JP2009243603A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission that is constituted simply and transmits power without using a belt and the like. <P>SOLUTION: The continuously variable transmission 100 includes: a fixed sheave 101 of a disc shape provided rotatably by power from an engine 106; a movable sheave 102 which contacts with the contact surface 140 of the fixed sheave 101 and is provided so as to be shiftable in the radial direction of the contact surface 140 and so as to be rotatable by the power transmitted from the fixed sheave 101; a final gear 104 which is arranged with an interval to the movable sheave 102 and provided rotatably; and a uniform velocity joint 125 which is connected to the final gear 104 and the movable sheave 102 and capable of transmitting power from the movable sheave 102 to the final gear 104. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission.

  Conventionally, various types of continuously variable transmissions have been proposed. For example, a continuously variable transmission described in Japanese Patent Application Laid-Open No. 2000-186758 includes an input pulley and an output pulley whose groove width can be changed, and a belt stretched over the input pulley and the output pulley.

Such a continuously variable transmission generally includes a hydraulic actuator for moving the movable sheave of the input pulley and a hydraulic actuator for moving the movable sheave of the output pulley.
JP 2000-186758 A

  As described above, the conventional continuously variable transmission is provided with the hydraulic actuator in each of the input pulley and the output pulley, which increases the cost of the continuously variable transmission itself and increases the volume of the continuously variable transmission. Become.

  Furthermore, in the conventional continuously variable transmission, power is transmitted from the input pulley to the output pulley via the belt, the power transmission efficiency is poor, and it is necessary to ensure the durability of the belt.

  The present invention has been made in view of the problems as described above, and an object thereof is to provide a continuously variable transmission that has a simple configuration and can transmit power without using a belt or the like. It is to be.

  The continuously variable transmission according to the present invention is in contact with the main surface of the fixed sheave and the fixed sheave that is rotatably provided by a power source, and is movable in the radial direction of the fixed sheave. A movable sheave provided to be rotated by power transmitted from a fixed sheave, an output section that is disposed at a distance from the movable sheave and is rotatably provided, and connected to the output section and the movable sheave. And a constant velocity joint capable of transmitting power from the movable sheave to the output unit.

  Preferably, the main surface of the fixed sheave with which the movable sheave contacts is separated from a virtual plane extending in a direction perpendicular to the rotation axis of the fixed sheave from the root of the main surface toward the outer peripheral edge of the movable sheave. Tilt. Preferably, an actuator for positioning the movable sheave is further provided.

  Preferably, the movable sheave is in contact with the main surface of the fixed sheave and is provided with a disk-like contact member rotatably provided around the output rotation axis, and in the extending direction of the output rotation axis from the contact member. A rotating member including a convex portion projecting toward the cylinder, a cylinder portion that engages the convex portion in the rotation direction of the contact member, and supports the convex portion so as to be movable in the extending direction of the output rotation axis; And a bearing portion that rotatably supports the cylinder portion. The actuator is connected to the bearing portion, and displaces the movable sheave in a direction intersecting the rotation axis of the fixed sheave. The second hydraulic actuator includes a first convex portion and a cylinder portion. Including.

  Preferably, the first actuator displaces the movable sheave in a direction orthogonal to the rotation axis of the fixed sheave.

  Preferably, the movable sheave is arranged so that the rotation axis of the fixed sheave and the output rotation axis are in parallel.

  According to the continuously variable transmission according to the present invention, the continuously variable transmission can be configured with a simple configuration, and power can be transmitted without using a belt or the like.

A continuously variable transmission according to the present embodiment will be described with reference to FIGS.
Note that in the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. In the following embodiments, each component is not necessarily essential to the present invention unless otherwise specified. In addition, when there are a plurality of embodiments below, it is planned from the beginning to appropriately combine the features of each embodiment unless otherwise specified.

(Embodiment 1)
A drive system that employs an FF (Front Engine / Front Wheel Drive) drive system and that has an engine and a continuously variable transmission placed laterally with respect to the vehicle will be described with reference to FIGS.

  FIG. 1 is a side view of a part of a continuously variable transmission 100 according to an embodiment of the present invention, and FIG. 2 is a plan view of the continuously variable transmission 100 of a part. As shown in FIG. 1, the continuously variable transmission 100 is applied with power from an engine (power source) 106, and an input shaft 103 that rotates about a rotation center line O <b> 1 and a circle fixed to the input shaft 103. A plate-shaped fixed sheave 101 and a movable sheave 102 that is in contact with the contact surface 140 of the fixed sheave 101, transmits power from the contact surface 140, and is rotatable about the rotation center line O3 are provided. In the present embodiment, the movable sheave 102 is arranged so that the rotation center line O3 of the movable sheave 102 and the rotation center line O1 are substantially parallel. The radius r1 of the fixed sheave 101 is larger than the radius r2 of the movable sheave 102. In the example shown in FIG. 1, the fixed sheave 101 is provided at a position adjacent to the engine 106 in the vehicle width direction.

  The continuously variable transmission 100 is provided at a distance from the movable sheave 102, and the final gear 104 that meshes with the differential gear 105, the constant velocity joint 125 that connects the final gear 104 and the movable sheave 102, and the movable sheave 102. And hydraulic actuators 115 and 120 for adjusting the position of the contact point P of the movable sheave 102 and the fixed sheave 101.

  The continuously variable transmission 100 transmits power to the movable sheave 102 by bringing the movable sheave 102 into direct contact with the fixed sheave 101, and transmits the power from the movable sheave 102 to the final gear 104 and the differential gear 105 via the constant velocity joint 125. Power can be transmitted. Further, the gear ratio can be changed by adjusting the contact point P between the fixed sheave 101 and the movable sheave 102. That is, when the contact point P is displaced, the distance r3 from the contact point P to the rotation center line O1 changes, and the gear ratio when power is transmitted from the fixed sheave 101 to the movable sheave 102 also changes.

  Here, compared with the conventional continuously variable transmission, the movable sheave corresponding to the fixed sheave 101, the hydraulic actuator for displacing the movable sheave, the fixed sheave corresponding to the movable sheave 102, the belt, and the like can be omitted. The number of points can be reduced. Accordingly, the continuously variable transmission 100 can be made compact. Furthermore, power is not transmitted through the belt, and transmission efficiency can be improved by contact between the steel blocks of the belt, and no adverse effects such as wear of the steel block occur.

  The main surface of the fixed sheave 101 is arranged in the direction of the rotation center line O1, and the contact surface 117 of the movable sheave 102 is in contact with one of the contact surfaces 140 thereof.

  The continuously variable transmission 100 includes hydraulic actuators 115 and 120 that adjust the contact position between the contact surface 117 of the movable sheave 102 and the contact surface 140 of the fixed sheave 101 by positioning the movable sheave 102. .

  Specifically, the continuously variable transmission 100 adjusts the position of the movable sheave 102 in the direction perpendicular to the rotation center line O3 and the hydraulic actuator 115 that adjusts the position of the movable sheave 102 in the extending direction of the rotation center line O3. The hydraulic actuator 120 is provided. The movable sheave 102 is displaced and positioned in the radial direction of the fixed sheave 101 with respect to the fixed sheave 101 by the hydraulic actuator 115 and the hydraulic actuator 120.

  The contact surface 140 is inclined so as to move away from the virtual plane S perpendicular to the rotation center line O1 from the root of the contact surface 140 toward the outer peripheral edge side of the fixed sheave 101. The back surface 141 extends in a direction perpendicular to the rotation center line O1, and the contact surface 140 is inclined so as to approach the back surface 141 toward the outer peripheral edge side of the fixed sheave 101. .

  Further, the contact surface 117 of the disk member 116 is inclined so as to coincide with the contact surface 140. Even if the contact surface 117 of the disk member 116 is worn over time, the disk member 116 is worn along the contact surface 140. Therefore, even after the wear, the contact surface 117 is not connected to the contact surface 140. A similar tilt state is maintained.

  Therefore, the hydraulic actuators 115 and 120 press the contact surface 117 toward the contact surface 140, so that the contact surface 117 and the contact surface 140 after wear can be brought into good contact with each other. For this reason, even if the contact surface 117 is worn, the contact state between the contact surface 117 of the movable sheave 102 and the contact surface 140 of the fixed sheave 101 can be satisfactorily maintained.

  The movable sheave 102 includes a contact member 110, a cylinder member 112 that supports the contact member 110 so as to be movable in the extending direction of the rotation center line O3, and a bearing portion 111 that is fixed to the outer periphery of the cylinder member 112. .

  The contact member 110 includes a disk member 116 formed in a disk shape, and a rod portion 114 protruding from the disk member 116 in the extending direction of the rotation center line O3. A contact surface 117 is formed on the outer peripheral edge of the main surface facing the fixed sheave 101 among the main surfaces of the disk member 116.

  The rod portion 114 is formed on the main surface located on the opposite side of the main surface of the disk member 116 with respect to the main surface on which the contact surface 117 is formed.

  The cylinder member 112 has a hole 113 that can receive the rod portion 114.

  As shown in FIGS. 1 and 2, the rod portion 114 has a substantially rectangular parallelepiped shape, and can be engaged with the cylinder member 112 in the rotation direction of the disk member 116. Furthermore, the rod part 114 is fitted in the hole 113 so as to be movable in the direction of the rotation center line O3.

  A hydraulic chamber 109 filled with oil is defined by the inner surface of the cylinder member 112 that defines the hole 113 and the rod 114. A hydraulic pipe (not shown) is connected to the hydraulic chamber 109, and the positioning adjustment of the contact member 110 in the direction of the rotation center line O3 is performed by the amount of oil and the oil pressure supplied into the hydraulic chamber 109, and the contact surface The contact surface pressure between 117 and the contact surface 140 is adjusted.

  As described above, the hydraulic actuator 115 is configured by the cylinder member 112 in which the hole 113 is formed and the rod portion 114 of the contact member 110 fitted in the cylinder member 112.

  The hydraulic actuator 120 includes a cylinder portion 122 and a rod portion 121 that is slidably provided in the cylinder portion 122.

  The tip of the rod 121 is engaged with the outer race 144 of the bearing 111 and is provided so as to be movable in the direction of the rotation center line O3 with respect to the bearing 111.

  3 is a cross-sectional view taken along line III-III in FIG. As shown in FIG. 3, the bearing portion 111 includes an outer race 144 formed in an annular shape, an inner race 142 that is disposed on the inner diameter side of the outer race 144 and supports the circumferential surface of the cylinder member 112, and an inner race 142. And a ball 143 provided between the outer races 144.

  The inner race 142 is shrink-fitted on the peripheral surface of the cylinder member 112, while the position of the outer race 144 is fixed.

  A slider mechanism 150 is provided on the outer peripheral surface of the outer race 144. The slider mechanism 150 includes a guide groove defining member 151 fixed to the outer peripheral surface of the outer race 144, and a roller mechanism 155 provided at the upper end portion of the rod portion 121.

  The roller mechanism 155 includes a shaft portion 153 that is rotatably inserted into a through hole 154 formed in the upper end portion of the cylinder portion 122, and rotating members 152 and 156 that are rotatably provided at both ends of the shaft portion 153. I have.

  The guide groove defining member 151 extends in the direction of the rotation center line O3 shown in FIG. 1, and defines a rail groove 157 and a rail groove 158 extending in the direction of the rotation center line O3. The rotating member 152 is provided to be movable in the rail groove 157, and the rotating member 156 is provided to be movable in the rail groove 158.

  Here, in FIGS. 1 and 3, when the hydraulic actuator 120 displaces the movable sheave 102 in the extending direction of O1, the rotating members 152 and 156 cause the inner surface of the guide groove defining member 151 to be the rotation center line O1. Press towards. Further, when the hydraulic actuator 120 displaces the movable sheave 102 away from the rotation center line O1, the rotation members 152 and 156 press the inner surface of the guide groove defining member 151 away from the rotation center line O1. As described above, the hydraulic actuator 120 moves the movable sheave 102 in a direction perpendicular to the rotation center line O1, and positions the movable sheave 102 in a direction perpendicular to the rotation center line O1.

  The constant velocity joint 125 includes a shaft 126, a connection mechanism 127 that connects one end of the shaft 126 and the final gear 104, and a connection mechanism 128 that connects the other end of the shaft 126 and the cylinder member 112. Yes.

  The connection mechanism 128 connects the shaft 126 to the end of the cylinder 122 opposite to the end where the opening of the hole 113 is formed, and the shaft 126.

  FIG. 4 is a cross-sectional view of the connection mechanism 128. As shown in FIG. 4, the connection mechanism 128 includes an outer race 212 integrally connected to the end of the cylinder member 112, an inner race 222 provided on the outer peripheral surface of the end of the shaft 126, and an inner race. 222 and the outer race 212, and a cage 231 that holds the ball 230.

  The outer race 212 is formed in a bottomed hollow hemispherical shape with an opening 213 formed at the tip, and a substantially spherical inner spherical surface 215 is formed on the inner peripheral surface of the outer race 212. .

  Inner spherical ball grooves 216 are formed in the inner spherical surface 215 at equal intervals in the circumferential direction of the outer race 212 when the outer race 212 is viewed from the front. The inner sphere ball groove 216 is curved along the outer peripheral surface of the ball 230 and extends toward the rotation center line direction of the cylinder member 112.

  An outer sphere ball groove 226 is formed on the outer peripheral surface of the inner race 222 at intervals in the circumferential direction so as to correspond to the inner sphere ball groove 216. The outer sphere ball groove 226 extends in the direction of the rotation center line O4 of the shaft 126 and is curved along the outer peripheral surface of the ball 230.

  The inner race 222 is formed in a cylindrical shape, and a spline 224 is formed on the inner peripheral surface of the inner race 222 at intervals and extending toward the rotation center line O4 of the shaft 126. A groove portion 223 corresponding to the spline 224 is formed on the outer peripheral surface of the shaft 126, and the inner race 222 is inserted into the inner race 222. Thereby, the inner race 222 and the shaft 126 are engaged with each other in the rotation direction.

  The cage 231 is formed in an annular shape, and is disposed between the inner peripheral surface of the outer race 212 and the outer peripheral surface of the inner race 222. In the cage 231, ball holding windows 232 are formed at intervals in the circumferential direction in portions corresponding to the inner sphere ball groove 216 and the outer sphere ball groove 226.

  Each ball 230 is fitted in the ball holding window 232 and is engaged with both the inner ball ball groove 216 and the outer ball ball groove 226.

  In this connection mechanism 128, the ball 230 moves in the inner ball ball groove 216 and the outer ball ball groove 226, so that the shaft 126 fitted to the inner race 222 is swingably connected to the outer race 212. Then, the cylinder member 112 and the shaft 126 are coupled to each other in a state in which constant speed transmission of rotation is maintained.

  In FIG. 1, the connection mechanism 127 is similarly configured. The connection mechanism 127 is provided between the outer race formed on the end face of the final gear 104 facing the cylinder member 112, the inner race provided on the end of the shaft 126, and the outer race and the inner race. A ball and a cage for holding the ball are provided.

  By this connection mechanism 127, the final gear 104 and the shaft 126 are slidably connected to each other. Further, constant speed transmission of rotation between the shaft 126 and the final gear 104 is maintained.

  Here, as shown in FIG. 2, the bearing portion 111 is provided with a slider mechanism 130. The slider mechanism 130 includes a guide protrusion 132 formed on the outer peripheral surface of the outer race 144 of the bearing portion 111 and a guide 131 that defines a groove that can receive the guide protrusion 132. As shown in FIG. 1, the guide 131 extends in an arc shape with the connection mechanism 127 as the center. The movable sheave 102 is displaced while being guided by the guide 131. The guide 131 is fixed to the vehicle body.

  FIG. 5 is a side view of the continuously variable transmission 100 showing a state where the gear is shifted from the state shown in FIG. 1 to the high speed side. In the state shown in FIG. 5, the movable sheave 102 is displaced to the outer peripheral edge side of the fixed sheave 101 from the state shown in FIG. 1.

  When the hydraulic actuator 115 and the hydraulic actuator 120 are driven, the movable sheave 102 is displaced from the position shown in FIG. 1 to the position shown in FIG.

  At this time, the cylinder member 112 is displaced along the guide 132 and displaced about the connection mechanism 127. The hydraulic actuator 115 urges the rod portion 114 to protrude from the cylinder member 112 so that the contact state between the disc member 116 and the fixed sheave 101 is maintained.

  Further, the hydraulic actuator 120 urges the movable sheave 102 toward the outer peripheral edge side of the fixed sheave 101 in a direction perpendicular to the rotation center line O1.

  Specifically, when the rod portion 121 is driven so as to be accommodated in the cylinder portion 122, the rotating members 152 and 156 provided at the distal end portion of the rod portion 121 cause the inner peripheral surface of the guide groove defining member 151 to be Is pressed toward the radially outer side of the fixed sheave 101.

  Thus, when the guide groove defining member 151 is pressed, the movable sheave 102 starts to be displaced toward the radially outer side of the fixed sheave 101.

  At this time, since the bearing portion 111 is engaged with the guide 132, the bearing portion 111 and the cylinder member 112 move on a virtual circle centering on the connection mechanism 127 while being guided by the guide protrusion 132.

  Thus, since the bearing portion 111 moves in an arc shape, the rotating member 152 and the rotating member 156 move in the rail groove 157 and the rail groove 158 toward the rotation center line O3.

  Thus, the movable sheave 102 can be moved by the hydraulic actuator 120 and the hydraulic actuator 115 while maintaining the contact state between the movable sheave 102 and the fixed sheave 101, and between the fixed sheave 101 and the movable sheave 102. The gear ratio can be changed sequentially.

  Even if the movable sheave 102 is displaced toward the outer peripheral edge of the fixed sheave 101, the constant velocity joint 125 maintains the constant velocity transmission from the cylinder member 112 to the final gear 104.

  In the example illustrated in FIGS. 1 to 5, the example in which the contact surface 140 of the fixed sheave 101 is an inclined surface has been described.

  Therefore, a modification of continuously variable transmission 100 according to the first embodiment will be described with reference to FIG. FIG. 6 is a side view showing a modification of continuously variable transmission 100 according to the first embodiment. 6 that are the same as or correspond to the configurations shown in FIG. 1 to FIG. 5 are given the same reference numerals and explanations thereof are omitted.

  In FIG. 6, the contact surface 140 of the fixed sheave 101 is a flat surface extending in a direction substantially perpendicular to the rotation center line O1.

  An annular protrusion 133 formed in an annular shape is formed on the main surface of the disk member 116 that faces the contact surface 140. The annular protrusion 133 extends in an annular shape around the rotation center line O3. The tip of the annular protrusion 133 has a curved surface shape, and the tip of the annular protrusion 133 is in contact with the contact surface 140 at the contact point P.

  In the continuously variable transmission 100 shown in FIG. 6, the position of the contact point P is maintained while the contact state between the annular protrusion 133 and the contact surface 140 is maintained by driving the hydraulic actuator 120 and the hydraulic actuator 115. Is appropriately displaced toward the outer peripheral edge of the contact surface 140, so that the gear ratio can be sequentially changed.

(Embodiment 2)
7 and 8, a description will be given of a front engine / front wheel drive (FF) drive system, in which the engine and the continuously variable transmission are vertically placed with respect to the vehicle.

  7 and 8, the same or corresponding components as those shown in FIGS. 1 to 6 are given the same reference numerals and description thereof is omitted.

  FIG. 7 is a side view of continuously variable transmission 100 according to Embodiment 2 of the present invention, and FIG. 8 is a continuously variable transmission 100 that shows a state where the gear is shifted from the state shown in FIG. FIG.

  In FIG. 7, the fixed sheave 101 is disposed on the rear side of the vehicle with respect to the engine 106. And the fixed sheave 101 is rotatably arranged so that the rotation center line O1 of the fixed sheave 101 extends in the front-rear direction of the vehicle.

  Furthermore, the movable sheave 102 is disposed on the vehicle rear side with respect to the fixed sheave 101. The movable sheave 102 is arranged such that the rotation center line O3 of the movable sheave 102 extends in the vehicle width direction. Thus, the fixed sheave 101 and the movable sheave 102 are arranged such that the rotation center line O1 and the rotation center line O3 intersect each other. The guide 132 extends on a virtual circle centered on the connection mechanism 127.

  In the example shown in FIGS. 7 and 8, the hydraulic actuator 115 displaces the disk member 116 in a direction perpendicular to the rotation center line O1, and the hydraulic actuator 120 causes the disk member 116 to rotate the rotation center line O1. Displace in the extending direction.

  The gear ratio is changed by the hydraulic actuator 115 and the hydraulic actuator 120 displacing the disk member 116 from the position shown in FIG. 7 as shown in FIG.

  In the present specification, a description is given of a continuously variable transmission that employs an FF drive system. However, the present invention is not limited to this, and is not limited to this. FR (Front Engine Rear Drive), MR (Mid-ship engine Rear drive), It can also be applied to (Rear Engine Rear Drive) drive type continuously variable transmissions.

  Although the embodiment of the present invention has been described above, it should be considered that the embodiment disclosed this time is illustrative and not restrictive in all respects. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims. Furthermore, the above numerical values are examples, and are not limited to the above numerical values and ranges.

  The present invention is suitable for a continuously variable transmission.

1 is a side view of a part of a continuously variable transmission according to an embodiment of the present invention as viewed in cross section. It is a top view of the continuously variable transmission which looked at a part in cross section. It is sectional drawing in the III-III line of FIG. It is sectional drawing of a connection mechanism. FIG. 2 is a side view of a continuously variable transmission that shows a state in which a gear is shifted from the state shown in FIG. 1 to a high speed side. It is a side view which shows the modification of the continuously variable transmission which concerns on this Embodiment. 1 is a side view of a continuously variable transmission according to an embodiment of the present invention. FIG. 8 is a side view of the continuously variable transmission showing a state in which the gear is shifted from the state shown in FIG. 7 to the high speed side.

Explanation of symbols

  100 continuously variable transmission, 101 fixed sheave, 102 movable sheave, 103 input shaft, 104 final gear, 105 differential gear, 106 engine, 109 hydraulic chamber, 110 contact member, 111 bearing portion, 112 cylinder member, 113 hole portion, 114 Rod part, 115, 120 Hydraulic actuator, 125 Constant velocity joint.

Claims (6)

A disk-shaped fixed sheave that is rotatably provided by power from a power source;
A movable sheave that comes into contact with the main surface of the fixed sheave and that is movable in the radial direction of the fixed sheave, and that can be rotated by power transmitted from the fixed sheave;
An output unit disposed at an interval with respect to the movable sheave and rotatably provided;
A constant velocity joint connected to the output portion and the movable sheave and capable of transmitting power from the movable sheave to the output portion;
A continuously variable transmission.   The main surface of the fixed sheave with which the movable sheave contacts is separated from a virtual plane extending in a direction perpendicular to the rotation axis of the fixed sheave from the root portion of the main surface toward the outer peripheral edge of the movable sheave. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is inclined to the left.   The continuously variable transmission according to claim 1 or 2, further comprising an actuator for positioning the movable sheave. The movable sheave is in contact with the main surface of the fixed sheave and is provided with a disk-shaped contact member that is rotatable about an output rotation axis, and the extending direction of the output rotation axis from the contact member A rotating member including a convex portion protruding toward the surface;
A cylinder portion that engages with the convex portion in the rotation direction of the contact member and supports the convex portion so as to be movable in the extending direction of the output rotation axis.
A bearing portion provided on an outer periphery of the cylinder portion and rotatably supporting the cylinder portion;
The actuator includes a first hydraulic actuator connected to the bearing portion and displacing the movable sheave in a direction intersecting a rotation axis of the fixed sheave, a first convex portion, and a cylinder portion. The continuously variable transmission according to claim 3, comprising two hydraulic actuators.   The continuously variable transmission according to claim 4, wherein the first actuator displaces the movable sheave in a direction orthogonal to a rotation axis of the fixed sheave.   The continuously variable transmission according to claim 4 or 5, wherein the movable sheave is arranged such that a rotation axis of the fixed sheave and the output rotation axis are parallel to each other.

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