheave; an actuator 70 of which the rotational phase is changed or fixed; and a planetary gear mechanism 50 in which a first rotary element is connected to a first cam member via a first parallel shaft type gear mechanism 61, a second rotary element is connected to a second cam member via a second parallel shaft type gear mechanism 62 and a third rotary element is connected to the actuator. For the parallel gear shaft type mechanisms 61 and 62, a speed transmission ratio is set in such a manner that both the cam members are rotated at an equal speed in the same direction in a case where a change gear ratio is fixed.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a pulley apparatus for a continuously variable transmission that moves a movable sheave in an axial direction by a mechanical actuator using a torque cam mechanism and an assembling method thereof.

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

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

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.

  The present invention was devised in view of such problems, and in a continuously variable transmission that moves a movable sheave in an axial direction by using a mechanical actuator, it is possible to reduce friction of pulley rotation and reduce power transmission loss. An object of the present invention is to provide a pulley device for a continuously variable transmission and an assembling method thereof that can suppress the occurrence of this.

  (1) In order to achieve the above object, a pulley device for a continuously variable transmission according to the present invention includes a primary pulley, a secondary pulley, and a belt spanned between the two pulleys. A movable sheave that is applied to one of the pulleys and that is disposed on one side in the axial direction across the belt moves in the axial direction with respect to a fixed sheave that is disposed on the other side in the axial direction to change the gear ratio. A pulley apparatus for a continuously variable transmission having a mechanical pulley moving mechanism for adjusting, wherein the mechanical pulley moving mechanism is arranged in series on the same axis as the movable sheave by sliding the cam surfaces of each other. 1 and a second cam member, the first cam member is directly connected to the one-direction side of the movable sheave, and the second cam member is further to the one-direction side than the first cam member. The fixed sheave is combined in When the relative rotation phase of the second cam member with respect to the first cam member is changed, the total length is changed and the movable sheave is pivoted. A torque cam mechanism that moves in the direction and adjusts the thrust, an actuator that changes or keeps the relative rotation phase of the second cam member, and three rotation elements of a sun gear, a carrier, and a ring gear, and these rotations Of the elements, a first rotating element is connected to the first cam member via a first power transmission mechanism, and a second rotating element is connected to the second cam member via a second power transmission mechanism. A planetary gear mechanism arranged on a second axis parallel to a first axis that is a rotation center of the fixed sheave and the movable sheave, and a third rotating element is connected to the actuator. The first power transmission mechanism includes a first gear that rotates integrally with the first cam member, and a second gear that rotates integrally with the first rotating element and meshes with the first gear. The second power transmission mechanism includes a third gear that rotates integrally with the second cam member, and a gear that rotates integrally with the second rotating element and meshes with the third gear. A second parallel gear mechanism comprising a fourth gear, wherein the first and second power transmission mechanisms are fixed at a gear ratio in which the relative rotational phase of the first and second cam members is constant by the actuator. The speed transmission ratio is set so that the first and second cam members rotate at the same speed in the same direction.

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

  (3) The first parallel shaft gear mechanism and the second parallel shaft gear mechanism are arranged in this order from the movable sheave toward the one direction side, and the third gear has a larger diameter than the first gear. And the second gear has a larger diameter than the fourth gear, extends concentrically with the movable sheave on the one-direction side of the first gear, and extends from the first rotation axis to the second gear. A cylindrical portion having an outer diameter smaller than the distance to the rotation region, a flange portion extending outwardly on the outer periphery of the second cam member so as to be close to the inner periphery of the cylindrical portion, and the second A gear support bearing which is interposed between an outer peripheral portion of the cam member and the cylindrical portion and which rotatably supports the first gear while restricting at least movement of the first gear in the axial direction; Also on the one direction side, the outer peripheral portion of the second cam member and the circle Formed on the inner peripheral side of the third gear, which is located in the storage space and is connected to the second cam member so as to rotate integrally therewith. An annular connection base, and a first restriction member that is attached to the second cam member on the one direction side of the connection base and restricts movement of the connection base in the axial direction. preferable.

(4) It is preferable that an axial movement allowance mechanism is interposed between the first cam member and the first gear.
(5) The gear support bearing is a ball bearing, and an outer race of the ball bearing is provided in an inwardly-opening annular groove formed on an inner peripheral surface of the cylindrical portion, and The movement in the axial direction is restricted by a second restricting member attached to the cylindrical portion, and the inner race of the ball bearing is mounted in an outwardly-opening annular groove formed on the outer peripheral surface of the connecting base portion, It is preferably sandwiched between the side wall surface of the orientation-opening annular groove and the facing surface of the flange portion facing the side wall surface.
(6) It is preferable that the first restricting member is a nut that is screwed and fastened to the second cam member.

(7) The gear support bearings are first and second thrust bearings, and the first thrust bearing is formed in the other direction side inside the cylindrical portion toward the one direction. The second wall surface is interposed between the first wall surface and the second wall surface formed on the flange portion so as to face the first wall surface, and the second thrust bearing is disposed in the one direction inside the cylindrical portion. It is interposed between the third wall surface facing the other direction of the wall member fixed to the side portion with the fixing member and the fourth wall surface formed on the flange portion so as to face the third wall surface. It is preferable.
(8) A main bearing that rotatably supports the pulley shaft is mounted on the one direction side of the second cam member, and a thrust bearing is provided between the second cam member and the inner race of the main bearing. It is preferable that the inner diameter of the coupling base is formed larger than the outer diameter of the main bearing.

  (9) Moreover, the assembly method of the pulley apparatus for continuously variable transmission of the 1st aspect of this invention is an assembly method of the pulley apparatus for continuously variable transmission of the said (5) term, Comprising: The said pulley of the said fixed sheave With respect to a pulley assembly in which the movable sheave is assembled to a shaft, and the first cam member is directly coupled to the movable sheave with the cam surface directed in the one direction, the first gear is connected to the first sheave. A first step of arranging the first gear on the outer periphery of the first cam member by being arranged on an axis and entering from the one direction side toward the other direction side; and the second gear is the planetary gear A planetary gear assembly assembled to the mechanism is arranged on the second axis and is advanced from the one direction side toward the other direction side, and the second gear meshes with the first gear. And the second cam member on the first shaft A third step of placing the first cam member in the one-direction side of the first cam member by being disposed on the one-direction side and entering the other-direction side; and the ball bearing as the gear support bearing. A first shaft is disposed on the first axis and is made to enter from the one direction side toward the other direction side, and the outer race of the ball bearing is fitted into the inwardly open annular groove of the first cam member. 4 steps, a 5th step of disposing the second restricting member on the first axis, entering from the one direction side toward the other direction side, and fixing to the cylindrical portion, and the third gear. Is disposed on the first axis and is made to enter from the one direction side toward the other direction side, so that the fastening base is accommodated in the accommodation space and the outward opening annular groove of the fastening base is Ball bearing inner race A sixth step of fitting, and the first restricting member is disposed on the first axis and is made to enter from the one direction side to the other direction side of the connection base portion, to the second cam member The seventh step of mounting the first restricting member is sequentially performed.

  (10) A method for assembling a second continuously variable transmission pulley apparatus according to the present invention is the method for assembling the continuously variable transmission pulley apparatus according to the above (7), wherein the pulley shaft of the fixed sheave is attached to the pulley shaft. With respect to a pulley assembly in which the movable sheave is assembled and the first cam member is directly coupled to the movable sheave with the cam surface directed in the one direction, the first gear is placed on the first axis. And the first step of incorporating the first gear into the outer periphery of the first cam member, and the second gear into the planetary gear mechanism. A second step of disposing the assembled planetary gear assembly on the second axis and entering from the one direction side toward the other direction side to mesh the second gear with the first gear; The first thrust bearing is connected to the first thrust bearing. The cam member is installed on the second wall surface of the flange portion, the second thrust bearing is installed on the fourth wall surface of the flange portion, and the second cam member is placed on the first axis. And the first thrust bearing is incorporated into the one-direction side of the first cam member, and the first thrust bearing is connected to the first wall surface and the second wall surface. And a third step interposed between the second wall surface and the second wall surface of the second thrust bearing between the third wall surface and the fourth wall surface. And a fifth step of disposing the second restricting member on the first axis, entering from the one direction side toward the other direction side, and fixing to the cylindrical portion. , The third gear is arranged on the first axis and the one direction side A sixth step of entering toward the other direction and accommodating the fastening base in the accommodation space; and arranging the first restricting member on the first axis so that the one direction side of the connection base And the seventh step of attaching the first restricting member to the second cam member in order toward the other direction.

  (11) Preferably, after the third step, there is provided a main bearing mounting step in which the main bearing is press-fitted and fixed to the pulley shaft on the one-direction side of the second cam member.

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

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

It is a typical block diagram of the continuously variable transmission and pulley apparatus for continuously variable transmission which concern on each embodiment of this invention. It is a typical block diagram of the pulley apparatus for continuously variable transmission which concerns on each embodiment of this invention. It is a speed diagram (collinear diagram) of the planetary gear mechanism of the pulley device for continuously variable transmission according to each embodiment of the present invention. It is a block diagram which shows the principal part of the pulley apparatus for continuously variable transmission which concerns on 1st Embodiment of this invention. It is a block diagram which shows the principal part of the pulley apparatus for continuously variable transmission which concerns on 2nd Embodiment of this 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.

[Configuration of continuously variable transmission according to each embodiment]
FIG. 1 is a configuration diagram schematically showing a continuously variable transmission according to each embodiment. As shown in FIG. 1, a drive source 2 including an internal combustion engine and an electric motor for running a vehicle includes a planetary gear. A continuously variable transmission 5 is connected via a forward / reverse switching mechanism 4 composed of a gear mechanism or the like.
The continuously variable transmission 5 includes a primary pulley 6 and a secondary pulley 14, and a belt 26 spanned between these pulleys 6 and 14.

  The primary pulley 6 is a continuously variable transmission pulley apparatus according to each embodiment, and includes a fixed sheave 8 and a movable sheave 12 with a belt 26 interposed therebetween. The movable sheave 12 is disposed on one side in the axial direction (right side in the drawing) with the belt 26 interposed therebetween, and has a sheave surface that forms a V-shaped groove of the pulley facing the sheave surface of the fixed sheave 8. Yes. The movable sheave 12 is connected to a rotating shaft (pulley shaft) 10 coupled to the fixed sheave 8 so as to be slidable in the axial direction and not relatively rotatable. It is separated from and fixed to the fixed sheave 8 arranged in the middle left).

  The secondary pulley 14 also has a fixed sheave 16 and a movable sheave 20 with a belt 26 interposed therebetween. The movable sheave 20 is arranged on the other side in the axial direction (left side in the figure) across the belt 26 and has a sheave surface that forms a V-shaped groove of the pulley facing the sheave surface of the fixed sheave 16. Yes. The movable sheave 20 is connected to a rotation shaft (pulley shaft and drive shaft) 18 coupled to the fixed sheave 16 so as to be slidable in the axial direction and not relatively rotatable. The fixed sheave 16 arranged on the side (right side in the figure) is in contact with the fixed sheave 16.

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

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

  Mechanical pulley movement that adjusts the gear ratio by moving the movable sheave 12 in the axial direction on the back side (surface opposite to the sheave surface) 13 side (one direction side in the axial direction) of the movable sheave 12 of the primary pulley 6 A mechanism 30 is provided. In FIG. 1, the mechanical pulley moving mechanism 30 is described in a very simplified manner. However, the mechanical pulley moving mechanism 30 includes a torque cam mechanism 40, a planetary gear mechanism 50, first and second power transmission mechanisms 60A, 60B and an electric motor 70 as an actuator are provided. As will be described later, here, the first parallel shaft gear mechanism 61 is used for the first power transmission mechanism 60A, and the second parallel shaft gear mechanism 62 is used for the power transmission mechanism 60B. In the following description, the parallel shaft gear mechanisms 61 and 62 are simplified and are also referred to as parallel gear mechanisms 61 and 62.

[Outline of Mechanical Pulley Moving Mechanism According to Each Embodiment]
As shown in FIG. 2, the torque cam mechanism 40 has a first cam surface 42a formed at one end (right side in the figure) and is directly connected to the movable sheave 12 (fixedly connected so that relative rotation is impossible and axial relative movement is impossible). The first cam (first cam member) 42 and the second cam surface 44a opposite to the first cam surface 42a of the first cam 42 are formed at the other end (left side in the figure). One end (right side in the figure) includes a second cam (second cam member) 44 whose axial position is regulated by the rotary shaft 10 via a thrust bearing 46. Here, the torque cam mechanism 40 is configured as a ball cam mechanism in which a ball (for example, a steel ball) 48 is interposed as a rolling element between the first cam 42 and the second cam 44.

  The first cam 42 and the second cam 44 are arranged in series on the outer periphery of the rotary shaft 10 coaxially with the first axis SC <b> 1 that is the rotation center of the rotary shaft 10. The rotary shaft 10 is rotatably supported by a transmission casing (not shown) via bearings 32 and 34. The first cam 42 that rotates integrally with the movable sheave 12 is supported so as not to rotate relative to the rotating shaft 10 and to be movable in the axial direction by a configuration similar to that of the movable sheave 12 (spline mechanism with a ball or roller interposed therebetween). Has been. The second cam 44 is supported so as to be relatively rotatable with respect to the rotary shaft 10 via a bearing or the like (not shown), and in the axial direction, the second cam 44 is held in a fixed position with respect to the rotary shaft 10 so as not to move. It is impossible.

  As described above, the first cam 42 is directly connected to the movable sheave 12 and the second cam 44 is supported so as not to move in the axial direction with respect to the rotary shaft 10. It is possible to move the movable sheave 12 in the axial direction (change the gear ratio).

  In other words, the first cam surface 42a and the second cam surface 44a are formed on the end surfaces of the cylindrical cams 42, 44 facing each other, and are disposed so as to be in sliding contact with each other. The shapes of these cam surfaces 42 a and 44 a are formed in a spiral slope inclined with respect to the axis SC <b> 1 of the rotary shaft 10. In each embodiment, the inclined surfaces (that is, the first and second cam surfaces 42a and 44a) are inclined so as to approach the back surface 13 of the movable sheave 12 along the rotational direction of the primary pulley 6 when the vehicle is traveling forward. ing.

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

  The planetary gear mechanism 50 is disposed on the outer periphery of the second cam 44, and includes three rotating elements: a carrier 50C that pivotally supports the sun gear 50S and the planetary gear 50P, and a ring gear 50R. Any one of these rotation elements (first rotation element) is connected to the first cam 42 via the first power transmission mechanism 60A, and any one of the remaining rotation elements (second rotation element) is connected. The rotating element) is connected to the second cam 44, and the remaining rotating element (third rotating element) is connected to an electric motor 70 as an actuator.

However, in each embodiment shown here, the carrier 50C is set as the first rotating element, the ring gear 50R is set as the second rotating element, and the sun gear 50S is set as the third rotating element. That is, the carrier 50C is connected to the first cam 42 via the parallel gear mechanism 61 of the power transmission mechanism 60, the ring gear 50R is connected to the second cam 44, and the remaining sun gear 50S is connected to the electric motor 70 as an actuator. ing.
An electric motor is suitable as the actuator, but the actuator is not limited to the electric motor as long as the controllability necessary for the actuator can be ensured.

The first parallel gear mechanism 61 of the first power transmission mechanism 60A is provided between the first cam 42 and the carrier 50C. The first parallel gear mechanism 61 is connected to the first cam 42 and has an external first gear 61a that rotates integrally with the first cam 42, and an external tooth that is connected to the carrier 50C and rotates integrally with the carrier 50C. The second gear 61b is configured to mesh with each other.
The second parallel gear mechanism 62 of the second power transmission mechanism 60B is provided between the second cam 44 and the ring gear 50R. The second parallel gear mechanism 62 is connected to the second cam 44 and has an external third gear 62a that rotates integrally with the second cam 44, and an outer ring that is provided on the outer periphery of the ring gear 50R and rotates integrally with the ring gear 50R. The toothed fourth gear 62b is configured to mesh with each other.

  In addition, between the 1st cam 42 and the 1st gear 61a of the 1st parallel gear mechanism 61 of 60 A of 1st power transmission mechanisms, relative movement along both axial directions is permitted, and relative rotation is impossible (rotation power is reduced. A slide allowance mechanism (spline mechanism or the like with a ball or a roller or the like) 80 is interposed.

  When each gear of the planetary gear mechanism 50, each gear of the first parallel gear mechanism 61 of the first power transmission mechanism 60A, and each of the second parallel gear mechanism 62 of the second power transmission mechanism 60B are configured by helical gears, Since the relative movement in the axial direction between the gears becomes impossible, the slide allowing mechanism 80 is necessary for allowing the relative movement between the first parallel gear mechanism 61 and the first cam 42. However, if either one or both of the planetary gear mechanism 50 and the power transmission mechanism 60 are made of spur gears, relative movement between the spur gears becomes possible, so that the slide allowing mechanism 80 can be omitted. .

  If the rotation of any one of the three rotating elements (sun gear 50S, carrier 50C, ring gear 50R) is restricted or actively controlled, the planetary gear mechanism 50 rotates one of the remaining two rotating elements. The element becomes a relative reaction force element, and the other rotating element rotates at a gear ratio (= output rotation speed / input rotation speed, also referred to as speed ratio) corresponding to the gear ratio. The rotation restriction or active control in this case can be defined as setting the rotation speed to a predetermined speed (including constant speed and rotation stoppage). The rotation is restricted by the electric motor 70. That is, by controlling 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.

  In each embodiment shown here, the third rotating element is a sun gear 50 </ b> S, and the sun gear 50 </ b> S is connected to the electric motor 70. By controlling the rotation of the sun gear 50S by the motor 70, the carrier 50C as the first rotation element and the ring gear 50R as the second rotation element rotate at a gear ratio corresponding to the gear ratio.

Since the first rotating element of the planetary gear mechanism 50 is connected to the first cam 42 via the first power transmission mechanism 60A, the rotational speed (N _{cam 1} ) of the first cam 42 is the same as that of the planetary gear mechanism 50. The first rotating element rotates at a rotational speed corresponding to the speed transmission ratio (N _{cam 1} / N ₁ ) of the first power transmission mechanism 60A with respect to the rotational speed (N ₁ ).
Further, since the second rotating element of the planetary gear mechanism 50 is connected to the second cam 44 via the second power transmission mechanism 60B, the rotational speed (N _{cam 2} ) of the second cam 44 is the planetary gear mechanism. With respect to the rotation speed (N ₂ ) of the 50 second rotation element, the rotation rotates at a rotation speed corresponding to the speed transmission ratio (N _{cam 2} / N ₂ ) of the second power transmission mechanism 60B.

These first and second power transmission mechanisms 60A and 60B are in a predetermined rotation control of the third rotation element by the actuator 70, that is, when the third rotation element is rotated or stopped at a predetermined speed (constant speed). In addition, the speed transmission ratio is set so that the first cam 42 and the second cam 44 rotate at a constant speed.
The speed transmission ratio is the reciprocal of the gear ratio (gear ratio) as shown in the following equation (1) where the rotational speed Nin of the input element, the number of teeth Zin, the rotational speed Nout of the output element, and the number of teeth Zout. Defined.
Speed transmission ratio = Nout / Nin = Zin / Zout = 1 / Gear ratio (speed ratio) (1)

In each embodiment shown here, since carrier 50C which is the 1st rotation element is connected with the 1st cam 42 via the 1st parallel gear mechanism 61 of 60A of 1st power transmission mechanisms, The rotational speed (N _{cam 1} ) is a rotational speed corresponding to the speed transmission ratio (N _{cam 1} / N _C ) of the first parallel gear mechanism 61 with respect to the rotational speed (N _C ) of the carrier 50 C of the planetary gear mechanism 50. Rotate with.
Further, since the ring gear 50R, which is the second rotating element, is connected to the second cam 44 via the second parallel gear mechanism 62 of the second power transmission mechanism 60B, the rotational speed of the second cam 44 (N _{cam 2} ) Rotates at a rotational speed corresponding to the speed transmission ratio (N _{cam 2} / N _R ) of the second parallel gear mechanism 62 with respect to the rotational speed (N _R ) of the ring gear 50 R of the planetary gear mechanism 50.

  These first and second power transmission mechanisms 60A, 60B rotate the sun gear 50S, which is the third rotating element, by a predetermined rotation by the actuator 70, that is, rotate the sun gear 50S at a predetermined speed (constant speed). The speed transmission ratio is set so that the first cam 42 and the second cam 44 rotate at a constant speed when stopped.

As a result, the rotation state of the third rotation element by the actuator 70 is changed, that is, the rotation speed of the third rotation element is changed (if the third rotation element is in the stopped state, the rotation is performed, or the third rotation element is predetermined). If the rotational speed is changed from the predetermined rotational speed), the first cam 42 is directly connected to the movable sheave 12, and the rotational speed does not change with respect to the movable sheave 12. Therefore, the first cam 42 and the second cam 42 A differential rotation occurs with the cam 44, the second cam 44 rotates relative to the first cam 42, and the relative rotation phase between the first cam 42 and the second cam 44 is changed. Thereby, the movable sheave 12 moves in the axial direction, and the gear ratio of the continuously variable transmission 5 is adjusted.
In each embodiment, the gear ratio is adjusted by the same configuration.

As shown in FIG. 2, in the mechanical pulley moving mechanism 30 according to each embodiment, the planetary gear mechanism 50 is separated from the rotation center (first axis) SC1 of the primary pulley 6 (movable sheave 12) with respect to the radial direction. In addition, it is disposed on another rotational center (second axis) SC2 parallel to the rotational center SC1.
In the planetary gear mechanism 50, the carrier 50 </ b> C is coupled to the first cam 42 via the first parallel gear mechanism 61 of the power transmission mechanism 60, and the ring gear 50 </ b> R is connected to the second cam via the second parallel gear mechanism 62 of the power transmission mechanism 60. The rotation shaft of the sun gear 50S is coupled to the cam 44 and is coupled to the rotation shaft of the electric motor 70 as an actuator.

In the first parallel gear mechanism 61, the number of teeth of the first gear 61a coupled to the first cam 42 is Z _G1 , and the number of teeth of the second gear 61b coupled to the carrier 50C is Z _G2. 61, when the first gear 61a is an input element and the second gear 61b is an output element, the speed transmission ratio R1 by the first parallel gear mechanism 61 is the rotational speed of the second gear 61b as shown in the following equation (2). N _G2 (= rotational speed of the carrier 50C) and the rotational speed N _G1 of the first gear 61a (= rotational speed N _{cam 2} of the first cam 42) (N _G2 / N _G1 ), and the gears 61a and 61b It is determined by the number of teeth Z _G1 and Z _G2 .
R1 = _NG2 / _NG1 = _ZG1 / _ZG2 (2)

Similarly, in the second parallel gear mechanism 62, the number of teeth of the third gear 62a coupled to the second cam 44 is Z _G3 , the number of teeth of the fourth gear 62b coupled to the ring gear 50R is Z _G4, and the second In the parallel gear mechanism 62, when the fourth gear 62b is an input element and the third gear 62a is an output element, the speed transmission ratio R2 by the second parallel gear mechanism 62 is, as shown in the following equation (3), the third gear 62a. Of the rotation speed N _G3 (= the rotation speed N _{cam 2} of the second cam 44) and the rotation speed N _G4 of the fourth gear 62b (= the rotation speed N _{R of the} ring gear 50R) (N _G1 / N _G2 ) It is determined by the number of teeth Z _G3 and Z _G4 of each gear 62a and 62b.
R2 = _NG3 / _NG4 = _ZG4 / _ZG3 (3)

Here, assuming that the gear ratio is fixed when the electric motor 70 is stopped, the alignment chart of the planetary gear mechanism 50 is as shown by a solid line L in FIG. In FIG. 3, C indicates the carrier 50C, S indicates the sun gear 50S, R indicates the ring gear 50R, and α indicates the gear ratio of the planetary gear mechanism 50. As shown in FIG. 3, the ratio between the rotation speed _{N C} of the rotational speed _{N R} and the carrier 50C of the ring gear 50R _(N R / _{N C)} becomes 1 + alpha.
In the collinear diagram of FIG. 3, the case of Z _G3 / Z _G4 = 1 is shown for easy understanding.

Further, the rotational speed ratio R3 (= N _R ) between the rotational speed N _R of the ring gear 50R (the rotational speed N _G4 of the fourth gear 62b) and the rotational speed N _{C of the} carrier 50C (= the rotational speed N _G2 of the second gear 61b). / N _C ) is determined by the number of teeth Z _S of the sun gear 50S and the number of teeth Z _R of the ring gear 50R, and is expressed by the following equation (4).
R3 = N _R / N _C = (Z _S + Z _R ) / Z _R = 1 + α (4)

If the rotation is transmitted from the first cam 42 to the second cam 44 via the first power transmission mechanism 60A, the planetary gear mechanism 50, and the second power transmission mechanism 60B, the rotational speed of the first cam 42 (N _{cam 1} ) Is shifted by the speed transmission ratio R1 (= N _G2 / N _G1 ) of the first power transmission mechanism 60A and transmitted to the planetary gear mechanism 50, and further the rotational speed ratio R3 (= N _R / of the planetary gear mechanism 50). N _C = 1 + α) and is transmitted to the second power transmission mechanism 60B. Further, the speed is changed by the speed transmission ratio R2 (= N _G3 / N _G4 ) of the second power transmission mechanism 60B and transmitted to the second cam 44. Is done.
The rotational speed (N _{cam 2} ) of the second cam 44 is expressed by the following equation (5).
N _{cam 2} = N _{cam 1} × R1 × R3 × R2 (5)

Here, in order to make the transmission ratio of the continuously variable transmission 5 constant, the first cam 42 and the second cam 44 rotate at the same speed in the same direction, that is, the relationship of (N _{cam 1} = N _{cam 2} ). It is necessary to satisfy. Therefore, the equation (5) can be converted into the following equation (6). What is necessary is just to set speed transmission ratio R1, R2 or a gear ratio so that Formula (6)-(6C) may be satisfy | filled.
R1 × R3 × R2 = 1 (6)
(N _G2 / N _G1 ) · (1 + α) · (N _G3 / N _G4 ) = 1 (6A)
(Z _G1 / Z _G2 ) · (1 + α) · (Z _G4 / Z _G3 ) = 1 (6B)
(Z _G2 / Z _G1 ) / (Z _G4 / Z _G3 ) = 1 + α> 1 (6C)
Further, since the first gear 61a and the third gear 62a are coaxial and the second gear 61b and the fourth gear 62b are coaxial, the following equation (7) is established.
Z _G1 + Z _G2 = Z _G3 + Z _G4 (7)
From the equations (6C) and (7), the following equation (8) is established.
Z _G1 <Z _G3 and Z _G2 > Z _G4 (8)
Accordingly, the third gear 62a has a larger number of teeth and a larger diameter than the first gear 61a, and the second gear 61b has a larger number of teeth and a larger diameter than the fourth gear 62b.

  If the speed transmission ratios R1 and R2 of the parallel gear mechanisms 61 and 62 are set as described above, the rotation of the electric motor 70 is stopped and the sun gear 50S of the planetary gear mechanism 50 is set in a fixed state, so that the second cam 44 Does not rotate relative to the first cam 42 and maintains a constant rotational phase. That is, the overall length of the torque cam mechanism 40 is not changed, and the speed ratio of the continuously variable transmission 5 is kept constant.

  On the other hand, when the electric motor 70 is operated so that the sun gear 50S rotates in the same direction (positive direction) as the carrier 50C and the ring gear 50R (see the arrow of the speed change a), the alignment chart of the planetary gear mechanism 50 is as follows. 3, the ring gear 50R (that is, the second cam 44) of the planetary gear mechanism 50 is at a lower speed than before the operation of the electric motor 70, and the second cam 44 is the first cam 42. And the relative rotation phase is changed. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

  Conversely, when the electric motor 70 is operated so that the sun gear 50S rotates in the opposite direction (negative direction) to the carrier 50C or the ring gear 50R (see the arrow of the shift b), the alignment chart of the planetary gear mechanism 50 is shown in FIG. The ring gear 50R (that is, the second cam 44) of the planetary gear mechanism 50 is at a higher speed than before the operation of the electric motor 70, and the second cam 44 is relative to the first cam 42. Rotate to change the relative rotational phase. Thereby, the total length of the torque cam mechanism 40 is changed, and the gear ratio is changed.

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

  In the mechanical pulley moving mechanism 30 according to each 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. . In addition, when the transmission gear ratio is fixed, the first cam 42 and the second cam 44 rotate at the same speed in the same direction and do not rotate relative to each other, so that friction due to rotation does not occur between these two members. For this reason, generation | occurrence | production of power transmission loss is suppressed.

  Further, when changing the gear ratio, the rotational speed of the electric motor 70 is changed to rotate the second cam 44 relative to the first cam 42 (and hence the movable sheave 12), so that the first cam 42 and the second cam The relative rotational phase with respect to 44 is changed. At this time, the thrust of the belt 26 received by the second cam 44 toward one end side (the right side in the figure) of the second cam 44 via the first cam 42 is applied to the thrust bearing 46, and friction due to relative rotation occurs. Since the speed change 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, as shown in FIG. 2, the first parallel gear mechanism 61 is disposed on the outer periphery of the first cam 42, and the planetary gear mechanism 50 and the second parallel gear mechanism 62 are disposed on the outer periphery of the second cam 44. Therefore, the pulley apparatus 6 and the continuously variable transmission 5 can be reduced in size in the axial direction. Further, since the electric motor 70 as an actuator is also connected to the sun gear 50S of the planetary gear mechanism 50, the other side (the outer peripheral side of the first cam 42), the fixed sheave 8, and the movable sheave 12 with respect to the planetary gear mechanism 50. This pulley apparatus 6 and the continuously variable transmission 5 can be downsized in the axial direction.

  Hereinafter, more specific configuration examples of the main part of the pulley device for continuously variable transmission according to the present invention will be described as a first embodiment and a second embodiment with reference to FIGS. 4 and 5. In addition, the same code | symbol is attached | subjected to the same member in 1st and 2nd embodiment, and description about these is abbreviate | omitted or simplified in 2nd Embodiment.

[First Embodiment]
As shown in FIG. 4, the primary pulley 6 as a continuously variable transmission pulley device includes a fixed sheave 8 and a movable sheave 12 with a belt 26 interposed therebetween, and the movable sheave 12 sandwiches the belt 26. From one axial side (right side in the figure), it is integrally formed with the fixed sheave 8 and is externally fitted to a rotary shaft (pulley shaft) 10 extending in the other direction. Further, between the movable sheave 12 and the rotating shaft 10, for example, a spline mechanism 12 </ b> A with a ball or a roller interposed is interposed. In the present embodiment, the first cam 42 is formed integrally with the hollow shaft portion of the movable sheave 12. As shown in FIG. 4, one axial direction (right direction in the figure) is indicated by R, and the other axial direction (right direction in the figure) is indicated by L.

  The main body portion of the primary pulley 6 is assembled in advance into a pulley assembly in which a movable sheave 12 is assembled to a rotating shaft 10 of a fixed sheave 8. The planetary gear mechanism 50 is also assembled in a state where the second gear 61b is assembled to the carrier 50C in advance and a planetary gear assembly including the sun gear 50S and the ring gear 50R. Although not shown, the pulley assembly is assembled to the transmission casing C from the one direction R side toward the other direction L side.

Each component of the mechanical pulley moving mechanism 30 is assembled to the pulley assembly of the primary pulley 6 and the planetary gear assembly.
Hereinafter, the configuration of the mechanical pulley moving mechanism 30 according to the present embodiment will be described in consideration of the assembly order with respect to the pulley assembly.

  The pulley assembly and the planetary gear assembly include the first gear 61a of the first parallel gear mechanism 61, the second cam 44, and the second parallel gear mechanism 62 from the side near the movable sheave 12 on the back surface 13 of the movable sheave 12. The third gear 62a is arranged concentrically on the rotation center SC1 of the primary pulley 6 and assembled in this order. The planetary gear assembly is also assembled after the first gear 61a is assembled.

  A slide allowing mechanism 80 is interposed between the outer periphery of the movable sheave 12 and the inner periphery of the first gear 61a. The outer periphery of the slide allowing mechanism 80 is engaged in a recess on the inner periphery of the first gear 61a, and is locked to the first gear 61a by a stopper ring 81 in the axial direction.

  A ball 48 is mounted on the second cam surface 44 a of the second cam 44. By assembling the second cam 44, the first cam surface 42 a of the first cam 42 and the second cam surface 44 a of the second cam 44 are connected. A ball 48 is sandwiched therebetween.

  Further, a bearing 49 that allows the rotation of the second cam 44 relative to the rotation shaft 10 is interposed between the rotation shaft 10 and the second cam 44. Further, a ball bearing (main bearing) 34 is assembled to the outer peripheral surface of the rotating shaft 10 by, for example, press-fitting from one direction R side of the second cam 44 with a thrust bearing 46 interposed therebetween. The ball bearing 34 is fastened in the axial direction by a nut 92 screwed onto the rotary shaft 10 from one direction R side, and the axial position is regulated. The outer diameter of the second cam 44 is set larger than the outer diameter of the ball bearing 34. In addition, since the transmission casing C is assembled from the one direction R side to the other direction L side after the ball bearing 34 is assembled, the ball bearing 34 is a predetermined part of the wall 90 (part constituting a part of the transmission casing C). The rotating shaft 10 is supported at the position.

  A cylindrical portion 611 extends from the first gear 61a on the one direction R side. The cylindrical portion 611 is disposed concentrically with the rotation center SC1 of the movable sheave 12. The outer diameter of the cylindrical portion 611 is set to be smaller than the distance from the rotation center SC1 to the rotation region of the second gear 61b that meshes with the first gear 61a.

The second cam 44 has a flange-like flange portion 442 on the outer periphery of the end portion on the other direction L side, and extends outward so as to be close to the inner periphery of the cylindrical portion 611 of the first gear 61a. ing.
Further, the annular coupling base portion 621 of the third gear 62 a is accommodated between the outer peripheral portion of the intermediate portion in the axial direction of the flange portion 442 of the second cam 44 on the one direction R side and the inner periphery of the cylindrical portion 611. A storage space 625 is formed.

  The third gear 62a has an annular coupling base 621 formed on the inner peripheral side thereof. That is, the third gear 62 a has an annular connection base 621 on the inner peripheral side and a gear part (external teeth) 622 on the outer peripheral side, and an intermediate part connecting the connection base 621 and the gear part 622. 623. The connection base portion 621 and the gear portion 622 protrude toward the other side L in the axial direction with respect to the intermediate portion 623. Conversely, the other direction L side of the intermediate part 623 is recessed in a concave shape to form an annular groove.

  A gear support bearing 600 is interposed between the outer peripheral portion of the second cam 44 (the outer peripheral portion of the coupling base portion 621 of the third gear 62 a) and the cylindrical portion 611. The gear support bearing 600 supports the first gear 61 a on the second cam 44 and the rotating shaft 10 through the cylindrical portion 611. The gear support bearing 600 rotates and supports the first gear 61a while restricting the movement of the first gear 61a in the axial direction, and a ball bearing is used here.

An outer race of the ball bearing 600 is provided in an inwardly-opening annular groove 601 formed on the inner peripheral surface of the cylindrical portion 611, and is a stopper ring (second regulating member) attached to the cylindrical portion 611 from one direction R side. ) 620 restricts the movement in the axial direction.
The inner race of the ball bearing 600 is installed in an outwardly-opening annular groove 602 formed on the outer peripheral surface of the coupling base 621, and a side wall surface of the outward-opening annular groove 602 and a flange portion 442 that faces the side wall surface. It is sandwiched between the opposing surfaces.

The third gear 62a is connected so that the connecting base portion 621 is accommodated in the accommodating space 625, and the inner peripheral portion of the connecting base portion 621 is integrally rotated with the outer peripheral portion of the second cam 44 by a spline mechanism or the like (relative rotation impossible). Is done. Further, the third gear 62a moves the third gear 62a from the one direction R side to the other direction L side after engaging the outer race of the ball bearing 600 in the inwardly open annular groove 601 of the cylindrical portion 611. The ball bearing 600 is assembled so that the inner race of the ball bearing 600 is engaged in the outwardly-opening annular groove 602 formed on the outer peripheral surface of the coupling base 621. At this time, positioning at the time of assembling the third gear 62a is also performed by the engagement between the inner race and the side wall surface of the outward opening annular groove 602.
A nut (first regulating member) 624 is screwed onto the outer periphery of the second cam 44 on one side R side of the assembled third gear 62a, and the third gear 62a is fastened in the axial direction by the nut 624. It is regulated at a predetermined position.

Since the continuously variable transmission pulley apparatus of the present embodiment is configured as described above, the apparatus can be manufactured by the following procedure (assembly method).
First, the pulley assembly is assembled to the transmission casing C from one direction R side to the other direction L side.

  Then, the first gear 61a is arranged on the first axis SC1 with respect to the pulley assembly and is advanced from one direction R side to the other direction L side, and the first gear 61a is placed on the outer periphery of the first cam 42. Incorporate (first step). At this time, a slide allowing mechanism 80 is interposed between the first cam 42 and the first gear 61 a and is locked by the stopper ring 81.

  Next, a planetary gear assembly in which the second gear 61b is assembled to the planetary gear mechanism 60 is disposed on the second axis SC2 and is advanced from one direction R side to the other direction L side, and the second gear 61b is inserted. The gear teeth 61bt of 61b are engaged with the gear teeth 61at of the first gear 61a (second step). Since the outer diameter of the cylindrical portion 611 of the first gear 61a is set smaller than the distance from the rotation center SC1 to the rotation region of the second gear 61b meshing with the first gear 61a, the cylindrical portion 611 is a planetary gear assembly. It will not interfere with the assembly.

  Next, the second cam 44 is arranged on the first axis SC <b> 1 so as to enter the outer periphery of the rotary shaft 10 from the one direction R side toward the other direction L side, and toward the one direction R side of the first cam 42. Incorporate (third step). At this time, a bearing 49 is interposed between the rotary shaft 10 and the second cam 44.

  Next, a ball bearing 600 as a gear support bearing is arranged on the first axis SC1 and is advanced from one direction R side to the other direction L side, and the outer race of the ball bearing 600 is moved to the first cam 42. It fits in the inward opening annular groove 601 formed in the inner peripheral surface of the cylindrical part 611 (4th process).

  Next, the stopper ring (second restricting member) 620 is disposed on the first axis SC1 and is advanced from the one direction R side toward the other direction L side and fixed to the cylindrical portion 611 (fifth step). .

  Next, the third gear 62a is arranged on the first axis SC1 to enter from the one direction R side toward the other direction L side, and the gear teeth 62at of the third gear 62a are moved to the gear teeth of the fourth gear 62b. The fastening base 621 is accommodated in the accommodation space 625 while being engaged with 62bt. At the same time, the inner race of the ball bearing 600 is fitted into the outward opening annular groove 602 of the fastening base 621 (sixth step).

  Then, a nut (first regulating member) 624 is arranged on the first axis SC1 and entered from the one direction R side toward the other direction L side, and the nut 624 is screwed and attached to the second cam 44. The third gear 62a is fastened in the axial direction (seventh step).

Further, at an appropriate stage after the third step, the ball bearing 34 as the main bearing is disposed on the first axis SC1, and the one direction R of the second cam 44 from the direction R side with the thrust bearing 46 interposed therebetween. A main bearing mounting step of press-fitting and fixing to the rotary shaft 10 on the side is performed. It is preferable that the main bearing mounting step is performed immediately after the third step and the second cam 44 is fastened in the axial direction because the subsequent workability can be improved.
Moreover, the transmission casing C provided with the wall part 90 which supports the ball bearing 34 is assembled | attached after a 7th process.

In this way, the mechanical pulley moving mechanism 30 can be assembled to the back surface 13 side of the movable pulley 12 of the primary pulley 6 without hindrance.
That is, in order to make the first cam 42 and the second cam 44 constant speed when the transmission gear ratio is fixed (non-shift state), the third gear 62a on the first axis SC1 is the first gear 61a. The second gear 61b on the second axis SC2 must have a larger diameter than the fourth gear 62b. For this reason, depending on the structure of the mechanical pulley moving mechanism 30, it is difficult to assemble the transmission casing C from the one direction R side to the other direction L side.

  In the present embodiment, the first parallel shaft gear mechanism 61 and the second parallel shaft gear mechanism 62 are arranged in this order from the movable sheave 12 toward the one direction R side, and as described above, the third gear 62a. Is larger in diameter than the first gear 61a, and the second gear 61b is larger in diameter than the fourth gear 62b. A cylindrical portion 611 is provided concentrically with the movable sheave 12 on the one direction R side of the first gear 61a. The cylindrical portion 611 is a distance from the first rotation axis SC1 to the rotation region of the second gear 61b. Has a smaller outer diameter.

  Further, the flange portion 442 extends outward on the outer periphery of the second cam 44 so as to be close to the inner periphery of the cylindrical portion 611. Further, a gear support bearing 600 is interposed between the outer peripheral portion of the second cam 44 and the cylindrical portion 611, and the gear support bearing 600 restricts at least the movement of the first gear 61a in the axial direction in the first direction. The gear 61a is rotatably supported.

  In addition, on one side R side with respect to the flange portion 442, an accommodation space 625 is formed between the outer periphery of the second cam 44 and the inner periphery of the cylindrical portion 611, and the accommodation space 625 on the inner periphery side of the third gear 62a. An annular connection base portion 621 that is connected to the second cam 44 so as to rotate integrally with the second cam 44 is disposed, and a nut (first restriction member) 624 is provided on the second cam 44 on one side R side of the connection base portion 621. The stopper ring (second regulating member) 620 regulates the movement of the coupling base 621 in the axial direction.

In this manner, the flange portion 442 that supports the bearing 600 and the fastening base portion 621 of the third gear 62a is formed to increase the diameter, and the outer diameter of the second cam 44 is larger than the inner diameter of the first gear 61a. Therefore, assembling requires some ideas. For example, as described above as the assembling method, the first gear 61a is assembled before the second cam 44 or the third gear 62a attached to the outer periphery of the second cam 44 is installed. Therefore, the first gear 61a can be assembled without interfering with the second cam 44 and the third gear 62a.
Further, since the planetary gear assembly in which the second gear 61b is assembled to the planetary gear mechanism 60 is assembled before the third gear 62a is attached, the planetary gear assembly can be assembled without interfering with the third gear 62a. it can.

  In addition, since a ball bearing is used for the gear support bearing 600, the gear support bearing 600 is provided so that expansion of the device in the axial direction can be suppressed. Therefore, the third gear 62a is restricted from moving in the axial direction. A nut 624 having an axial width can be used as one restricting member, and the third gear 62a can be firmly fastened in the axial direction by screwing the nut 624 to the outer periphery of the second cam 44.

  Further, by utilizing the spaces along the respective surfaces of the flange portion 442, the cylindrical portion 611, and the fastening base portion 621, an oil passage can be configured as indicated by an arrow in FIG. 4, which can improve lubricity. it can.

  That is, the lubricating oil inside the rotating shaft 10 is supplied between the outer periphery of the rotating shaft 10 and the inner periphery of the hollow shaft portion of the movable sheave 12 through an oil hole 10 a formed in the rotating shaft 10. It enters between the outer periphery of the hollow shaft portion of the movable sheave 12 and the inner periphery of the cylindrical portion 611 of the first gear 61a from between the surfaces 42a and 44a. During this time, the lubricating oil lubricates each part.

  A part of the lubricating part that has entered the inside of the cylindrical part 611 further passes through the slide allowing mechanism 80 and enters between the movable sheave 12 and the first gear 61a, and moves outward by centrifugal force. Lubricate each part.

  The remaining portion of the lubrication part that has entered the inside of the cylindrical part 611 passes through the bearing 600 while being guided by the surface of the flange part 442, and between the cylindrical part 611 and the surface on the other direction L side of the third gear 62a. Passing between the movable sheave 12, the first gear 61a and the third gear 62a, the parts are lubricated while moving outward by centrifugal force.

[Second Embodiment]
As shown in FIG. 5, in the present embodiment, the gear support bearing that supports the first gear 61 a on the second cam 44 and the rotating shaft 10 through the cylindrical portion 611 and the surrounding configuration are different from the first embodiment.

That is, in this embodiment, the first and second thrust bearings 631 and 632 are provided as gear support bearings.
A first wall surface 635 is formed in the other direction L side inside the cylindrical portion 611 toward the one direction R. A second wall surface 443 is formed on the flange portion 442 so as to face the first wall surface 635. The first thrust bearing 631 is interposed between the first wall surface 635 and the second wall surface 443.

  A wall member 630 is fixed by a fixing member 641 to a portion on one side R side inside the cylindrical portion 611. The wall member 630 is formed with a third wall surface 636 facing the other direction L. A fourth wall surface 444 is formed on the flange portion 442 so as to face the third wall surface 636. The second thrust bearing 632 is interposed between the third wall surface 636 and the fourth wall surface 444.

Further, a stopper ring (first restricting member) 634 is locked to one direction R side of the third gear 62a, and the axial movement of the third gear 62a is restricted by the stopper ring 634.
Other configurations are the same as those of the first embodiment.

The pulley device for continuously variable transmission of the present embodiment is configured as described above, and therefore the same procedure as in the first embodiment, except that the third step and the fourth step of the first embodiment are changed. The device can be manufactured by the (assembly method).
Hereinafter, only the third step and the fourth step will be described.

  In the present embodiment, as the third step, the first thrust bearing 631 is installed on the second wall surface 443 of the flange portion 442 of the second cam 44, and the second thrust bearing 632 is mounted on the fourth wall surface 444 of the flange portion 442. After the installation, the second cam 44 is arranged on the first axis SC1 and enters the outer periphery of the rotary shaft 10 from the one direction R side toward the other direction L side, and the one direction R of the first cam 42 is obtained. Side (third step). At this time, a bearing 49 is interposed between the rotary shaft 10 and the second cam 44. A second cam 44 is disposed on the first axis and is made to enter from the one direction side toward the other direction side, and is incorporated into the one direction side of the first cam member, so that the first thrust A bearing is interposed between the first wall surface and the second wall surface.

In the next fourth step, the wall member 630 is advanced from the one direction R side toward the other direction L side, and the second thrust bearing 632 is interposed between the third wall surface 636 and the fourth wall surface 444.
Also in the present embodiment, substantially the same effects as in the first embodiment can be obtained by such an apparatus configuration and method configuration.

[Others]
In each of the above embodiments, the first rotating element connected to the first cam member via the power transmission mechanism is used as the carrier, the second rotating element connected to the second cam member is used as the ring gear, and the actuator. The third rotating element coupled to the sun gear is a sun gear. However, according to the present invention, the power transmission mechanism rotates in unison with the first cam member and the first rotating element. A first parallel gear mechanism comprising a second gear meshing with one gear, and rotating integrally with the second cam member between the second cam member and the planetary gear mechanism and larger than the first gear; As long as it has a second parallel gear mechanism comprising a third gear having a diameter and a fourth gear that rotates integrally with the second rotating element and meshes with the third gear, each rotating element of the planetary gear mechanism , Connection with first cam member, second cam member and actuator Only together can be adopted as appropriate.

  In each of the above embodiments, the speed ratio of the continuously variable transmission 5 is set to be constant by setting the electric motor 70, which is an actuator, to a rotation stop state at a rotation speed of zero. The electric motor 70 may be controlled while rotating. In this case, control in a region where the motor efficiency is low can be avoided.

  Furthermore, in each of the above embodiments, the primary pulley 6 is equipped with a mechanical pulley moving mechanism, but the secondary pulley 14 may be equipped with a mechanical pulley moving mechanism. Further, a mechanical pulley moving mechanism can be provided on both the primary pulley 6 and the secondary pulley 14.

2 Drive source 5 Continuously variable transmission 6 Primary pulley (pulley device for continuously variable transmission)
8 Fixed sheave of primary pulley 6 10 Rotating shaft (pulley shaft) of primary pulley 6
DESCRIPTION OF SYMBOLS 12 Movable sheave of primary pulley 6 14 Secondary pulley 16 Fixed sheave of secondary pulley 14 18 Drive shaft of secondary pulley 14 20 Movable sheave of secondary pulley 14 22 Spring constituting thrust adjusting mechanism 24 Cam mechanism constituting thrust adjusting mechanism 26 Belt (Endless strip member)
30 Mechanical pulley moving mechanism 34 Ball bearing (main bearing)
40 torque cam mechanism 42 first cam 42a first cam surface 44 second cam 44a second cam surface 46 thrust bearing 48 ball 50 planetary gear mechanism 50S, S sun gear 50C, C carrier 50R, R ring gear 50P planetary gear 60A first power transmission mechanism 60B Second power transmission mechanism 61 First parallel shaft gear mechanism (first parallel gear mechanism)
61a First gear 61b Second gear 62 Second parallel shaft gear mechanism (second parallel gear mechanism)
62a Third gear 62b Fourth gear 70 Electric motor as actuator 80 Slide permissible mechanism 442 Flange 443 Second wall surface 444 Fourth wall surface 600 Gear support bearing (ball bearing)
601 Inwardly opening annular groove 602 Outwardly opening annular groove 611 Cylindrical portion 621 Connection base 624 Nut (first regulating member)
625 Accommodating space 630 Wall member 631 First thrust bearing 632 Second thrust bearing 634 Stopper ring (first regulating member)
635 1st wall surface 636 3rd wall surface 641 Fixing member SC1 The rotation center (1st axis) of the rotating shaft 10
SC2 Center of rotation of planetary gear mechanism 50 (second axis)

Claims (11)

A movable pulley 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 is disposed on one side in the axial direction across the belt. A continuously variable transmission pulley apparatus having a mechanical pulley moving mechanism that moves a sheave in an axial direction with respect to a fixed sheave arranged on the other side in the axial direction to adjust a gear ratio,
The mechanical pulley moving mechanism is
The first cam member has first and second cam members arranged in series on the same axis as the movable sheave with the cam surfaces slidingly contacted, and the first cam member is directly connected to the one-direction side of the movable sheave. The second cam member is connected to the pulley shaft to which the fixed sheave is coupled on the one-direction side further than the first cam member so as to be relatively rotatable and axially non-movable. A torque cam mechanism that changes a total length when the relative rotation phase of the cam member with respect to the first cam member is changed, moves the movable sheave in an axial direction, and adjusts a thrust force;
An actuator for changing or maintaining the relative rotational phase of the second cam member;
It has three rotating elements, a sun gear, a carrier, and a ring gear, and among these rotating elements, the first rotating element is connected to the first cam member via the first power transmission mechanism, and the second rotating element An element is connected to the second cam member via a second power transmission mechanism, a third rotating element is connected to the actuator, and is parallel to a first axis that is the rotation center of the fixed sheave and the movable sheave. A planetary gear mechanism disposed on the second axis,
The first power transmission mechanism includes a first gear that rotates integrally with the first cam member, and a second gear that rotates integrally with the first rotating element and meshes with the first gear. 1 parallel shaft gear mechanism,
The second power transmission mechanism includes a third gear that rotates integrally with the second cam member, and a fourth gear that rotates integrally with the second rotating element and meshes with the third gear. 2 parallel shaft gear mechanism,
The first and second power transmission mechanisms are configured so that the first and second cam members are in the same direction when the gear ratio is fixed so that the relative rotational phase of the first and second cam members is constant by the actuator. A pulley device for a continuously variable transmission, wherein a speed transmission ratio is set so as to rotate at a constant speed. The first rotating element is the carrier;
The second rotating element is the ring gear;
The pulley device for a continuously variable transmission according to claim 1, wherein the third rotating element is the sun gear. From the movable sheave toward the one direction side, the first parallel shaft gear mechanism and the second parallel shaft gear mechanism are arranged in this order.
The third gear has a larger diameter than the first gear and the second gear has a larger diameter than the fourth gear;
A cylindrical portion extending concentrically with the movable sheave on the one-direction side of the first gear and having an outer diameter smaller than a distance from the first rotation axis to the rotation region of the second gear;
A flange portion extending outwardly on the outer periphery of the second cam member so as to be close to the inner periphery of the cylindrical portion;
A gear support bearing that is interposed between an outer peripheral portion of the second cam member and the cylindrical portion, and that rotatably supports the first gear while restricting at least movement of the first gear in the axial direction;
An accommodation space formed between the outer peripheral portion of the second cam member and the inner periphery of the cylindrical portion on the one-direction side of the flange portion;
An annular coupling base formed on the inner peripheral side of the third gear, which is positioned in the housing space and coupled to rotate integrally with the second cam member;
The first restricting member that is mounted on the second cam member on the one direction side of the connection base and restricts the movement of the connection base in the axial direction is provided. Or the pulley apparatus for continuously variable transmissions of 2. The pulley apparatus for a continuously variable transmission according to any one of claims 1 to 3, wherein an axial movement allowance mechanism is interposed between the first cam member and the first gear. . The gear support bearing is a ball bearing,
The outer race of the ball bearing is mounted in an inwardly-opening annular groove formed on the inner peripheral surface of the cylindrical portion, and is axially moved by a second restricting member mounted on the cylindrical portion from the one direction side. Restricted movement,
An inner race of the ball bearing is installed in an outwardly-opening annular groove formed on an outer peripheral surface of the connection base, and a side surface of the outward-opening annular groove and an opposing surface of the flange portion facing the side wall surface The pulley device for a continuously variable transmission according to any one of claims 1 to 4, wherein the pulley device is continuously clamped. The pulley device for a continuously variable transmission according to claim 5, wherein the first restricting member is a nut that is screwed and fastened to the second cam member. The gear support bearings are first and second thrust bearings,
The first thrust bearing is formed on the inner side of the cylindrical portion on the other direction side so as to face in the one direction, and the flange portion is formed to face the first wall surface. Interposed between the second wall surface and
The second thrust bearing opposes the third wall surface facing the other direction of the wall member fixed to the one-direction side portion inside the cylindrical portion by the fixing member, and the flange portion facing the third wall surface. The pulley apparatus for continuously variable transmission according to any one of claims 1 to 4, wherein the pulley apparatus is interposed between the fourth wall surface formed as described above. A main bearing that rotatably supports the pulley shaft is attached to the one end side of the second cam member,
A thrust bearing is interposed between the second cam member and the inner race of the main bearing,
The continuously variable transmission pulley apparatus according to any one of claims 1 to 7, wherein an inner diameter of the coupling base is formed larger than an outer diameter of the main bearing. A pulley assembly method for a continuously variable transmission according to claim 5,
With respect to a pulley assembly in which the movable sheave is assembled to the pulley shaft of the fixed sheave, and the first cam member is directly coupled to the movable sheave with the cam surface directed in the one direction. A first step of disposing one gear on the first axis and entering from the one direction side toward the other direction side, and incorporating the first gear on the outer periphery of the first cam member;
A planetary gear assembly in which the second gear is assembled to the planetary gear mechanism is disposed on the second axis and is advanced from the one direction side to the other direction side, and the second gear is moved to the second direction. A second step for meshing with the first gear;
A third step of disposing the second cam member on the first axis and entering from the one direction side toward the other direction side and incorporating the second cam member into the one direction side of the first cam member; ,
The ball bearing as the gear support bearing is disposed on the first axis and is advanced from the one direction side toward the other direction side, and the outer race of the ball bearing is moved to the first cam member. A fourth step of fitting into the inwardly opening annular groove;
A fifth step of disposing the second restricting member on the first axis, entering from the one direction side toward the other direction side, and fixing to the cylindrical portion;
The third gear is arranged on the first axis and is made to enter from the one direction side toward the other direction side so that the fastening base portion is accommodated in the accommodation space and the outward opening of the fastening base portion is annular. A sixth step of fitting the inner race of the ball bearing in the groove;
The first restricting member is disposed on the first axis and is made to enter from the one direction side to the other direction side of the connection base portion, and the first restricting member is attached to the second cam member. A method for assembling a pulley apparatus for a continuously variable transmission, wherein the seventh step is sequentially performed. An assembly method for a continuously variable transmission pulley device according to claim 7,
With respect to a pulley assembly in which the movable sheave is assembled to the pulley shaft of the fixed sheave, and the first cam member is directly coupled to the movable sheave with the cam surface directed in the one direction. A first step of disposing one gear on the first axis and entering from the one direction side toward the other direction side, and incorporating the first gear on the outer periphery of the first cam member;
A planetary gear assembly in which the second gear is assembled to the planetary gear mechanism is disposed on the second axis and is advanced from the one direction side toward the other direction side, and the second gear is moved to the second direction. A second step for meshing with the first gear;
The first thrust bearing is installed on the second wall surface of the flange portion of the second cam member, and the second thrust bearing is installed on the fourth wall surface of the flange portion, and then the second The first thrust bearing is arranged on the first axis and is made to enter from the one direction side toward the other direction side and is incorporated in the one direction side of the first cam member. A third step of interposing between the first wall surface and the second wall surface;
A fourth step of interposing the second thrust bearing between the third wall surface and the fourth wall surface by causing the wall member to enter from the one direction side toward the other direction side;
A fifth step of disposing the second restricting member on the first axis, entering from the one direction side toward the other direction side, and fixing to the cylindrical portion;
A sixth step in which the third gear is arranged on the first axis and is made to enter from the one direction side toward the other direction side, and the fastening base portion is accommodated in the accommodation space;
The first restricting member is disposed on the first axis and is made to enter from the one direction side to the other direction side of the connection base portion, and the first restricting member is attached to the second cam member. A method for assembling a pulley apparatus for a continuously variable transmission, wherein the seventh step is sequentially performed. The continuously variable transmission pulley device comprises the configuration according to claim 7,
The main bearing attaching step of press-fitting and fixing the main bearing to the pulley shaft on the one end side of the second cam member is provided after the third step. Assembly method of pulley device for continuously variable transmission.

Images