JP5099154B2 - Conical friction wheel ring type continuously variable transmission - Google Patents

Description

  The present invention includes a pair of conical friction wheels arranged parallel to each other and arranged so that the large diameter side and the small diameter side are opposite in the axial direction, and sandwiched between the inclined surfaces facing each other. The present invention relates to a conical friction ring type continuously variable transmission that has a ring that moves in the axial direction by moving the ring in the axial direction, and more particularly, relates to a speed change operation device (means) that moves the ring in the axial direction.

  Conventionally, a conical friction wheel on the input side, a conical friction wheel on the output side, and a metal ring sandwiched between inclined surfaces facing both friction wheels, the two friction wheels A conical friction ring type continuously variable transmission (hereinafter referred to as a “conical friction ring-type continuously variable transmission”) that is arranged in parallel so that the large-diameter portion and the small-diameter portion thereof are opposite in the axial direction, and the ring is moved in the axial direction. Corn ring type CVT) is known.

  As the cone ring type CVT gear shifting operation device, there are those described in Patent Document 1 and Patent Document 2 below. A speed change operation device described in Patent Document 1 includes a fork that can rotate and integrally move in the axial direction with the ring interposed therebetween, and a feed that supports the fork so as to swing in a moving direction via a pin. A nut and a feed screw shaft that feeds the feed nut in the movement direction, and by moving the feed nut in the axial direction by the feed screw shaft, the fork is tilted in the movement direction around the pin, A ring that is sandwiched and rotated between the input side friction wheel and the output side friction wheel is tilted with respect to the rotation axis. As a result, the ring becomes a helical line with respect to the friction wheel, and moves in the axial direction to be shifted.

  The speed change operation device described in the cited document 2 supports the ring rotatably on a frame supported so as to be axially movable by two parallel shafts, and supports the frame in a plane including the axes of the two friction wheels. And is supported rotatably about a rotation axis orthogonal to the axis. By tilting the frame about the rotation shaft, the ring becomes a helical line with respect to the friction wheel, and moves in the axial direction to be shifted.

JP-A-3-288049 JP-T-2006-501425

  In the speed change operation device described in Patent Document 1, the fork is arranged on the side where the ring is sandwiched between both the input side and output side friction wheels, and the fork is supported by a pin so as to be swingable. Shifting operation can be easily performed by moving the feed nut by the shaft, and by stopping the axial movement of the feed nut by the feed screw shaft, the ring is autonomously orthogonal to the rotational axis of the friction wheel. The neutral position where the shifting operation is stopped can be easily obtained because it is located on the plane.

  However, since the fork has a pin serving as a swing fulcrum for tilting the ring integrally, the pin is located upstream of the contact point of the ring with the friction wheel. The shift operation and the shift stop operation are smoothly performed. However, when the friction wheel rotates in the direction opposite to the rotation direction, the smooth shift operation and the shift stop operation are difficult. That is, the speed change operation device described in Patent Document 1 cannot be applied to a cone ring CVT that requires forward and reverse rotation.

  On the other hand, in the speed change operation device described in Patent Document 2, since the frame supporting the ring swings around the rotation shaft, the ring can be forcibly inclined with respect to the plane including the axis of both friction wheels. Even if the friction wheel rotates forward and backward, the speed change operation can be performed in the same manner. However, since the speed change operation device forcibly rotates the frame about the rotation shaft to perform the speed change operation, the speed change operation (speed change ratio) of both friction wheels on the input / output side is always detected to detect the frame. It is necessary to control the rotation angle. For example, even when the shifting operation is held at the neutral position where it is stopped, it is necessary to always control the rotation angle of the frame so as to maintain a predetermined rotation ratio.

  Therefore, the present invention allows a speed change operation regardless of the rotation direction (forward / reverse) of the friction wheel, and the ring is a conical friction ring type in which the ring is autonomously held at a predetermined position by moving and stopping in the axial direction. The object is to provide a continuously variable transmission (cone ring type CVT).

The present invention relates to a pair of conical friction wheels (22) arranged on mutually parallel axes (ll) (nn) and arranged so that the large diameter side and the small diameter side are reversed. (23), a ring (25) that is sandwiched between the opposing inclined surfaces of the two friction wheels so as to surround one of the two friction wheels, and a speed change operation means that shifts the ring in the axial direction. (60), in the conical friction wheel ring type continuously variable transmission (3),
The shift operation means (60) includes a moving member (63) capable of moving in parallel along the axial direction, which is the shift operation direction of the ring (25),
The moving member (63) includes a support member (67) (69) that is integrally arranged at least with respect to the moving direction of the moving member and that can rotatably support the ring (25),
The support member is different in position relative to the plane including the axes (l-l) (n-n) of the friction wheels (22) and (23) according to the rotation direction of the ring (25). The ring is positioned and supported in the axial direction on the side close to the upstream side of rotation with respect to the contact portion held between the friction wheels.
In the conical friction wheel ring type continuously variable transmission.

  In general, the moving direction of the moving member (63) is such that the friction wheels (22) and (23) move along an inclined surface in contact with the ring (25). Therefore, the axial direction that is the speed change operation direction of the ring means the moving direction of the moving member, and does not necessarily coincide with the axis of the friction wheel.

For example, referring to FIGS. 2 to 11, the support members are disposed at different positions with respect to the planes including the axes (l−l) and (n−n) of the friction wheels (22) and (23). A first support member (67) and a second support member (69),
Said first and second support members, in the state positioned on the rotation upstream side of the front SL contact portion, positioning the ring in the axial direction, or One prior Symbol rotation downstream with respect to the contact portion In the positioned state, it has a pair of operating portions (70...) That support the ring so as to allow movement in the axial direction.

For example, referring to FIG. 4 and FIGS. 6 to 11, the operating portion (70 ₁ , 70 ₄ , 70 ₅ to 70 ₉ ) has an arm (85) rotatably supported by the moving member. ,
Of the first and second support members, the arm of the support member positioned on the upstream side of the rotation approaches the ring by rotation in a direction in which the tip side thereof follows the rotation direction of the ring (25), And the ring is positioned in the axial direction as defined by the stopper (76).
Of the first and second support members, the arm of the support member positioned on the downstream side of the rotation is allowed to move in the axial direction of the ring by turning in the direction in which the tip side thereof follows the rotation direction of the ring. Do it.

  For example, referring to FIG. 6 to FIG. 10, the arm (85) rotates at the tip thereof a rotating member (86) (93) (96) (100) (103) at least in a direction following the ring rotating direction. Support freely.

  For example, referring to FIG. 4 and FIG. 11, the arm (85) has a sliding contact surface (75) (105) that smoothly slides on the ring (25) at its tip.

For example, referring to FIG. 5, the operating portion includes (70 ₂ ) (70 ₃ ), a cage (80) having a receiving space whose bottom surface is an inclined surface (80a), and the ring ( 25) and a sprag (for example, a ball 81 or a piece 82) that is stored so as to be movable in the rotational direction.
Of the first and second support members, the sprag of the support member located on the upstream side of the rotation moves to the narrow side of the accommodation space in the rotation direction of the ring (25), and Positioning the ring axially,
Of the first and second support members, the sprags of the support member located on the downstream side of the rotation move to the wide side of the accommodation space in the rotation direction of the ring, and the axial direction of the ring Allow movement.

For example, referring to FIG. 3 and FIGS. 7 to 11, the ring (25) rotates in a plane (mm) orthogonal to the axis (l-l) of the one friction wheel (22). The cross section is a parallelogram,
The pair of actuating portions (70, 70 ₅ to 70 ₉ ) are arranged so that their positions or radial lengths are different in the radial direction so as to correspond to both side surfaces different in the radial direction of the ring.

  For example, referring to FIGS. 2 and 3, the support members (67) and (69) support the ring (25) at a position farthest from a plane including the axis of the two friction wheels.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, it does not have any influence on the structure as described in a claim by this.

  According to the first aspect of the present invention, regardless of whether the conical friction wheel ring type continuously variable transmission is in forward or reverse rotation, the ring is axially moved by the support member on the side close to the rotation upstream side of the contact portion with the friction wheel. Since the ring can be tilted smoothly on either the forward or reverse side of the continuously variable transmission, the speed change operation can be easily performed without requiring troublesome control. A constant speed can be maintained in the neutral position.

  According to the second aspect of the present invention, the first or second support member located on the upstream side of the rotation of the contact portion with the friction wheel is operated regardless of the forward or reverse rotation of the continuously variable transmission. The second or first support member, which defines the axial position of the ring by the portion and is located on the downstream side of the rotation, moves in the axial direction when the operating portion is pushed by the ring. Can be shifted and shifted.

  Further, since the first or second support member supports the ring so as to grip the rotation upstream side of the ring and inclines the ring, the speed change operation is performed at a speed change following the moving speed of the moving member, and the moving member moves. When stopped, the ring is autonomously held in the neutral position, the continuously variable transmission is in a constant speed state, and it is easy to perform gear shifting operations without the need for feedback control such as by monitoring the rotational speed of both friction wheels. It can be performed.

According to the third aspect of the present invention, since the operating portion is composed of an arm that is rotatably supported, the arm defines the axial position of the ring according to the rotational direction of the ring, and the axial direction of the ring. It is possible to automatically and reliably switch to a state in which the direction movement is allowed.

  According to the fourth aspect of the present invention, since the rotating member is supported at the tip of the arm, the rotating member abuts on the ring and rotates to accurately define the axial position of the ring by the operating portion. At the same time, it is possible to maintain the smooth rotation of the ring, reduce wear of the ring and the operating portion, and improve the durability of the continuously variable transmission.

  According to the fifth aspect of the present invention, since the slidable contact surface such as a shoe that smoothly slidably contacts the ring is provided at the tip of the arm, smooth rotation of the ring can be maintained with a relatively simple configuration. .

According to the sixth aspect of the present invention, since the operating portion is a one-way clutch having a cage and a sprag, the axial positioning of the ring and the axial movement allowance can be reliably switched with a simple and compact configuration. Can do.

According to the seventh aspect of the present invention, the right and left actuating portions have different radial positions or radial lengths in accordance with both side surfaces of the ring having a parallelogram cross section, so the force from the actuating portion is It acts on the center in the radial direction of both side surfaces of the ring and does not act on the ring from the operating portion.

  According to the eighth aspect of the present invention, since the ring is axially defined by the support member at a position farthest from the contact portion of the ring with the friction wheel, the inclination angle of the ring (perpendicular to the axis) (Including the state) can be stably performed, and the shifting operation and the holding operation at a constant speed can be easily and reliably performed, and the shifting operation can be performed with a quick response.

The expanded sectional view which shows the hybrid drive device which can apply this invention. The side view which shows the conical friction wheel ring type continuously variable transmission (cone ring type CVT) which concerns on this invention. The front view which carried out the partial cross section which shows the transmission operation means part of the said cone ring type CVT. It is the schematic which shows the action | operation part of a support member, (A) is the state which prescribed | regulated the axial direction position of the ring, (B) shows the state which accept | permitted the axial direction movement of the ring. It is front sectional drawing which shows the supporting member by a one-way clutch system, (A) shows the embodiment whose operation part is a ball, and (B) shows the operation part which is a piece. Schematic which shows the supporting member by a swing roller system. The support member which used the ball bearing for the operation part is shown, (A) is a front sectional view, and (B) is the B arrow view. The support member which used the needle bearing for the operation part is shown, (A) is a front sectional view and (B) is the B arrow view. A support member using a roller is shown in an operation part, (A) is a front sectional view and (B) is the B arrow line view. The supporting member which used the bush for the action | operation part is shown, (A) is front sectional drawing, (B) is the B arrow directional view. The support member which used the shoe for the operation part is shown, (A) is a front sectional view, and (B) is the B arrow view.

  A hybrid drive device to which the present invention is applied will be described with reference to the drawings. As shown in FIG. 1, the hybrid drive device 1 is interlocked with an electric motor 2, a conical friction wheel ring type continuously variable transmission (cone ring type CVT) 3, a differential device 5, and an output shaft of an engine (not shown). An input shaft 6 and a gear transmission 7 are provided. Each of the above devices and shafts is housed in a case 11 configured by combining two case members 9 and 10, and the case 11 is divided into a first space A and a second space B by a partition wall 12. It is partitioned in an oil-tight manner.

  The electric motor 2 has a stator 2 a fixed to the first case member 9 and a rotor 2 b provided on the output shaft 4, and the output shaft 4 has a bearing on the first case member 9 at one end. 13, and the other end is rotatably supported by the second case member 10 via a bearing 15. An output gear 16 composed of a gear (pinion) is formed on one side of the output shaft 4, and the output gear 16 meshes with an intermediate gear (gear) 19 provided on the input shaft 6 via an idler gear 17. ing.

  The cone ring type CVT 3 includes a conical (one conical) friction wheel 22 as an input member, a similar conical (the other conical) friction wheel 23 as an output member, and a metal ring 25. Become. The friction wheels 22 and 23 are arranged such that the axes l-l and nn are parallel to each other and the large-diameter side and the small-diameter side are opposite to each other in the axial direction. It is arranged so as to be sandwiched between the opposed inclined surfaces of the wheels 22 and 23 and so as to surround one of the two friction wheels, for example, the input side friction wheel 22. A large thrust force acts on at least one of the two friction wheels, and the ring 25 is clamped by a relatively large clamping pressure based on the thrust force. Specifically, an axial force applying means (not shown) including an inclined cam having a ball interposed between the output side friction wheel 23 and the continuously variable transmission output shaft 24 is formed on a surface opposed in the axial direction. Thus, a thrust force in the direction of arrow D corresponding to the transmission torque is generated in the output side friction wheel 23, and the ring 25 is large with the input side friction wheel 22 supported in a direction against the thrust force. A pinching pressure is generated.

  One end (large diameter side) end of the input side friction wheel 22 is supported by the first case member 9 via the roller bearing 26, and the other side (small diameter side) end is a tapered roller bearing 27. Is supported by the partition wall 12. The output side friction wheel 23 has one end (small diameter side) end supported by the first case member 9 via a roller (radial) bearing 29 and the other side (large diameter side) end positioned as a roller. A (radial) bearing 30 supports the partition 12. The other end of the output shaft 24 in which the thrust force in the direction of arrow D is applied to the output side friction wheel 23 is supported by the second case member 10 via the tapered roller bearing 31. The other end of the input side friction wheel 22 is sandwiched between the inner race of the bearing 27 by a stepped portion and a nut 32, and from the output side friction wheel 23 acting on the input side friction wheel 22 via the ring 25. A thrust force is carried by the tapered roller bearing 27. On the other hand, the reaction force of the thrust force acting on the output side friction wheel 23 acts on the output shaft 24 in the counter arrow D direction, and the thrust reaction force is carried by the tapered roller bearing 31.

  The ring 25 is moved in the axial direction by a speed change operation means (described later) according to the present invention to change the contact position of the input side friction wheel 22 and the output side friction wheel 23, so that the input member 22, the output member 23, The speed ratio is continuously changed. The thrust force D corresponding to the transmission torque is canceled out in the integrated case 11 via the tapered roller bearings 27 and 31 and does not require an equilibrium force as an external force such as hydraulic pressure.

  The differential device 5 has a differential case 33. One end of the differential case 33 is supported by the first case member 9 via a bearing 35, and the other end is a second case member. 10 through a bearing 36. A shaft orthogonal to the axial direction is mounted inside the differential case 33, bevel gears 37 and 37 serving as differential carriers are engaged with the shaft, and left and right axle shafts 39l and 39r are supported. Bevel gears 40 and 40 that mesh with the differential carrier are fixed to the shaft. Further, a large-diameter differential ring gear (gear) 41 is attached to the outside of the differential case 33.

  A gear (pinion) 44 is formed on the continuously variable transmission output shaft 24, and the differential ring gear 41 is engaged with the gear 44. The motor output gear (pinion) 16, idler gear 17 and intermediate gear (gear) 19, continuously variable transmission output gear (pinion) 44, and diff ring gear (gear) 41 constitute the gear transmission 7. The motor output gear 16 and the diff ring gear 41 are arranged so as to overlap in the axial direction, and the intermediate gear 19 and the continuously variable transmission output gear 44 are further in the axial direction with the motor output gear 16 and the diff ring gear 41. Are arranged to overlap. The gear 45 that is spline-engaged with the continuously variable transmission output shaft 24 is a parking gear that locks the output shaft at the parking position of the shift lever. Further, the gear means a meshing rotation transmission means including a gear and a sprocket. In the present embodiment, the gear transmission is a gear transmission composed entirely of gears.

  The input shaft 6 is supported by the second case member 10 by a roller bearing 48, and is engaged (drive coupled) to the input member 22 of the continuously variable transmission 3 by a spline S at one end thereof, and The other end side is linked to the output shaft of the engine via a clutch (not shown) housed in a third space C formed by the second case member 10. The third space C side of the second case member 10 is open and connected to an engine (not shown).

  The gear transmission 7 is accommodated in the electric motor 2 and a second space B which is a portion between the first space A and the third space C in the axial direction, and the second space B is The second case member 10 and the partition wall 12 are formed. The shaft support portions (27, 30) of the partition wall 12 are oil-tightly partitioned by oil seals 47, 49, and the shaft support portions of the second case member 10 and the first case member 9 are also oil seals. The second space B is sealed with a shaft 50, 51, 52, and is configured to be oil-tight, and the second space B is filled with a predetermined amount of lubricating oil such as ATF. The first space A formed by the first case member 9 and the partition wall 12 is similarly configured to be oil-tight, and the first space A has a shearing force, particularly a shearing force in an extreme pressure state. Is filled with a predetermined amount of large traction oil.

  Next, the operation of the hybrid drive device 1 described above will be described. The hybrid drive device 1 is used in such a manner that the third space C side of the case 11 is coupled to an internal combustion engine, and the output shaft of the engine is linked to the input shaft 6 via a clutch. The rotation of the input shaft 6 to which power from the engine is transmitted is transmitted to the input side friction wheel 22 of the cone ring type continuously variable transmission 3 via the spline S, and further to the output side friction wheel 23 via the ring 25. Communicated.

  At this time, a large contact pressure acts between the friction wheels 22, 23 and the ring 25 due to the thrust force in the direction of arrow D acting on the output-side friction wheel 23, and the traction oil is in the first space A. Since it is filled, an extreme pressure state in which an oil film of the traction oil is interposed between the two friction wheels and the ring. In this state, since the traction oil has a large shearing force, power is transmitted between the friction wheels and the ring by the shearing force of the oil film. Accordingly, the friction wheel and the ring can be transmitted without slipping while being in contact with each other, and the predetermined torque can be transmitted without slipping, and the ring 25 can be smoothly moved in the axial direction. The contact position is changed to change continuously.

  The rotation of the continuously variable speed output side friction wheel 23 is transmitted to the differential case 33 of the differential device 5 via the output shaft 24, the output gear 44 and the differential ring gear 41, and the power is distributed to the left and right axle shafts 39l and 39r. Then, the wheel (front wheel) is driven.

  On the other hand, the power of the electric motor 2 is transmitted to the input shaft 6 via the output gear 16, the idler gear 17 and the intermediate gear 19. The rotation of the input shaft 6 is continuously variable via the cone ring type continuously variable transmission 3 and further transmitted to the differential device 5 via the output gear 44 and the diff ring gear 41 as described above. . The gear transmission 7 comprising the gears 16, 17, 19, 44, 41, 37, 40 is housed in a second space B filled with lubricating oil, and the lubricating oil is engaged when the gears are engaged. Smoothly transmits power. At this time, the differential ring gear 41 disposed at the lower position of the second space B is combined with the large-diameter gear to scoop up the lubricating oil and other gears (gears) 16, 17, 19 , 44 and the bearings 27, 30, 20, 21, 31, 48 are reliably and sufficiently supplied with lubricating oil.

  Various operation modes of the engine and the electric motor, that is, the operation mode of the hybrid drive device 1 can be adopted as necessary. As an example, when the vehicle starts, the clutch is disengaged and the engine is stopped, the engine is started only by the torque of the electric motor 2, and when the vehicle reaches a predetermined speed, the engine is started and accelerated by the power of the engine and the electric motor. Then, the electric motor is set to the free rotation or regenerative mode and travels only by the engine. During deceleration and braking, the electric motor is regenerated to charge the battery. Alternatively, the clutch may be used as a starting clutch, and may be used to start while using the motor torque as an assist by the power of the engine.

  Next, a conical friction ring type continuously variable transmission (cone ring type CVT) 3 according to the present invention will be described with reference to FIGS. As described above, the continuously variable transmission 3 includes the input side friction wheel 22, the output side friction wheel 23, and the ring 25. Both the friction wheel and the ring are made of metal such as steel. The friction wheels 22 and 23 are arranged so that their axis lines l-n and n-n (see FIG. 1) are parallel to each other in parallel and have a conical shape whose inclined surface is a straight line. A ring 25 is sandwiched between the two inclined surfaces. The ring 25 is arranged so as to surround either one of the friction wheels, specifically, the input side (first conical) friction wheel 22, and a cross section in a plane perpendicular to the circumferential direction is substantially parallel to the four sides. It has a shape, and its rotation surface mm is set so as to be substantially orthogonal to the axis line l-1.

  The cone ring type CVT 3 is covered at one end side and the entire circumference thereof with a bottomed cylindrical first case member 9, and the opening side of the first case member 9 is covered with a partition wall 12. The first space A is stored in an oil-tight manner. The two friction wheels are arranged obliquely so that the shaft 23a of the output side (the other conical shape) friction wheel 23 is positioned a predetermined amount above the shaft 22a of the input side (the one conical shape) friction wheel 22. The input side friction wheel 22 is arranged with a margin between the input side friction wheel 22 and the case member 9 on the upper side, the lower side, and the side opposite to the output side friction wheel 22. The ring 25 surrounding the input-side friction wheel 22 is disposed in a space between the input-side friction wheel and the case member 9, and a speed change operation means 60 that moves the ring 25 in the axial direction is disposed. ing. In FIG. 2, the upper portion 9A of the case member 9 is a portion where the electric motor 2 is disposed, and 9B is a portion where the differential device 5 is disposed. A space J below the input side friction wheel 22 between the case member 9 is an oil reservoir 59 (oil level is indicated by 59a) for traction oil.

  The shift operation means 60 includes a feed screw shaft 61 disposed in the upper space F of the input side friction wheel 22, a guide rail 62 disposed in the lower space J serving as the oil slide 59, and the input side friction wheel 22. And a moving member 63 disposed in the side space G so as to surround the opposite surface of the output side friction wheel 23. The feed screw shaft 61 and the guide rail 62 are arranged in a vertical position with the input side friction wheel 22 in between, and are arranged in parallel to each other, and in parallel so that the two conical friction wheels 22 and 23 are along the opposing inclined surfaces. Has been placed. The feed screw shaft 61 is rotatably supported by the case member 9 and is linked with a speed change driving means such as a motor. From the control unit according to the driver's intention such as an accelerator pedal and the traveling state of the vehicle. The drive signal is appropriately rotated by the drive signal.

  The moving member 63 is supported so as to be axially movable across the feed screw shaft 61 and the guide rail 62, and a ball nut 65 that is screwed to the feed screw shaft 61 is fixed to the upper portion of the moving member 63. Further, a guide member 66 supported by the guide rail 62 so as to be movable in the axial direction is fixed. An upper (first) support member 67 is installed on the inner surface side opposite to the ball nut 65 in the moving member 63, and lower (second) on the inner surface side opposite to the guide member 66. ) A support member 69 is installed. The upper support member 67 and the lower support member 69 are disposed on different sides with respect to the plane including the axes ll and nn of the friction wheels 22 and 23 on the input side and the output side. However, both support members 67 and 69 are arranged so as to support the ring 25 at a position farthest from the axis plane.

  The upper support member 67 and the lower support member 69 can support the ring 25 so as to sandwich the ring 25, and move integrally with the moving member 63 to move the ring 25 in the axial direction. The members 67 and 69 support the ring 25 from both sides when the ring 25 is on the upstream side in the rotational direction where the ring 25 is drawn into the contact portion with the two friction wheels 22 and 23 so as to be defined in the axial direction. Although interlocked, it has a structure that allows the axial movement (swing) of the ring 25 on the downstream side in the rotational direction pushed out from the contact portion. Accordingly, the ring 25 is supported so as to be picked by the upper or lower support member 67 or 69 located upstream of the friction wheel regardless of whether the friction wheel is rotating forward or backward, and the position based on the movement or stop of the moving member 63. Accordingly, either the upper or lower support member 69 or 67 allows the swing of the ring 25 in the above movement or stop at that time, and the ring 25 is autonomously supported.

  As shown in FIG. 3, the upper and lower support members 67 and 69 have the same configuration and have a pair of operating portions 70 and 70 disposed on the left and right sides of the ring 25, but the left and right operating portions 70 and 70 are included. The thickness (radial length) or the working position of the ring is different because the ring 25 is configured to be a plane mm that is perpendicular to the axis 11 of the friction wheel, so that the cross section is formed in a parallelogram. This is because a supporting force is applied to the center of the ring 25 on the left and right sides so that no moment is applied to the ring.

  In addition, the ring 25 has an inclination angle (including an inclination angle 0 perpendicular to the axis) determined by the contact portion between the support member 67 or 69 on the upstream side that defines the axial movement and the friction wheels. Since the support member supports the ring at a position farthest from the contact portion, the inclination angle of the ring is stable, an accurate speed change operation and a constant speed speed maintenance operation can be easily performed, and the moving member The inclination angle of the ring according to the moving speed of 63 can be set easily and reliably, and a shift with a quick response speed becomes possible.

  Next, a specific configuration of the support members 67 and 69 will be described with reference to FIGS. Since the upper and lower support members have the same configuration, only one of them may be shown and the other may be omitted.

FIG. 4 shows swing arm type support members 67 and 69. Right and left actuating unit 70 _1, 70 ₁ of the support member comprises a swing arm 85 about the pivot shaft 73 is rotatably supported. The left and right swing arms 85, 85 are configured to be mirror-symmetric with respect to the ring 25, are rotatably supported by a frame 71 fixed to the moving member 63 via a pivot shaft 73, and contact the ring side surface at the tip thereof. A possible cam surface (sliding contact surface) 75 is formed, and a stopper 76 that restricts further rotation with respect to rotation in a direction approaching the ring is formed by the frame 71 of the moving member 63 and the like.

  In a state where the vehicle equipped with the hybrid drive device 1 is moving forward, as shown in FIG. 4A, the cone ring type CVT 3 rotates in the forward rotation direction (the ring 25 is in the direction of the arrow) and contacts the friction vehicle. The lower support member 69 on the upstream side in the rotational direction of the ring 25 is operated with respect to the portion. That is, when the ring 25 rotates in the direction of the arrow, the swing arms 85 and 85 are respectively dragged and rotated in a direction approaching the ring 25, and come into contact with the stopper 76. In this state, the axial position is defined so that the tip cam surfaces 75 of both swing arms 85, 85 support both side surfaces of the ring 25, and the ring 25 is positioned and supported on the upstream side of the rotation by the support member 69. Rotate. In this state, the gap between the swing arm cam surfaces 75 and 75 is set to be slightly wider than the width of the ring 25, and the axial movement is restricted while allowing rotation of the ring 25 via oil. It is like that. Accordingly, the cam surface 75 at the tip of the arm constitutes a sliding contact surface that smoothly contacts the ring 25. As shown in the right swing arm 85, it is preferable to provide a spring 77 that urges the swing arm to move closer to the ring so as to urge the swing arm to the operating position. The spring 77 may not be provided.

  On the other hand, as shown in FIG. 4B, the upper support member 67 on the downstream side in the rotation direction of the ring 25 with respect to the friction wheel contact portion is a swing arm 85 (see the right side) that contacts the ring 25. It is dragged by the rotation and pivoted away from the stopper 76. Therefore, the swing arm 85 does not hinder the axial movement (swing) of the ring 25, and the ring 25 freely moves in the axial direction and does not hinder the inclination of the ring.

  Therefore, by moving the ball nut 65 by the rotation of the feed screw shaft 61, the moving member 63 is guided by the guide rail 62 and moves in parallel along the opposing inclined surfaces of the friction wheels 22 and 23. In this state, the lower support member 69 on the upstream side of the ring rotation is in a state in which the left and right swing arms 85, which are operating portions thereof, are close to the stopper 76, and positions and supports the ring 25 in the axial direction. 25 is moved in the axial direction with the rotation upstream side being picked by the lower support member 69, and in combination with the fact that the upper support member 67 allows the ring 25 to move in the axial direction, It inclines at an angle corresponding to the moving speed of 63. As a result, the ring 25 has a helical shape with respect to the input side friction wheel 22, so that the ring 25 moves in the axial direction at a speed corresponding to the angle, and the contact position between the input side and output side friction wheels 22, 23. The cone ring type CVT 3 is changed in speed by changing.

  When the movement of the moving member 63 is stopped by stopping the feed screw shaft 61, the upper and lower support members 67 and 69 are also stopped. In this state, the swing arm 85 of the lower support member 69 on the upstream side of the rotation is in a state where the ring 25 is positioned and supported in the axial direction and is stopped at that position, and both swing arms 85 of the upper support member 67 are It is in a state of allowing 25 axial movements. Accordingly, since the ring 25 continues to rotate with the upstream side of the rotation being held at a fixed position, the helical angle is autonomously 0, that is, perpendicular to the axes l-l and n-n of both friction wheels. It rotates on the plane mm and is kept at a predetermined rotation ratio at that position and continues to rotate at a constant rotation.

  When the vehicle reverses and the cone ring type CVT 3 reverses, the upper support member 67 becomes upstream in the rotational direction of the ring 25 with respect to the friction wheel contact portion shown in FIG. As shown in B), it is on the downstream side of the rotation direction of the ring 25, and operates in the reverse direction as in the normal rotation described above.

FIG. 5 shows support members 67 and 69 of a one-way clutch (OWC) system. The support member is disposed so as to sandwich the ring 25, and has left and right cages 80 fixed to the moving member 63. The cages 80 each contain a sprag (ball or piece). The bottom surface of the storage space is composed of an inclined cam surface 80a inclined with respect to the rotation surface (mm) of the ring 25. 5A, balls 81 are housed in the cage 80, and FIG. 5B shows a piece 82 that is movable in the radial direction along the cam surface 80a. Is stored. The cage 80 and ball 81 or frame 82 acts as a one-way clutch disengaging the rotation direction of the ring 25, constituting the right and left operating portions 70 _2, 70 _3.

To describe the supporting member 69, 67 consisting of a ball actuated portion 70 ₂ along in FIG. 5 (A), if the ring 25 there during the vehicle forward is rotated in the forward direction, it is dragged by the rotation of the ring 25 below The ball 81 of the support member 69 is moved in the narrow direction of the inclined cam surface 80a of the cage 80 and comes into contact with a stop surface 80b which is an end surface of the storage space. The ball 81 of the upper support member 67 located on the rotation downstream side of the ring 25 is dragged by the rotation of the ring 25 and is moved in the wide direction of the inclined cam surface 80a. In this state, the axial position is positioned so that the lower support member 69 grips the ring 25, and the upper support member 67 allows the ring 25 to move in the axial direction.

  On the other hand, during reverse rotation of the cone ring CVT accompanying the reverse travel of the vehicle, the ball 81 of the upper support member 67 is in the specified position, and the ball of the lower support member 69 is in the free position. Thus, as in the previous embodiment, during forward rotation, the ring 25 is positioned by the ball 81 of the lower support member 69 located on the upstream side of the ring rotation, and the speed is changed or held at a constant speed. In this case, the upper support member 67 positioned on the upstream side of the ring rotation positions and supports the ring 25 of the ball 81 to change the speed or hold it at a constant speed. Even in the supporting member on the side positioned in the axial direction of the ring, the movement of the ball 81 is restricted by the stop surface 80b, and the ball 81 is idled by contact with the ring 25, and the rotation of the ring 25 is prevented. It does not prevent it.

Supporting members 67 and 69 made of piece operating portion 70 ₃ shown in FIG. 5 (B) also, as in the previous ball actuating portion, a predetermined position or free position is dragged to rotation of the ring 25. In addition, the oil adhering to the ring depending on the rotation direction of the ring 25 is guided from the gap g of the cage 80 to the storage space in the cage. When the ring 25 rotates in the forward rotation direction, oil is introduced into the storage space of the cage 80 of the lower support member 69 and acts on the piece 82 as a dynamic pressure p indicated by an arrow. Move in the narrow direction. At this time, the oil is interposed between the piece 82 and the ring 25 so as to be in a lubrication state, and the rotation of the ring 25 is not hindered. Further, the upper support member 67 enables the ring 25 to freely swing in the axial direction by the dynamic pressure p due to the oil moving the piece 82 in the wide direction of the inclined cam surface 80a according to the rotation direction of the ring 25. Become free.

FIG. 6 shows a swing roller type support member, and shows support members 67 and 69 that are operated by normal rotation of the ring 25. Actuating portion 70 ₄ of the left and right, has an arm 85 which is rotatably supported by a shaft 73 to a fixed frame in the moving member 63, the tip of the arm roller 86 is disposed. Both arms 85 are urged by a spring 77 in a direction approaching the ring 25, and a stopper 76 that abuts at a predetermined position approaching and prevents further rotation is constituted by the frame or the like. The position of the stopper 76 is set at a position where the arm 85 slightly exceeds the rotation plane mm of the ring 25. In addition, the arm 85 is provided with a restricting portion 87 that restricts the arm 85 at, for example, about 10 degrees in the direction away from the ring 25.

  In this embodiment, a one-way clutch 89 is interposed between the roller 86 and the support shaft 84 at the tip of the arm 85, and these one-way clutches are attached to the lower support member 69 of the ring 25. It is a direction that allows free rotation by contacting the ring in the forward rotation direction, and the upper support member 67 is a direction that allows free rotation by contacting the ring in the reverse rotation direction of the ring.

  Therefore, when the ring 25 is rotating forward, the lower support member 69 (see the right side in FIG. 6) positioned on the upstream side of the rotation is positioned by the stopper 76 by the arm 85 being rotated by the spring 77 in the direction approaching the ring 25. Both rollers 86 support the ring 25 and are positioned in the axial direction. At this time, both the left and right rollers 86 are positioned to position the ring 25 in the axial direction. When the rollers 86 come into contact with the ring 25, the rollers 86 are freely rotated by the one-way clutch 89 and the rotation of the ring 25 is not hindered.

  On the other hand, when the ring 25 is reversed, the lower support member 69 (see the left side in FIG. 6) rotates the arm 85 against the spring 77 when the roller 86 abuts against the ring 25, and the shaft of the ring 25 Allow directional movement (runout). At this time, the roller 86 tries to rotate while coming into contact with the ring 25, but the rotation is blocked by the one-way clutch 89, and the arm 85 is rotated by being dragged by the reverse rotation of the ring 25.

Above description has described the time of forward rotation and reverse rotation, the upper support member 67 corresponds to the operation portion 70 ₄ of the left side of the drawing during the forward rotation, the upper support member 67 in the operating portion 70 ₄ of the right side of the drawing during reverse rotation Equivalent to.

  Various specific examples of the support members 67 and 69 will be described with reference to FIGS. The support members 67 and 69 have two headed shafts 73 and 73 planted on the inner diameter side of the frame 71 in the moving member 63, and are secured to the frame 71 by a retaining pin 90. Arms 85 and 85 are rotatably supported by these shafts 73, respectively, and a torsion spring 91 is interposed between the arm boss 85a and the frame 71 to urge both arms toward the ring 25. ing. In addition, a stopper 76 is provided on the frame 71 so that the arm 85 abuts and is held at the predetermined position at which the arm 85 approaches the ring 25. In the lower support member 69, each arm 85, 85 is urged to rotate in the direction in which the tip approaches in the forward rotation direction of the ring 25, and in the upper support member 67, the ring 25 In the reverse rotation direction, the rotation is biased in the direction in which the tips approach each other.

Figure 7 (A), operation unit 70 ₅ shown in (B) is the support shaft 92 to the distal end of the arm 85 is fixed to the support shaft 92 is interposed between the head 92a and the arm 85 A ball (or roller) bearing 93 is mounted. The left and right ball bearings 93 have different radial positions by changing the wall thickness of the frame 71 so that the cross section just contacts the side surface of the ring 25 having a parallelogram shape.

Therefore, the operating portion 70 ₅ of the support portion located on the rotation upstream side (the lower support member 69 is a forward, above a reverse supporting member 67) of the friction wheel contact portion of the ring 25, the arm 85 is rotated by the torsion spring 91 in a direction approaching the ring and is brought into contact with the stopper 76. In this state, the ball bearings 93 and 93 are positioned in the axial direction with the ring 25 interposed therebetween. At this time, the ball bearing 93 rotates while the outer race abuts against the side surface of the ring 25, the rotation of the ring 25 is not impaired, and the axial position of the ring 25 is worn accurately and over a long period of time. It is possible to position without doing.

On the other hand, the operating portion 70 ₅ of the support member located on the rotation downstream side (the lower support member 69 is a forward a top support member 67, reverse) of the ring 25, the arm 85 is dragged by the ring 25 Rotates away from the stopper 76 and is pushed by the ring 25 to allow axial movement of the ring. Similarly, the ball bearing 93 on the contact side rotates in contact with the ring and does not impair the rotation of the ring 25.

FIG. 8 (A), the operating portion 70 ₆ shown in (B), said arm 85 has a two divided structure of the body 85c and the lid 85d, to form a notch 95 at the distal end of the main body 85c, A needle bearing 96 is mounted and supported between the notch and the lid body 85d. The main body 85c and the lid body 85d are integrally fixed by a screw 97 in a state where the needle bearing 96 is mounted.

  Even in the present embodiment, the needle bearing 96 that is the operating portion rotates in contact with the ring 25 and rotates the ring 25 smoothly and accurately positions the axial position.

FIG. 9 (A), the actuating part 70 ₇ shown in (B) is a recess 85e is formed in the arm 85, the roller 100 is accommodated in the recess, rotatably supported via a headed pin 101 Has been. The roller 100 is made of bearing steel, synthetic resin, cylindrical iron coated with fluororesin (PTFE) having excellent self-lubricating property, or ceramic.

  In the present embodiment, the roller 100 as the operating portion rotates in contact with the ring 25 and smoothly rotates the ring, but can be configured inexpensively and compactly with a relatively simple structure.

FIG. 10 (A), the actuating portion 70 ₈ shown in (B) is made of steel or the like end of the arm 85 is bent in L-shape are integrally formed as a support shaft 102, the support shaft 102 Bush 103 is rotatably fitted.

  This embodiment also has a relatively simple structure while the bush 103 serving as the operating portion rotates like a roller of a roller chain and maintains the smooth rotation of the ring 25.

FIG. 11 (A), the actuating portion ₇₀₉ shown in (B), the recess 85e in the front end of the arm 85 is formed, the legs 105a of the shoe 105 in the recess is accommodated in the distal end of the arm 85 A shoe 105 is attached by a headed pin 101. The shoe 105 is made of iron or a ceramic whose surface is coated with fluorine or ceramic.

  In the present embodiment, the shoe 105 contacts the side surface of the ring 25 and allows the ring 105 to move in the axial direction by positioning the ring in the axial direction or pressing the ring. In this case, the shoe 105 slips in an excellent self-lubricated state. Thus, the smooth rotation of the ring 25 is maintained.

3 Conical friction wheel ring type continuously variable transmission (cone ring type CVT)
22 One (input side) friction wheel 23 The other (output side) friction wheel 25 Ring 60 Transmission operation means 61 Feed screw shaft 62 Guide rail 63 Moving member 67 First (upper) support member 69 Second (lower) Support members 70, 70 ₁ to 70 ₉ Actuating portion 85 Arm 86, 93, 96, 100, 103 Rotating member (roller, ball bearing, needle bearing, roller, bush)
75,105 Sliding contact surface (cam surface, shoe)
ll, nn Axis mm plane

Claims (8)

A pair of conical friction wheels arranged on axes parallel to each other and arranged so that the large-diameter side and the small-diameter side are opposite to each other, and the two friction wheels are opposed to each other so as to surround one of the two friction wheels. In a conical friction wheel ring type continuously variable transmission comprising: a ring sandwiched between inclined surfaces; and a shift operation means for shifting the ring by moving the ring in the axial direction.
The shift operation means includes a moving member that can move in parallel along the axial direction that is a shift operation direction of the ring;
A support member that is disposed integrally with the moving member in at least the moving direction of the moving member and that can rotatably support the ring;
The support member is located upstream of the contact portion where the ring is sandwiched between the friction wheels at a position different from the plane including the axis of the friction wheels according to the rotation direction of the rings. The ring is positioned and supported in the axial direction on the near side,
A conical friction wheel ring type continuously variable transmission. The support member includes a first support member and a second support member arranged at different positions with respect to the plane including the axis of the friction wheels,
Said first and second support members, in the state positioned on the rotation upstream side of the front SL contact portion, positioning the ring in the axial direction, or One prior Symbol rotation downstream with respect to the contact portion In the positioned state, each has a pair of actuating parts that support the axial movement of the ring.
The conical friction wheel ring type continuously variable transmission according to claim 1. The operating unit has an arm rotatably supported by the moving member,
Of the first and second support members, the arm of the support member positioned on the upstream side of the rotation approaches the ring by rotation in a direction in which the tip side thereof follows the rotation direction of the ring, and serves as a stopper. The ring is positioned in the axial direction,
Of the first and second support members, the arm of the support member positioned on the downstream side of the rotation is allowed to move in the axial direction of the ring by turning in the direction in which the tip side thereof follows the rotation direction of the ring. Become
The conical friction wheel ring type continuously variable transmission according to claim 2. The arm is configured to support a rotating member at the tip thereof so as to be rotatable at least in a direction following the ring rotating direction.
The conical friction wheel ring type continuously variable transmission according to claim 3. The arm has a sliding contact surface that smoothly contacts the ring at the tip thereof.
The conical friction wheel ring type continuously variable transmission according to claim 3. The operating portion includes a cage having a storage space whose bottom surface is an inclined surface, and a sprag that is stored in the storage space of the cage so as to be movable in the rotation direction of the ring,
Of the first and second support members, the sprag of the support member located on the upstream side of the rotation moves to the narrow side of the accommodation space in the rotation direction of the ring, and the ring is pivoted. Positioning in the direction
Of the first and second support members, the sprags of the support member located on the downstream side of the rotation move to the wide side of the accommodation space in the rotation direction of the ring, and the axial direction of the ring Allowing movement,
The conical friction wheel ring type continuously variable transmission according to claim 2. The ring has a parallelogram in cross section so that the ring rotates in a plane perpendicular to the axis of the one friction wheel.
The pair of actuating portions are arranged so that their positions or radial lengths are different in the radial direction so as to correspond to both side surfaces different in the radial direction of the ring.
The conical friction wheel ring type continuously variable transmission according to any one of claims 2 to 6. The support member supports the ring at a position farthest from a plane including the axis of the friction wheels.
The conical friction wheel ring type continuously variable transmission according to any one of claims 1 to 7.

Images