JP6133116B2 - One-way clutch and continuously variable transmission - Google Patents

Description

  The present invention relates to a one-way clutch and a continuously variable transmission using the one-way clutch.

  Patent Document 1 discloses a continuously variable transmission that converts the rotation of an input shaft connected to an engine into a reciprocating motion of a connecting rod, and converts the reciprocating motion of the connecting rod into a rotating motion of an output shaft by a one-way clutch. Yes.

JP 2012-1048 A

  A configuration of a one-way clutch used in a conventional continuously variable transmission will be described with reference to FIGS. The one-way clutch 1321 is basically formed between a circular inner peripheral surface 1322a of an annular outer member 1322 and an outer peripheral surface 1323a bent in a wave shape of a cylindrical inner member 1323 disposed coaxially inside the outer member 1322. A roller 1325 is arranged in an annular space formed in the above. In order to form a wedge-shaped space with which the roller 1325 engages between the inner peripheral surface 1322a of the outer member 1322 and the outer peripheral surface 1323a of the inner member 1323, the outer peripheral surface 1323a of the inner member 1323 bent in a wave shape is The member 1322 has a peripheral surface inclined with respect to the circular inner peripheral surface 1322a.

  An annular groove 1322c is formed in the inner peripheral surface 1322a of the outer member 1322, and an annular ring spring 1339 is disposed in the annular groove 1322c. The ring spring 1339 abuts on the circumferential surface of the roller 1325 and urges toward the outer circumferential surface 1323a of the inner member 1323.

  A connecting rod 1319 is connected to protrusions 1322b and 1322b provided on the outer periphery of the outer member 1322 via pins 1319c and clips 1340 and 1340. Between the outer member 1322 and the inner member 1323, a pair of ball bearings 1334, 1334 located on both sides in the axial direction of the roller 1325 are disposed, and the outer member 1322 and the inner member 1323 are the same by the ball bearings 1334, 1334. It is connected so that relative rotation is possible while maintaining the core state. The inner member 1323 is held by the outer member 1322 by the shims 1351 and 1351 and the clips 1352 and 1352 arranged on both sides of the ball bearings 1334 and 1334.

  The one-way clutch 1321 includes an engagement spring 1324 for urging the roller 1325 in the circumferential direction of the annular space and a cage 1331 for supporting the engagement spring 1324. The cage 1331 includes a pair of annular members 1332 and 1332 made of an annular plate material, and a support rod 1333 that is arranged at equal intervals in the circumferential direction and connects the pair of annular members 1332 and 1332 to each other. The engage spring 1324 is fixed to the support rod 1333 of the cage 1331. An axial spring 1338 is disposed between one ball bearing 1334 and one annular member 1332 of the cage 1331, and a plurality of protrusions 1338 a protruding from the inner periphery of the axial spring 1338 are elastically formed on the end surface of the roller 1325. Abut.

  The roller 1325 engages with a wedge-shaped space formed between the inner peripheral surface 1322a of the outer member 1322 and the outer peripheral surface 1323a of the inner member 1323, whereby the one-way clutch 1321 is engaged. When the roller 1325 is pushed out from a wedge-shaped space between the inner peripheral surface 1322a of the outer member 1322 and the outer peripheral surface 1323a of the inner member 1323, the roller 1325 is centrifugally and the inner peripheral surface of the outer member 1322 positioned radially outward. The centrifugal force acting on the roller 1325 is suppressed by the radially inward force of the ring spring 1339 (ring spring force). In the damping state after disengagement, the one-way clutch 1321 urges the roller 1325 with the engagement spring 1324 and pushes it back to the datum point standby position indicating the state immediately before the one-way clutch is engaged.

  FIG. 14A is a schematic view of the one-way clutch 1321 as viewed from the direction of the arrow 1350, and FIG. 14B is a schematic view showing a cross section AA of the one-way clutch of FIG. As shown in FIG. 14B, the annular ring spring 1339 abuts on the circumferential surface of the roller 1325 at the central portion in the axial direction of the roller 1325 and urges toward the outer circumferential surface 1323a of the inner member 1323. A radially inward force F (ring spring force) by the ring spring 1339 urges the roller 1325 toward the outer peripheral surface 1323a.

  FIG. 15 shows a configuration in which a roller 1325 disposed in a space between the inner peripheral surface 1322a of the outer member and the outer peripheral surface 1323a of the inner member is urged in the left direction of the paper surface by an engagement spring 1324 fixed to the support rod 1333. FIG. The outer peripheral surface 1323a of the inner member 1323 that bends in a wavy shape has an outer peripheral surface that is inclined with respect to the circular inner peripheral surface 1322a of the outer member 1322, and this inclination causes the inner peripheral surface 1322a of the outer member 1322 to be in contact with the inner surface. A wedge-shaped space in which the roller 1325 engages is formed between the outer periphery 1323a of the member 1323.

  The biasing force (ring spring force F) of the ring spring 1339 biases the roller 1325 toward the outer peripheral surface 1323a, but the outer peripheral surface 1323a of the inner member 1323 is inclined with respect to the inner peripheral surface 1322a of the outer member 1322. Therefore, the urging force (ring spring force F) of the ring spring does not act in a direction orthogonal to the outer peripheral surface 1323a as shown in FIG. 15, but acts in an oblique direction on the outer peripheral surface 1323a of the inner member. . Therefore, as a component of the force of the ring spring force F, the roller 1325 is orthogonal to the tangential force f1 of the outer peripheral surface of the inner member that contacts the outer peripheral surface 1323a of the inner member and the tangential direction of the outer peripheral surface 1323a of the inner member. Force f <b> 2 in the direction to be generated. The tangential force f1 on the outer peripheral surface of the inner member acts in a direction that cancels the force (pressing force) that biases the roller 1325 by the engagement spring 1324. Therefore, even if the roller 1325 is biased by the engagement spring 1324, the roller The pressing force of the engagement spring 1324 transmitted to 1325 is insufficient, the roller 1325 does not return to the datum point standby position, the posture of the roller 1325 becomes unstable, and the stable engagement of the one-way clutch may be prevented.

  In view of the above-described circumstances, an object of the present invention is to provide a one-way clutch excellent in damping performance and a continuously variable transmission using the one-way clutch by stabilizing the posture of the roller.

In order to achieve the above object, the present invention described in claim 1 includes an annular outer member,
An inner member disposed coaxially within the outer member;
A plurality of rollers disposed in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member;
A plurality of elastic members that respectively abut against the plurality of rollers and bias in the circumferential direction of the annular space;
A one-way clutch that transmits a driving force by engaging the roller between the inner peripheral surface and the outer peripheral surface by relative rotation of the outer member and the inner member in a predetermined direction;
The elastic member is
An engagement spring supported by a gauge fixed to the inner member;
The engagement spring includes a plurality of biasing portions juxtaposed in an axial direction intersecting a direction in which the roller moves in the annular space,
The biasing part is
A first biasing portion disposed at the center in the axial direction;
A second biasing portion disposed at a symmetrical position on both sides of the first biasing portion,
Before SL and end of the first biasing part is set longer on the roller side than the end of the second biasing section,
A one-way clutch is proposed in which a force opposite to the centrifugal force of the roller is applied to the roller by the first urging portion coming into contact with the roller .

Moreover, the present invention described in claim 2 includes an annular outer member,
An inner member disposed coaxially within the outer member;
A plurality of rollers disposed in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member;
A plurality of elastic members that respectively abut against the plurality of rollers and bias in the circumferential direction of the annular space;
A one-way clutch that transmits a driving force by engaging the roller between the inner peripheral surface and the outer peripheral surface by relative rotation of the outer member and the inner member in a predetermined direction;
The elastic member is
An engagement spring supported by a gauge fixed to the inner member;
The engagement spring includes a plurality of biasing portions juxtaposed in an axial direction intersecting a direction in which the roller moves in the annular space,
The biasing part is
A first biasing portion disposed at the center in the axial direction;
A second biasing portion disposed at a symmetrical position on both sides of the first biasing portion,
The one-way clutch is
A transmission state in which the roller meshes between the outer member and the inner member and torque transmission is possible;
The non-transmission state in which the engagement of the roller is disengaged between the outer member and the inner member, and torque transmission is impossible.
When the roller passes through a changing point from the transmission state to the non-transmission state, the first urging portion of the plurality of urging portions contacts the roller ,
A one-way clutch is proposed in which a force opposite to the centrifugal force of the roller is applied to the roller by the first urging portion coming into contact with the roller .

In the present invention described in claim 3, in addition to the configuration of claim 2, wherein the first biasing portion includes a first surface capable of contact with the roller, the at the end of the first surface A one-way clutch is proposed , which has a second surface that is bent toward the roller and has a second surface that can contact the roller at a position closer to the inner peripheral surface of the outer member than the first surface.

  According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, when the roller passes through the changing point, the first urging portion is connected to the roller on the second surface. A one-way clutch characterized by contact is proposed.

  Further, in the present invention described in claim 5, in addition to the configuration of claim 3, the urging portion includes a second urging portion having a first surface that can come into contact with the roller, In the transmission state, the second urging portion contacts the roller on the first surface, and the first urging portion contacts the roller on the first surface and the second surface. A clutch is proposed.

According to a sixth aspect of the present invention, the continuously variable transmission including the one-way clutch according to any one of the first to fifth aspects, wherein the rotation of the input shaft is shifted and transmitted to the output shaft. The amount of eccentricity from the axis of the input shaft is variable, and an input side fulcrum that rotates together with the input shaft and an output side fulcrum provided on the outer member of the one-way clutch are connected by a connecting rod. A continuously variable transmission is proposed in which the inner member of the one-way clutch is connected to the output shaft.

According to the first aspect, engagement spring of the one-way clutch, the roller comprises a plurality of urging units juxtaposed in the axial direction intersecting the direction of movement of the annular space, among the plurality of urging units Since the end portion of the first urging portion is set longer on the roller side than the end portion of the second urging portion, the centrifugal force of the roller acting on the outer member side when the roller returns from the torque transmission state. It becomes possible to cancel, and it becomes possible to stabilize the posture of the roller. Further, the urging portion has a first urging portion disposed at the center in the axial direction and a second urging portion disposed at symmetrical positions on both sides of the first urging portion, so that the rollers are evenly distributed. A stable pressing force can be applied to stabilize the posture of the roller.

According to the second aspect of the present invention, when the roller passes through the changing point from the transmission state in which torque transmission is possible to the non-transmission state in which torque transmission is impossible, the first urging unit among the urging units By contacting the roller, the posture of the roller can be stabilized before the non-transmission state. Further, the urging portion has a first urging portion disposed at the center in the axial direction and a second urging portion disposed at symmetrical positions on both sides of the first urging portion, so that the rollers are evenly distributed. A stable pressing force can be applied to stabilize the posture of the roller.

Further, according to the configuration of claim 3, the first biasing portion includes a first surface capable of contacting with the rollers, bent to the roller side end portion of the first surface, of the outer member than the first surface position and the second surface and the roller that can contact with the peripheral surface, to have a, it is possible to apply a force of the centrifugal force against the component with respect to the roller.

  According to the fourth aspect of the present invention, when the roller passes through the changing point, the first urging portion is in contact with the roller on the second surface, thereby stabilizing the posture of the roller before the non-transmission state. In this way, it is possible to apply a force against the centrifugal force to the roller.

  According to the fifth aspect of the present invention, in the non-transmission state, the second urging portion contacts the roller on the first surface, and the first urging portion contacts the roller on the first surface and the second surface. As a result, it is possible to apply a pressing force to the roller while applying a force against the centrifugal force.

According to the sixth aspect of the present invention, the one-way clutch of the present invention is applied to a continuously variable transmission that shifts the rotation of the input shaft and transmits it to the output shaft. The continuously variable transmission has a variable amount of eccentricity from the axis of the input shaft, and an input side fulcrum that rotates together with the input shaft and an output side fulcrum provided on the outer member of the one-way clutch are connected by a connecting rod. Since the inner member of the clutch is connected to the output shaft, when the input shaft rotates and the connecting rod reciprocates, the one-way clutch is intermittently engaged and the output shaft rotates to transmit the driving force. At this time, the operation of the one-way clutch of the present invention is stabilized, so that the power transmission performance of the continuously variable transmission is enhanced.

The skeleton figure of the power transmission device for vehicles. FIG. 2 is a detailed view of part 2 of FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (TOP state). FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (LOW state). The action explanatory view in the TOP state. The action explanatory view in the LOW state. The disassembled perspective view of a one-way clutch. The perspective view of a cage and an engagement spring. 9 is an enlarged view of 9 parts in FIG. The figure which illustrates the engagement state of a one-way clutch. The figure which illustrates the DP state of a one-way clutch. The figure which illustrates the damping state of a one-way clutch. The disassembled perspective view of the conventional one-way clutch. The figure which shows the structure of the conventional one-way clutch. The figure which shows the structure of the conventional one-way clutch.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. As shown in FIG. 1, the vehicle power transmission device for transmitting the driving force of the engine E to the drive wheels W, W via the left and right axles 10, 10 includes a crank type continuously variable transmission T and a differential gear D. Prepare.

  Next, the structure of the continuously variable transmission T will be described with reference to FIGS. As shown in FIG. 2, the continuously variable transmission T according to the present embodiment is obtained by superimposing a plurality (four in the embodiment) of power transmission units U having the same structure in the axial direction. These power transmission units U include a common input shaft 11 and a common output shaft 12 arranged in parallel, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Hereinafter, the structure of one power transmission unit U will be described as a representative. The input shaft 11 connected to the engine E and rotates passes through the hollow rotating shaft 14a of the speed change actuator 14 such as an electric motor so as to be relatively rotatable. The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the casing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 and can rotate relative to the input shaft 11 at a different speed.

  A first pinion 15 is fixed to the input shaft 11 passing through the rotation shaft 14 a of the speed change actuator 14, and a crank-shaped carrier 16 is connected to the rotation shaft 14 a of the speed change actuator 14 so as to straddle the first pinion 15. The Two second pinions 17, 17 having the same diameter as the first pinion 15 are supported via pinion pins 16 a, 16 a at positions forming an equilateral triangle in cooperation with the first pinion 15, respectively. The first pinion 15 and the second pinions 17, 17 mesh with a ring gear 18 a formed eccentrically inside a disc-shaped eccentric disk 18. A ring portion 19 b provided at one end of the rod portion 19 a of the connecting rod 19 is fitted to the outer peripheral surface of the eccentric disk 18 via a ball bearing 20 so as to be relatively rotatable.

  A one-way clutch 21 provided on the outer periphery of the output shaft 12 is arranged inside the outer member 22 with a ring-shaped outer member 22 pivotally supported by a rod portion 19a of a connecting rod 19 via a pin 19c. 12 and an inner member 23 fixed to 12 and a roller 25 disposed in a wedge-shaped space formed between the outer member 22 and the inner member 23 and biased by an engagement spring 24 (elastic member). The specific structure of the one-way clutch 21 will be described in detail later.

  As is apparent from FIG. 2, the four power transmission units U share the crank-shaped carrier 16, but the phases of the eccentric discs 18 supported by the carrier 16 via the second pinions 17 and 17 are respectively. The power transmission unit U differs by 90 °. For example, in FIG. 2, the eccentric disk 18 of the leftmost power transmission unit U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third power transmission unit U from the left is relative to the input shaft 11. The eccentric discs 18 and 18 of the second and fourth power transmission units U and U from the left are located in the middle in the vertical direction.

  Next, the structure of the one-way clutch 21 will be described with reference to FIGS. 3 to 6, the one-way clutch 21 is schematically shown, and the actual structure is shown in FIGS.

  The one-way clutch 21 according to the present embodiment basically includes a circular inner peripheral surface 22a of an annular outer member 22 and an outer peripheral surface that bends in a wave shape of a cylindrical inner member 23 that is coaxially disposed inside the outer member. Twelve rollers 25 are arranged in an annular space formed between the roller 23a and the outer space 23a. The connecting rod 19 is connected to the projecting portions 22b and 22b provided on the outer periphery of the outer member 22 via pins 19c and clips 40 and 40, and the output shaft 12 is coupled to the inner peripheral portion of the inner member 23 so as not to be relatively rotatable. The

  The one-way clutch 21 includes a cage 31 for supporting an engagement spring 24 that biases the roller 25 in the circumferential direction of the annular space. The cage 31 includes a pair of annular members 32 and 32 made of an annular plate material, and twelve spring support rods 33 that are arranged at equal intervals in the circumferential direction and connect the pair of annular members 32 and 32 to each other. ing. A pair of annular members 32, 32 are disposed on both axial sides of the twelve rollers 25, and twelve spring support rods 33 are disposed between the twelve rollers 25. The inner peripheral portion of the annular member 32 is formed in a corrugated shape, and the cage 31 is coupled to the inner member 23 so as not to be relatively rotatable by engaging with the corrugated outer peripheral surface 23 a of the inner member 23.

  The engagement spring 24 is composed of one elastic plate, and one end side of the engagement spring 24 is fixed to the spring support rod 33 of the cage 31 by welding or the like, and the other end side is divided by four parallel cuts 24a. Four urging portions 24b and one urging portion 24c are formed. The four urging portions 24b and the one urging portion 24c are arranged in a state where the rollers 25 are juxtaposed in the axial direction of the roller 25 that intersects the direction in which the roller 25 moves in the annular space. One urging portion 24c is arranged in the center of the roller 25 in the axial direction, and two urging portions 24b and 24b are arranged on the left and right sides of the urging portion 24c. The gist of the present invention is not limited to this configuration example, and any configuration may be used as long as the urging portions 24b are arranged symmetrically with respect to the central urging portion 24c.

  Each of the urging portions 24 b has a first surface 24 b 1 that comes into contact with the roller 25. When the urging portion 24b comes into contact with the roller 25 by the first surface 24b1, the roller 25 is urged by the right and left equal pressing force, and the datum point (DP) standby position indicating the state immediately before the one-way clutch is engaged is set. Push back.

  Further, the urging portion 24c has a first surface 24c1 and a second surface 24c2. The first surface 24c1 of the urging portion 24c is configured in the same manner as the first surface 24b1 of the urging portion 24b, and when the urging portion 24c contacts the roller 25 by the first surface 24c1, the same as the urging portion 24b. It is possible to apply a pressing force to the roller 25.

  The second surface 24c2 of the urging portion 24c is bent at the end of the first surface 24c1, and the first surface 24c1 and the second surface 24c2 are formed in a “h” shape (FIG. 8). By configuring the second surface 24c2 to be bent, the end of the urging portion 24c is set longer on the roller 25 side than the end of the urging portion 24b. When the urging portion 24 c comes into contact with the roller 25 by the second surface 24 c 2, a force (centrifugal force resisting force) against the centrifugal force of the roller 25 is applied to the roller 25.

  Between the outer member 22 and the inner member 23, a pair of ball bearings 34, 34 located on both sides in the axial direction of the roller 25 are disposed, and the outer member 22 and the inner member 23 are the same by the ball bearings 34, 34. It is connected so that relative rotation is possible while maintaining the core state. The ball bearing 34 has a plurality of balls 37 disposed between an outer ring 35 and an inner ring 36, the outer ring 35 is formed integrally with the axial end of the outer member 22, and the inner ring 36 is configured as a separate member to form an inner member. 23 is fixed to the outer periphery. The ball bearings 34 are classified into a double row and a single row, and the two ball bearings 34 and 34 located at both axial ends of the four one-way clutches 21 are a single row, and the other three Since the ball bearings 34 are shared by the two adjacent one-way clutches 21 and 21, they form a double row.

  An axial spring 38 is disposed between one ball bearing 34 and one annular member 32 of the cage 31, and a plurality of protrusions 38 a protruding from the inner periphery of the axial spring 38 are provided on the inner periphery of the annular member 32. It passes between the recesses 32a and elastically contacts the end surface of the roller 25.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  First, the operation of one power transmission unit U of the continuously variable transmission T will be described. When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11, the carrier 16 rotates about the axis L <b> 1 of the input shaft 11. At this time, the center O of the carrier 16, that is, the center of the equilateral triangle formed by the first pinion 15 and the two second pinions 17, 17 rotates around the axis L 1 of the input shaft 11.

  3 and 5 show a state in which the center O of the carrier 16 is on the opposite side of the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The eccentricity is maximized and the ratio of the continuously variable transmission T is in the TOP state. 4 and 6 show a state in which the center O of the carrier 16 is on the same side as the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The amount of eccentricity is minimized and the ratio of the continuously variable transmission T is in the LOW state.

  In the TOP state shown in FIG. 5, when the input shaft 11 is rotated by the engine E and the rotation shaft 14 a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotation shaft 14 a, the carrier 16, With the one pinion 15, the two second pinions 17 and 17, and the eccentric disk 18 being integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from the state shown in FIG. 5A to the state shown in FIG. 5C, a ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by the pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of rotation of the outer member 22 in the arrow B direction.

  When the outer member 22 rotates in the direction of arrow B in this manner, the roller 25 is engaged in the wedge-shaped space between the outer member 22 and the inner member 23 of the one-way clutch 21, and the rotation of the outer member 22 is performed via the inner member 23. Since it is transmitted to the output shaft 12, the output shaft 12 rotates counterclockwise (see arrow C).

  When the input shaft 11 and the first pinion 15 further rotate, the eccentric disk 18 in which the ring gear 18a is engaged with the first pinion 15 and the second pinion 17, 17 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, a ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B '). 5C and 5A show both ends of rotation of the outer member 22 in the direction of arrow B ′.

  When the outer member 22 rotates in the direction of the arrow B ′ in this way, the roller 25 is pushed out from the wedge-shaped space between the outer member 22 and the inner member 23 while compressing the engagement spring 24, so that the outer member 22 is The output shaft 12 does not rotate by slipping with respect to the inner member 23.

  As described above, when the outer member 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the rotation direction of the outer member 22 is counterclockwise (see arrow B). The shaft 12 rotates intermittently.

  FIG. 6 shows the operation when the continuously variable transmission T is operated in the LOW state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 becomes zero. In this state, when the input shaft 11 is rotated by the engine E and the rotating shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotating shaft 14a, the carrier 16, the first pinion 15, 2 In a state where the second pinions 17 and 17 and the eccentric disk 18 are integrated, the input pin 11 is rotated eccentrically in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 18 is zero, the stroke of the reciprocating motion of the connecting rod 19 is also zero, and the output shaft 12 does not rotate.

  Therefore, if the speed change actuator 14 is driven and the position of the carrier 16 is set between the TOP state of FIG. 3 and the LOW state of FIG. 4, operation at an arbitrary ratio between the zero ratio and the predetermined ratio becomes possible.

  In the continuously variable transmission T, the phases of the eccentric disks 18 of the four power transmission units U arranged side by side are shifted from each other by 90 °, so that the four power transmission units U alternately transmit the driving force. In other words, that is, any one of the four one-way clutches 21 is always in an engaged state, so that the output shaft 12 can be continuously rotated.

  Next, the operation of the one-way clutch 21 will be described. FIG. 11 shows a DP (Datum Point) state of the one-way clutch 21, that is, a state immediately before the one-way clutch 21 is engaged. Of the five urging portions of the engagement spring 24, one urging portion 24c is disposed in the center (FIG. 11A). The urging portions 24b, 24b are arranged two by two symmetrically with respect to the urging portion 24c, and apply a bilaterally symmetrical pressing force F1 to the roller 25.

  When the outer member 22 rotates relative to the inner member 23 in the direction of arrow B from the engaged state of the one-way clutch 21 in FIG. 10, the roller 25 is moved in the direction of arrow B by the frictional force received from the outer member 22 and the inner member 23. It moves and leaves | separates from the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23. At this time, when the roller 25 comes into contact with the second surface 24c2 of the urging portion 24c, a force that opposes the centrifugal force of the roller 25 is applied to the roller 25.

  As shown in FIG. 11B, for example, when the force applied by the second surface 24c2 of the urging portion 24c acts in a direction orthogonal to the outer peripheral surface 23a of the inner member 23 (FIG. 11B). ) F2), no component of force acting in the tangential direction of the inner member 23 is generated (the component of force in the tangential direction of the inner member 23 is zero), and the applied force F2 counteracts the centrifugal force of the roller 25. To counteract centrifugal force.

  Further, when the force applied by the second surface 24c2 of the urging portion 24c is not orthogonal to the outer peripheral surface 23a of the inner member 23 and acts in an inclined direction (F3 in FIG. 11B), F3 As a force component, a force component f1 acting in the tangential direction of the inner member 23 and a force component f2 orthogonal to the outer peripheral surface 23a are generated. The force component f1 acts in the direction of pushing back the roller 25 together with the pressing force F1. Further, the force component f2 acts as a centrifugal force counteracting force against the centrifugal force of the roller 25. The force component f1 acts not in the direction of canceling out the pressing force F1 (f1 in FIG. 13) but in the direction in which the roller 25 is pushed back, so that the damping performance of the engagement spring is improved.

  In the DP state, the two urging portions 24b, 24b on the outer side in the axial direction of the roller 25 abut on the outer peripheral surface of the roller 25, and the roller 25 is placed between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23. Energize in the direction of biting. When the force component f1 is applied, the force component f1 also urges the roller 25 in a direction in which the roller 25 is engaged between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23.

  In the DP state, the one-way clutch 21 is not yet engaged, and the roller 25 is in contact with the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23 without being engaged.

  When the outer member 22 rotates relative to the inner member 23 in the direction of arrow A from the DP state, the roller 25 receives the biasing force received from the engagement spring 24 and the frictional force received from the outer member 22 and the inner member 23 in the direction of arrow A. The one-way clutch 21 is engaged by moving into the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23 (FIG. 10B). In the engaged state, the engagement spring 24 and the roller 25 are in a non-contact state (FIG. 10A), and the roller 25 is engaged between the outer member 22 and the inner member 23 in the engaged state of the one-way clutch 21. Thus, a transmission state in which torque transmission is possible is obtained. When the outer member 22 rotates relative to the inner member 23 in the direction of arrow B from the engaged state of the one-way clutch 21 shown in FIG. 10, the roller 25 is engaged with the engagement spring 24 by the frictional force received from the outer member 22 and the inner member 23. The one-way clutch as shown in FIG. 12 by moving in the direction of arrow B against the urging force received from the outer member 22 and separating from the wedge-shaped space between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23. 21 is disengaged. This state is called a damping state. In the damping state, the engagement of the roller 25 is disengaged between the outer member 22 and the inner member 23, resulting in a non-transmission state where torque cannot be transmitted.

  When the roller 25 passes through a changing point (datum point) from the engaged state where the torque can be transmitted to the damping state, first, the urging portion 24 c comes into contact with the roller 25. When the urging portion 24 c comes into contact with the roller 25, a force (centrifugal force resisting force) that opposes the centrifugal force of the roller 25 is applied to the roller 25.

  In the damping state, the roller 25 rotates in the direction of arrow B while compressing all the urging portions 24b of the engagement spring 24, and the roller 25 is caused to resist the centrifugal force from the urging portion 24c. Get away from. At this time, since the force (f2 to F2) against the centrifugal force acts on the roller 25 by the urging portion 24c, the roller 25 rotates together with the outer member 22 in a state of contacting the inner peripheral surface 22a of the outer member 22. This can be suppressed. Further, since the roller 25 is equally urged along the axial direction by the urging portions 24b arranged symmetrically in a state where the influence of the centrifugal force of the roller 25 is suppressed by the urging portion 24c, FIG. It is possible to quickly return to the DP state shown in FIG.

  If the roller 25 is inclined when the roller 25 is engaged between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23, the roller 25 cannot be engaged smoothly, and the one-way clutch 21 is stably engaged. Engagement and disengagement may be hindered. As in the embodiment of the present invention, the roller 25 is uniformly urged along the axial direction by the urging portion 24b while the influence of the centrifugal force of the roller 25 is suppressed by the urging portion 24c. Stable engagement and disengagement are possible by suppressing the skew of 25.

  If the urging portions 24b and 24c of the engagement spring 24 are not divided by the slit 24a, when the engagement spring 24 is inclined, only one end portion of the urging portion of the engagement spring 24 hits the roller 25, and the roller 25 may be inclined. However, according to the present embodiment, the engagement spring 24 is divided into four urging portions 24b and one urging portion 24c by the slit 24a. Can be prevented.

  Further, in the power transmission unit U of the continuously variable transmission T according to the present embodiment, the connecting rod 19 reciprocates at a high speed, so that the one-way clutch 21 is repeatedly engaged and disengaged in a short cycle. It is required to improve responsiveness. In the one-way clutch 21 of the present embodiment, the engagement spring 24 includes one urging portion 24c in the center and two urging portions 24b and 24b at the left and right symmetrical positions, so that the posture of the roller 25 is stabilized. Therefore, the roller 25 can be surely engaged, the engagement response of the one-way clutch 21 is improved, and the power transmission performance of the continuously variable transmission T is enhanced.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the one-way clutch 21 of the present invention can be applied to any use other than the continuously variable transmission T.

  Although the continuously variable transmission T according to the embodiment includes four power transmission units U, the number of power transmission units U is not limited to four. In the embodiment, the inner member 23 of the one-way clutch 21 is configured as a separate member from the output shaft 12, but the inner member 23 may be used as the output shaft 12 as it is.

  In the embodiment, the cage 31 is fixed to the inner member 23, but it may be fixed to the outer member 22. Further, the number of rollers 25 of the one-way clutch 21 and the number of engagement springs 24 are not limited to the embodiment.

  In the embodiment, the engagement spring 24 has a configuration including one urging portion 24c at the center and two urging portions 24b and 24b at the left and right symmetrical positions, but is not limited to this example. What is necessary is just the structure by which the biasing part 24b is arrange | positioned symmetrically with respect to the center biasing part 24c. For example, as a configuration including three urging portions, a configuration including one urging portion 24c at the center and one urging portion 24b at the left and right symmetrical positions may be employed.

  According to the embodiment of the present invention, the centrifugal force is applied to the roller by making the central part of the engagement spring a centrifugal force counter part that opposes the centrifugal force of the roller and the both end parts as pressing parts that apply the pressing force to the roller. The pressing force for returning the roller to the datum point (DP) can be stably applied while the counter force is applied. Thereby, without using an annular ring spring, it is possible to simultaneously improve the damping performance with one spring (engage spring).

  Since the force of the centrifugal force resisting component urged by the conventional annular ring spring is applied by one part of the engagement spring (the urging part 24c), the conventional ring spring can be abolished. The score can be reduced.

  In the DP state of the roller, when the force applied by the urging portion 24c that functions as a centrifugal force counter portion acts in a direction orthogonal to the outer peripheral surface 23a of the inner member 23 (F2 in FIG. 11B), The tangential force component of the inner member 23 is zero. Further, when the force applied by the urging portion 24c acts in a direction inclined with respect to the outer peripheral surface 23a of the inner member 23 (F3 in FIG. 11B), the force acts in the tangential direction of the inner member 23. The component f1 acts together with the pressing force F1 of the urging portion 24b in the direction in which the roller 25 is pressed (the direction in which the roller 25 is engaged). The force component zero to f1 does not impede the force in the direction in which the roller 25 is engaged, and the roller 25 is in contact with the outer peripheral surface 23a of the inner member 23 even when a large centrifugal force is acting on the roller 25. Can be made larger than the surface pressure when the roller 25 contacts the inner peripheral surface 22 a of the outer member 22. Thereby, in the damping state, the roller 25 is prevented from rotating due to contact with the inner peripheral surface 22a of the outer member 22, so that the pressing force of the urging portion 24b can be efficiently transmitted to the roller 25.

Claims (6)

An annular outer member;
An inner member disposed coaxially within the outer member;
A plurality of rollers disposed in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member;
A plurality of elastic members that respectively abut against the plurality of rollers and bias in the circumferential direction of the annular space;
A one-way clutch that transmits a driving force by engaging the roller between the inner peripheral surface and the outer peripheral surface by relative rotation of the outer member and the inner member in a predetermined direction;
The elastic member is
An engagement spring supported by a gauge fixed to the inner member;
The engagement spring includes a plurality of biasing portions juxtaposed in an axial direction intersecting a direction in which the roller moves in the annular space,
The biasing part is
A first biasing portion disposed at the center in the axial direction;
A second biasing portion disposed at a symmetrical position on both sides of the first biasing portion,
Before SL and end of the first biasing part is set longer on the roller side than the end of the second biasing section,
The one- way clutch, wherein a force that opposes the centrifugal force of the roller is applied to the roller by the first urging portion coming into contact with the roller . An annular outer member;
An inner member disposed coaxially within the outer member;
A plurality of rollers disposed in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member;
A plurality of elastic members that respectively abut against the plurality of rollers and bias in the circumferential direction of the annular space;
A one-way clutch that transmits a driving force by engaging the roller between the inner peripheral surface and the outer peripheral surface by relative rotation of the outer member and the inner member in a predetermined direction;
The elastic member is
An engagement spring supported by a gauge fixed to the inner member;
The engagement spring includes a plurality of biasing portions juxtaposed in an axial direction intersecting a direction in which the roller moves in the annular space,
The biasing part is
A first biasing portion disposed at the center in the axial direction;
A second biasing portion disposed at a symmetrical position on both sides of the first biasing portion,
The one-way clutch is
A transmission state in which the roller meshes between the outer member and the inner member and torque transmission is possible;
The non-transmission state in which the engagement of the roller is disengaged between the outer member and the inner member, and torque transmission is impossible.
When the roller passes through a changing point from the transmission state to the non-transmission state, the first urging portion of the plurality of urging portions contacts the roller ,
The one- way clutch, wherein a force that opposes the centrifugal force of the roller is applied to the roller by the first urging portion coming into contact with the roller . Said first biasing portion includes a first surface capable of contact with the rollers, bent to the roller side end portion of the first surface, the position of the inner peripheral surface of the outer member than said first surface The one-way clutch according to claim 2 , further comprising a second surface that can come into contact with the roller.   4. The one-way clutch according to claim 3, wherein when the roller passes through the changing point, the first urging portion contacts the roller on the second surface. 5. The urging portion has a second urging portion having a first surface that can come into contact with the roller,
In the non-transmission state, the second urging portion contacts the roller on the first surface,
The one-way clutch according to claim 3, wherein the first urging portion contacts the roller on the first surface and the second surface. A continuously variable transmission comprising the one-way clutch according to any one of claims 1 to 5, wherein the continuously variable transmission transmits a rotation of an input shaft to an output shaft by changing speed.
An eccentric amount of the input shaft from the axis is variable, and an input side fulcrum that rotates together with the input shaft and an output side fulcrum provided on the outer member of the one-way clutch are connected by a connecting rod, and the one-way clutch A continuously variable transmission in which the inner member is connected to the output shaft.

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