JP6062381B2 - Bearing and continuously variable transmission equipped with bearing - Google Patents

Description

  The present invention relates to a bearing used for a rotating body that rotates in an eccentric state and a continuously variable transmission including such a bearing.

  The present applicant has already proposed a continuously variable transmission provided with this type of bearing in, for example, Patent Document 1. This continuously variable transmission is mounted on a vehicle having an internal combustion engine and is of a type that uses the principle of a four-bar link. An input shaft directly connected to the internal combustion engine, an output shaft parallel to the input shaft, and an input An eccentric disk provided on the shaft side, a one-way clutch provided on the output shaft side, and a connecting rod for interconnecting the eccentric disk and the one-way clutch are provided.

  The eccentric disk is eccentric with respect to the axis of the input shaft, and the amount of eccentricity can be changed. Further, an annular portion formed at one end portion of the connecting rod is rotatably fitted to the eccentric disk via a roller bearing. The roller bearing includes an outer ring and an inner ring provided on the annular portion and the eccentric disk, respectively, and a plurality of rollers disposed between the outer ring and the inner ring.

  On the other hand, the one-way clutch has an inner shaft that rotates integrally with the output shaft, an outer ring that is rotatable relative to the inner shaft, and a clutch roller and a spring that are disposed between the inner shaft and the outer ring. The other end of the connecting rod is rotatably connected to the outer ring.

  In the above configuration, when the input shaft is driven by the rotation of the internal combustion engine, the eccentric disk rotates while being eccentric about the axis of the input shaft, and the connecting rod reciprocates accordingly. In this reciprocating motion, when the connecting rod moves to the one-way clutch side, the outer ring rotates in a predetermined direction with respect to the inner shaft, and the clutch roller engages with both of them so that the one-way clutch is engaged. . In this engaged state, the power of the input shaft is transmitted to the output shaft via the one-way clutch. Further, the speed ratio of the continuously variable transmission is controlled steplessly by changing the amount of eccentricity of the eccentric disk with respect to the input shaft.

  Thereafter, when the connecting rod moves to the opposite side of the one-way clutch, the outer ring rotates in the opposite direction to the inner shaft, thereby disengaging the clutch roller. In this disengaged state, the transmission of power from the input shaft to the output shaft is interrupted by blocking between the outer ring and the inner shaft.

JP 2013-19429

  In the conventional continuously variable transmission described above, when the one-way clutch is engaged, the reaction force from the outer ring of the one-way clutch acts on the roller bearing via the connecting rod. As a result, the distance between the outer ring and the inner ring of the roller bearing becomes narrow at the one-way clutch side portion, but increases at the opposite side portion, so that a clearance (play) occurs between the inner ring and the roller. When the one-way clutch is switched from this state to the non-engaged state, the reaction force from the outer ring suddenly disappears, so that the distance between the expanded outer ring and inner ring returns to the original interval, and the above If the clearance is clogged abruptly, a collision between the roller and the inner ring occurs, which may cause noise and vibration deterioration.

  The present invention has been made in order to solve the above-described problems. With a simple configuration, the impact of the rolling element when it collides with the inner ring can be reduced, and noise and vibration due to the collision can be suppressed. It aims at providing a continuously variable transmission which can acquire the same effect by providing a bearing and such a bearing.

  In order to achieve the above object, a bearing according to claim 1 of the present invention (a ball bearing 40 in the embodiment (hereinafter the same in this section)) includes an outer ring 41 having an inner peripheral surface 41a, an inner ring of the outer ring 41, The peripheral surface 41a has an outer peripheral surface 42a facing from the inside, is provided concentrically and rotatably with respect to the outer ring 41, and is parallel to the axis of the outer ring 41 (center OD of the eccentric disk) (input shaft) Is disposed in an annular space 45 between the inner ring 42 rotating eccentrically around the axis L1) and the inner peripheral surface 41a of the outer ring 41 and the outer peripheral surface 42a of the inner ring 42, and the inner peripheral surface 41a and the outer peripheral surface 42a. A plurality of rolling elements (balls 43) that roll in contact with each other, and a holder 44 that is disposed in the annular space 45 and holds the plurality of rolling elements. The holder 44 includes a plurality of rolling elements. Accommodates and holds each moving object The connecting portion 47 includes a plurality of pocket portions 46 and a connecting portion 47 that connects the plurality of pocket portions 46 to each other. The connecting portion 47 is made of an elastic material that can be expanded and contracted by the inertial force of the rolling elements. And a contact portion (protrusion 47a) that contacts the outer peripheral surface 42a of the inner ring 42 when the connecting portion 47 is extended by the inertial force of the rolling element.

  In this bearing, the inner ring rotates in an eccentric state around another axis parallel to the axis of the bearing. The plurality of rolling elements arranged in the annular space between the outer ring and the inner ring are accommodated and held in the plurality of pocket portions of the cage, and the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring are accompanied by the rotation of the inner ring. Roll while in contact with The plurality of pocket portions are connected to each other by a connecting portion, and the connecting portion is made of an elastic material that can be expanded and contracted by the inertial force of the rolling elements.

  As the inner ring rotates in an eccentric state, the clearance between the inner ring and the rolling element is increased due to the increase in the distance between the outer ring and the inner ring. At the same time, the connecting portion extends due to the inertial force of the rolling elements. Along with the extension of the connecting part, the contact part provided on the radially inner side of the connecting part comes into contact with the outer peripheral surface of the inner ring. After that, when the collision between the rolling element and the inner ring occurs by returning the interval between the outer ring and the inner ring to the original interval, the contact portion of the connecting portion is pressed against the inner ring and is in a stretched state. Therefore, the rolling element is supported by the connecting portion and decelerated before the collision. Thereby, the noise and vibration due to the collision can be suppressed by absorbing the collision energy.

  According to a second aspect of the present invention, in the bearing according to the first aspect, the connecting portion 47 is on the outer peripheral side with respect to a line connecting the centers of the plurality of rolling elements in the circumferential direction when the connecting portion 47 is not extended. The contact portion is formed by a protrusion 47a protruding inward in the radial direction.

  According to this configuration, since the connecting portion is formed to be convex on the outer peripheral side, the protrusion provided on the radially inner side is pushed out to the inner ring side as the connecting portion expands, so that the protrusion is formed on the inner ring. It is possible to securely contact the outer peripheral surface. Thereby, collision energy can be absorbed more reliably and satisfactorily, and noise and vibration can be further suppressed.

  According to a third aspect of the present invention, in the bearing according to the first or second aspect, each of the plurality of pocket portions 46 is opposed to each other in the circumferential direction, and a pair of holding surfaces 46b that hold the rolling elements in sliding contact with each other. 46b, and the pair of holding surfaces 46b, 46b are formed in a tapered shape in which the distance between the holding surfaces 46b, 46b gradually narrows toward the inside in the radial direction in order to restrict the movement of the rolling elements toward the inner ring 42 side. It is characterized by being.

  According to this configuration, the movement of the rolling element toward the inner ring side is restricted by the pair of tapered holding surfaces formed in the pocket portion of the cage, so that the collision between the rolling element and the inner ring is reduced or alleviated. Therefore, noise and vibration can be further suppressed.

  A fourth aspect of the invention is a continuously variable transmission T that includes the bearing according to any one of the first to third aspects, and that continuously shifts and outputs an input driving force, and the driving force is input. Input shaft 11, an output shaft 12 that is arranged in parallel with the input shaft 11 and outputs a shifted driving force, and a swing link (outer ring 22) that is swingably attached to the output shaft 12. A lever crank mechanism that converts the rotational motion of the input shaft 11 into the swing motion of the swing link, and the swing link and the output shaft 12, and the swing link rotates in one predetermined direction. When moving, the swing link is connected to the output shaft 12 by being engaged, and when the swing link is rotated in the other direction, the swing link is disconnected. A one-way clutch 21 that shuts off the output shaft 12; The lever crank mechanism includes a rotating body (carrier 16) that rotates integrally with the input shaft 11 while being eccentric with respect to the input shaft 11, and an eccentric disk 18 that is rotatable with respect to the rotating body. An adjusting mechanism (transmission actuator 14) for adjusting the eccentric amount R1 of the eccentric disk 18 with respect to the input shaft 11 by changing the relative angle of the rotating body with respect to the input shaft 11, and one end portion of which can freely rotate to the eccentric disk 18. And a connecting rod 19 whose other end is rotatably connected to a swing link. The connecting rod 19 has an annular portion 19b fitted to the outside of the eccentric disk 18 via a bearing. The bearing outer ring 41 is provided on the annular portion 19 b of the connecting rod 19, and the bearing inner ring 42 is provided on the outer peripheral portion of the eccentric disk 18. It is characterized in.

  This continuously variable transmission shifts and outputs the input driving force in a stepless manner, and includes the above-described bearing. In this continuously variable transmission, when the input shaft rotates, the eccentric disk rotates in an eccentric state with respect to the input shaft, and accordingly, the connecting rod reciprocates to swing the swing link. The bearing is disposed between the eccentric disk and the annular part of the connecting rod fitted thereto, and the outer ring is provided on the annular part and the inner ring is provided on the outer peripheral part of the eccentric disk.

  When the swing link rotates in one predetermined direction, the one-way clutch is engaged, whereby the swing link is connected to the output shaft, and the driving force is transmitted while being shifted to the output shaft. . On the other hand, when the swing link rotates in the other direction, the one-way clutch is disengaged, whereby the swing link is disconnected from the output shaft, and transmission of the driving force to the output shaft is interrupted. The The speed ratio of the continuously variable transmission is performed by adjusting the amount of eccentricity of the eccentric disk with respect to the input shaft by changing the relative angle of the rotating body with respect to the input shaft.

  In the continuously variable transmission configured as described above, when the one-way clutch is in the engaged state, the reaction force from the one-way clutch acts on the bearing, so that in the region of the bearing opposite to the one-way clutch, the inner ring When the clearance with the rolling element is generated, and then the one-way clutch is switched from the engaged state to the non-engaged state, the reaction force from the one-way clutch is abruptly eliminated, thereby causing a collision between the rolling element and the inner ring.

  Therefore, by providing the bearing according to claims 1 to 3 as a bearing of this continuously variable transmission, it is possible to suppress the above-described effects of this bearing, that is, noise and vibration due to a collision between the rolling element of the bearing and the inner ring. The effect can be obtained effectively.

1 is a diagram schematically showing a continuously variable transmission including a ball bearing according to an embodiment of the present invention together with a vehicle on which the continuously variable transmission is mounted. FIG. It is a skeleton figure which shows the structure of a continuously variable transmission. FIG. 3 is a sectional view taken along line III-III in FIG. 2 when the continuously variable transmission is in a top state. FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2 when the continuously variable transmission is in a neutral state. It is a figure for demonstrating operation | movement when a continuously variable transmission exists in the top state of FIG. FIG. 5 is a diagram for explaining an operation when the continuously variable transmission is in the neutral state of FIG. 4. It is a figure which shows a ball bearing typically. It is the elements on larger scale of FIG. It is a fragmentary perspective view which shows the ball | bowl of a ball bearing and a holder | retainer. When a one-way clutch is a non-engagement state, it is (a) a figure showing typically a continuously variable transmission, and (b) a partial enlarged view showing an operation state of a bearing. FIG. 11 is a view similar to FIG. 10 just before the end of the engaged state of the one-way clutch. FIG. 11 is a view similar to FIG. 10 immediately after the one-way clutch is switched from the engaged state to the non-engaged state. It is a figure for demonstrating the inertial force which acts on the ball | bowl of a ball bearing.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. As shown in FIG. 1, a vehicle V is, for example, an FF type four-wheel vehicle, and is disposed between an internal combustion engine (hereinafter referred to as “engine”) 3 and left and right drive wheels (front wheels) DW and DW. The continuously variable transmission T is provided.

  The power of the engine 3 is input to the continuously variable transmission T via the input shaft 11, and is continuously shifted by the continuously variable transmission T and then output from the output shaft 12. This power is further transmitted to the drive wheels DW and DW via the differential device DF and the left and right drive shafts DS and DS, thereby driving the vehicle V.

  The continuously variable transmission T applies the principle of the four-bar link and uses the one-way clutch 21 according to the present invention. As shown in FIGS. 2 to 4, the input shaft 11 and the output shaft are parallel to each other. 12 and a plurality (four in this example) of power transmission units U provided between the input shaft 11 and the output shaft 12. The output shaft 12 has a hollow shape, and a drive shaft DS is coaxially passed through the output shaft 12.

  The input shaft 11 is directly connected to a crankshaft (not shown) of the engine 3 and extends coaxially. A hollow rotary shaft 13 is rotatably fitted to the input shaft 11, and a speed change actuator 14 is provided between the input shaft 11 and the rotary shaft 13. The speed change actuator 14 is a combination of a motor and a planetary gear mechanism (both not shown). When the motor is rotated, the relative angle (phase) of the rotary shaft 13 to the input shaft 11 according to the rotation angle. ) Is configured to change. When power is transmitted to the input shaft 11, the rotary shaft 13 rotates integrally with the input shaft 11 while maintaining a relative angle with respect to the input shaft 11.

  The four power transmission units U are arranged along the input shaft 11 and have the same configuration. Each power transmission unit U includes a first pinion 15 provided integrally with the input shaft 11, a carrier 16 provided integrally with the rotary shaft 13, and two second pinions 17, 17 supported by the carrier 16. An eccentric disc 18 and a connecting rod 19 are provided.

  The carrier 16 has a crank shape that surrounds the first pinion 15 and extends from the rotary shaft 13 toward one side in the radial direction. As shown in FIG. 2, the extending direction of the carrier 16 from the rotation shaft 13 is shifted by 90 ° between the four power transmission units U. For example, in FIG. 2, the leftmost carrier 16 extends upward, the second carrier 16 from the left extends to the back of the drawing, the third carrier 16 from the left extends downward, and the rightmost carrier 16. Extends to the front side of the drawing.

  The second pinions 17 and 17 have the same diameter and the same number of teeth as the first pinion 15, and are rotatably supported by pinion pins 16 a and 16 a provided integrally with the carrier 16. The first pinion 15 and the second pinions 17 and 17 are arranged in a plane perpendicular to the input shaft 11 so that their three centers form an equilateral triangle.

  The eccentric disk 18 has a circular eccentric hole 18a, and a ring gear 18b is formed on the peripheral surface thereof. The first pinion 15 and the second pinions 17 and 17 are accommodated in the eccentric hole 18a and meshed with the ring gear 18b.

  The connecting rod 19 includes a triangular rod portion 19a and an annular portion 19b provided on one end side of the rod portion 19a. The annular portion 19b is connected to the outer peripheral portion of the eccentric disk 18 via a ball bearing 40. And is mounted rotatably. Details of the configuration of the ball bearing 40 will be described later.

  The power transmission unit U further includes a one-way clutch 21 on the output shaft 12 side. The one-way clutch 21 includes an outer ring 22, an inner shaft 23, and a plurality of leaf springs 24 and rollers 25 disposed between the two rings 22 and 23. The outer ring 22 has a circular inner peripheral surface, and is rotatably provided on the outer side of the output shaft 12. The outer ring 22 is rotatable on the other end of the rod portion 19a of the connecting rod 19 via a pin 19c. It is connected to.

  The inner shaft 23 has a predetermined uneven outer peripheral surface, is provided integrally with the output shaft 12, and is disposed inside the outer ring 22. The plurality of rollers 25 are arranged between the outer ring 22 and the inner shaft 23 so as to be aligned in the circumferential direction, and are urged in a predetermined direction by a leaf spring 24.

  Next, the operation of the continuously variable transmission T configured as described above will be described. First, the operation of one power transmission unit U will be described. When the motor of the speed change actuator 14 is rotated in a state where the input shaft 11 is not rotating, the rotation shaft 13 is rotated relative to the input shaft 11 according to the rotation angle. The integrated carrier 16 and the second pinions 17 and 17 supported by the carrier 16 rotate around the axis line L1 of the input shaft 11 (hereinafter referred to as “input axis line”). Accordingly, the center (hereinafter referred to as “carrier center”) OC of the equilateral triangle formed by the first pinion 15 and the second pinions 17 and 17 rotates around the input axis L1 by the same angle as the rotation shaft 13.

  As a result, the center of the eccentric hole 18a of the eccentric disk 18 engaged with the first pinion 15 and the second pinion 17 and 17 via the ring gear 18b also rotates at the same angle as the rotary shaft 13, and accordingly the eccentric disk 18 The distance between the center 18 (hereinafter referred to as “disk center”) OD and the input axis L1, that is, the eccentric amount R1 of the eccentric disk 18 with respect to the input shaft 11 is changed.

  For example, FIGS. 3 and 5 show a state where the disc center OD is on the opposite side of the input axis L1 with respect to the carrier center OC. In this state, the eccentric amount R1 of the eccentric disk 18 with respect to the input shaft 11 is maximized, and the continuously variable transmission T is in a top state where the rotational speed of the output shaft 12 is maximum and the speed ratio is minimum. On the other hand, FIGS. 4 and 6 show a state where the disk center OD coincides with the input axis L1. In this state, the eccentric amount R1 of the eccentric disk 18 with respect to the input shaft 11 becomes 0, and the continuously variable transmission T enters a neutral state in which the rotational speed of the output shaft 12 is 0 and the speed ratio is infinite.

  Next, the operation when the continuously variable transmission T is set to the top state of FIG. 3 will be described with reference to FIG. In this top state, when the power of the engine 3 is transmitted, when the input shaft 11 rotates counterclockwise in the figure, the first pinion 15 rotates (rotates) integrally with the input shaft 11. Further, the rotary shaft 13 rotates integrally with the input shaft 11, and accordingly, the second pinions 17 and 17 supported by the carrier 16 rotate around the input axis L1 in the same direction as the input shaft 11 at the same speed ( Revolve). As a result, the eccentric disk 18 rotates once counterclockwise (arrow X direction) while being eccentric about the input axis L1 every time the input shaft 11 rotates once.

  FIGS. 5A and 5C show states where the disc center OD is at the farthest position and the nearest position from the outer ring 22 of the one-way clutch 21, respectively. When the eccentric disk 18 rotates from the position (a) to the position (c) through the intermediate position (b) as the input shaft 11 rotates, the connecting rod is rotatably fitted to the eccentric disk 18 during the rotation. 19 moves to the outer ring 22 side, presses the outer ring 22 via the pin 19c at the tip, and rotates it counterclockwise (arrow Y direction).

  Thus, when the outer ring 22 rotates in the arrow Y direction, each roller 25 of the one-way clutch 21 is engaged (engaged) with the inner peripheral surface of the outer ring 22 and the outer peripheral surface of the inner shaft 23. Thereby, the rotation of the outer ring 22 is transmitted to the output shaft 12 via the inner shaft 23, whereby the output shaft 12 rotates in the same counterclockwise direction as the outer ring 22.

  Thereafter, as the input shaft 11 further rotates, when the eccentric disk 18 rotates from the position (c) to the position (a) through the intermediate position (d), the connecting rod 19 and the outer ring 22 It moves to the opposite side, pulls the outer ring 22 via the pin 19c, and rotates it clockwise (arrow Y ′ direction).

  Thus, when the outer ring 22 rotates in the direction of the arrow Y ′, each roller 25 of the one-way clutch 21 is disengaged from the inner peripheral surface of the outer ring 22 and the outer peripheral surface of the inner shaft 23 while compressing the leaf spring 24. As a result, the outer ring 22 and the inner shaft 23 are blocked from each other, so that the rotation of the outer ring 22 is not transmitted to the output shaft 12.

  As described above, as the input shaft 11 rotates, the eccentric disk 18 rotates while being eccentric about the input axis L1, so that the connecting rod 19 reciprocates, and the outer ring 22 of the one-way clutch 21 is moved as shown in FIG. Oscillate between position (a) and position (c). Only when the outer ring 22 rotates counterclockwise from the position (a) to the position (c) due to the engagement / disengagement of the roller 25 accompanying the swing of the outer ring 22, the input shaft 11 is intermittently transmitted to the output shaft 12.

  On the other hand, when the continuously variable transmission T is set to the neutral state of FIG. 4, the disc center OD coincides with the input axis L1, and the eccentric amount R1 of the eccentric disc 18 with respect to the input shaft 11 is zero. . Therefore, as shown in FIG. 6, as the input shaft 11 rotates, the eccentric disk 18 rotates eccentrically around the input axis L1 as the carrier 16 and the second pinions 17 and 17 rotate. However, the position of the disk center OD is not changed at all. As a result, since the reciprocating motion of the connecting rod 19 and the swinging of the outer ring 22 do not occur, the rotation of the input shaft 11 is not transmitted to the output shaft 12 and the rotation speed of the output shaft 12 becomes zero.

  As is clear from the above operation, the eccentric amount R1 of the eccentric disk 18 corresponds to the length of the input link of the four-bar linkage mechanism, and the swing angle of the outer ring 22 is determined according to the eccentric amount R1. Further, the rotational speed of the output shaft 12, that is, the gear ratio of the continuously variable transmission T is determined. Therefore, the gear ratio of the continuously variable transmission T is shown in FIG. 3 by changing the relative angle of the rotating shaft 13 with respect to the input shaft 11 and changing the eccentric amount R1 of the eccentric disk 18 by the motor of the transmission actuator 14. It is set steplessly between the top state (minimum transmission ratio) and the neutral state (infinite transmission ratio) shown in FIG.

  Further, as described above, between the four power transmission units U, the extending direction of the carrier 16 from the rotating shaft 13, that is, the phase of the eccentric disk 18 with respect to the input shaft 11 is shifted by 90 ° from each other. For this reason, transmission of power from the input shaft 11 to the output shaft 12 is intermittently performed by the one-way clutch 21 in each power transmission unit U, but is alternately performed between the four power transmission units U. As a whole of the step transmission T, transmission of power from the input shaft 11 to the output shaft 12 is continuously performed without interruption.

  Next, the configuration of the ball bearing 40 provided between the eccentric disk 18 and the connecting rod 19 will be described in detail with reference to FIGS. As shown in these drawings, the ball bearing 40 includes an outer ring 41 and an inner ring 42 that are opposed to each other in the radial direction, a plurality of balls 43 that are provided between the outer ring 41 and the inner ring 42, and a plurality of balls. A holder 44 for holding 43 is provided.

  The outer ring 41 is provided on the annular portion 19b of the connecting rod 19, and the inner ring 42 is provided on the outer peripheral portion of the eccentric disk 18 (see FIGS. 3 and 4). The plurality of balls 43 and the cage 44 are arranged in an annular space 45 formed between the inner peripheral surface 41 a of the outer ring 41 and the outer peripheral surface 42 a of the inner ring 42.

  As shown in FIG. 7, the retainer 44 is an annular one provided in the entire annular space 45, and is integrally formed from a stretchable elastic material, for example, a relatively hard synthetic resin having elasticity. ing. Further, as shown in FIG. 8, the retainer 44 has a plurality of pocket portions 46 arranged at equal intervals in the circumferential direction, and a connecting portion 47 that connects these pocket portions 46 to each other.

  Each pocket portion 46 includes a receiving hole 46a that penetrates in the radial direction, and a pair of holding surfaces 46b and 46b that face each other on both sides in the circumferential direction of the receiving hole 46a. These holding surfaces 46b and 46b are formed in a taper shape in which the distance between the holding surfaces 46b and 46b gradually becomes narrower inward in the radial direction.

  The ball 43 is accommodated and held in the accommodation hole 46a of each pocket portion 46, and in this state, the ball 43 partially protrudes outward and inward in the radial direction from the pocket portion 46, and the inner peripheral surface 41a of the outer ring 41. And an outer peripheral surface 42 a of the inner ring 42. Further, since the pair of holding surfaces 46b and 46b have the taper as described above, the movement of the ball 43 inward in the radial direction is restricted.

  In addition, the connecting portion 47 has a central portion in the circumferential direction between each of the two pocket portions 46, 46 on the outer peripheral side with respect to a line (a chain line in FIG. 8) connecting the centers of the plurality of balls 43 in the circumferential direction. It is convexly curved. On the radially inner surface of the curved portion, a protrusion 47a protruding inward in the radial direction is integrally provided over the entire width direction (the circumferential direction and the direction orthogonal to the radial direction).

  Next, the operation of the ball bearing 40 having the above-described configuration will be described with reference to FIGS. First, the inertial force acting on the ball 43 will be described. 10-12, the arrow attached | subjected to the one part ball | bowl 43 shows the inertial force F which acts on each ball | bowl 43 typically. As shown in FIG. 13, this inertial force F is represented by the resultant force of the first inertial force F1 and the second inertial force F2.

  The first inertia force F <b> 1 is a centrifugal force that acts when the ball 43 rotates along the annular space 45 as the ball bearing 40 rotates. For this reason, the first inertial force F1 acts in a direction from the disc center OD (= center of the ball bearing 40) toward the center of each ball 43, the magnitude thereof is the same, and the circumferential component is zero. .

  On the other hand, the second inertia force F2 is a centrifugal force acting on the ball 43 as a result of the ball bearing 40 rotating eccentrically with respect to the input axis L1 as a whole. For this reason, the second inertial force F2 acts in any ball 43 in the same direction as the direction LD from the input axis L1 toward the disk OD, and the magnitude thereof is the same.

  Further, the circumferential component of the second inertial force F2 varies depending on the position of the ball 43 as follows. Here, as shown in FIG. 10 and the like, the position on the input axis L1 side of the ball bearing 40 where the straight line connecting the input axis L1 and the disk center OD intersect and the position on the opposite side thereof are denoted as A and C, respectively. A position 90 degrees from position A in the clockwise direction is B, and a position 90 degrees from position C is D.

  With respect to these positions, the circumferential component of the second inertial force F2 is 0 at the position A, increases from the position A toward the position B, and becomes the maximum at the position B when the rotational direction of the eccentric disk 18 is positive. , Decreases from position B toward position C, and becomes zero at position C. Further, it further decreases as it goes from position C to position D, becomes minimum at position D, increases as it goes from position D to position A, and becomes 0 at position A.

  As described above, since the circumferential component of the first inertial force F1 is 0, the circumferential component of the inertial force F of the ball 43 is equal to that of the above-described second inertial force F2. For this reason, as indicated by an arrow in FIG. 10A and the like, in the first region on the input axis L1 side from the position D to the position B, the circumferential component of the inertial force F increases toward the position B. The inertial force F acts to keep the balls 43 away from each other. Conversely, in the second region on the opposite side of the input axis L1 from the position B to the position D, the circumferential component of the inertial force F of the ball 43 decreases toward the position D. Acts to bring the balls 43 closer to each other.

  Next, the operation of the ball bearing 40 will be described. FIG. 10 shows the state of the continuously variable transmission T and the ball bearing 40 when the one-way clutch 21 is in the disengaged state (corresponding to the state of FIG. 5D). In this state, the reaction force from the one-way clutch 21 side is almost zero, and only the reaction force from the connecting rod 19 acts on the ball bearing 40. For this reason, as shown in FIG.10 (b), each ball | bowl 43 contacts the outer ring | wheel 41 and the inner ring | wheel 42, and is restrained by these. Further, the outer peripheral portion of the connecting portion 47 and the protrusion 47 a of the retainer 44 are separated from the inner peripheral surface 41 a of the outer ring 41 and the outer peripheral surface 42 a of the inner ring 42.

  FIG. 11 shows a state of the continuously variable transmission T and the ball bearing 40 when the one-way clutch 21 is in an engaged state, particularly a state immediately before the end (corresponding to the state of FIG. 5C). In this engaged state, a large reaction force Fw from the one-way clutch 21 side acts on the ball bearing 40 via the connecting rod 19 as shown in FIG. Further, in the state immediately before the end of the engagement, the disc center OD is positioned closest to the one-way clutch 21, so that the distance between the outer ring 41 and the inner ring 42 of the ball bearing 40 is the second one on the one-way clutch 21 side. It becomes narrow in the area, and expands in the first area on the opposite side.

  As a result, as shown in FIG. 11B, in the first region, a clearance C is generated between the inner ring 42 and the ball 43, and the restriction of the ball 43 is released. Further, in this first region, since the inertial force F described above acts on the ball 43, the ball 43 moves away from each other. As a result, the connecting portion 47 of the retainer 44 is extended by being pulled by the ball 43, and accordingly, the protrusion 47a of the connecting portion 47 is pushed radially inward and abuts on the outer peripheral surface 42a of the inner ring 42, Pressed.

  Thereafter, when the one-way clutch 21 is switched from the engaged state to the non-engaged state, the reaction force from the one-way clutch 21 side suddenly disappears. Therefore, as shown in FIG. The distance between the balls 42 returns to the original distance, and a collision between the ball 43 and the inner ring 42 occurs. However, at this time, since the protrusion 47a of the connecting portion 47 is pressed against the inner ring 42 and is stretched, the ball 43 is supported by the connecting portion 47 and decelerated before the collision. Thereby, collision energy is absorbed and noise and vibration due to collision are suppressed.

  As described above, according to the present embodiment, when the one-way clutch 21 of the continuously variable transmission T is switched from the engaged state to the non-engaged state, if a clearance is generated between the inner ring 42 and the ball 43, the ball 43 As the connecting portion 47 of the cage 44 extends due to the inertial force, the protrusion 47 a comes into contact with the outer peripheral surface 42 a of the inner ring 42. For this reason, even when the ball 43 and the inner ring 42 collide when the one-way clutch 21 is switched from the engaged state to the non-engaged state, the ball 43 is supported by the connecting portion 47 and decelerated before the collision. Therefore, it is possible to absorb collision energy and suppress noise and vibration due to the collision.

  Further, since the connecting portion 47 is formed on the outer peripheral side so that the protrusion 47a provided on the radially inner side is pushed out toward the inner ring 42 as the connecting portion 47 extends, the protrusion 47 is connected to the inner ring 42. It is possible to securely contact the outer peripheral surface 42a. Thereby, collision energy can be absorbed more reliably and well, and noise and vibration can be further suppressed.

  Further, the pair of holding surfaces 46b and 46b of the pocket portion 46 of the cage 44 that accommodates the ball 43 are formed in a tapered shape that becomes narrower inward in the radial direction, so that the ball 43 toward the inner ring 42 side is formed. Therefore, the collision between the ball 43 and the inner ring 42 is reduced or alleviated, and noise and vibration can be further suppressed.

  In addition, this invention can be implemented in various aspects, without being limited to the described embodiment. For example, in the embodiment, the bearing is a ball bearing in which the rolling element is a ball, but is not limited thereto, and may be a roller bearing in which the rolling element is a roller.

  In the embodiment, the protrusion 47a of the cage 44 is integrally formed of the same material as that of the connecting portion 47, but may be formed of a material different from that of the connecting portion 47 or may be formed separately. Furthermore, in the embodiment, the bearing is used for the continuously variable transmission, but it is needless to say that the bearing may be used for other devices as long as it is used for a rotating body that rotates eccentrically. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

11 Input shaft 12 Output shaft 14 Variable speed actuator (adjustment mechanism)
16 Carrier (Rotating body)
18 Eccentric disc 19 Connecting rod 19b Annular part 21 One-way clutch 22 Outer ring (swinging link)
40 Ball bearing
41 Outer ring 41a Inner peripheral surface of outer ring 42 Inner ring 42a Outer peripheral surface of inner ring 43 Ball (rolling element)
44 cage 45 annular space 46 pocket portion 46b holding surface 47 connecting portion 47a protrusion T continuously variable transmission L1 axis of the input shaft (other axis)
OD Center of eccentric disk (axis of outer ring)
R1 Eccentricity of eccentric disc

Claims (4)

An outer ring having an inner peripheral surface;
In the state which has the outer peripheral surface which faces the inner peripheral surface of the outer ring from the inside, is provided concentrically and rotatably with respect to the outer ring, and is eccentric around another axis parallel to the axis of the outer ring A rotating inner ring,
A plurality of rolling elements arranged in an annular space between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, and rolling in a state in contact with the inner peripheral surface and the outer peripheral surface;
A cage that is disposed in the annular space and holds the plurality of rolling elements,
The retainer accommodates and holds the plurality of rolling elements, respectively, and a plurality of pocket portions,
A connecting portion for connecting the plurality of pocket portions to each other,
The connecting part is made of an elastic material that can be expanded and contracted by the inertial force of the rolling element, and is provided on the radially inner side of the connecting part, and when the connecting part is extended by the inertial force of the rolling element, A bearing having a contact portion that contacts the outer peripheral surface of the inner ring. The connecting portion is formed in a convex shape on the outer peripheral side with respect to a line connecting the centers of the plurality of rolling elements in the circumferential direction in a state where the connecting portion is not extended,
The bearing according to claim 1, wherein the contact portion is configured by a protrusion protruding inward in the radial direction. Each of the plurality of pocket portions has a pair of holding surfaces that are opposed to each other in the circumferential direction and hold the rolling elements in a sliding contact state,
The pair of holding surfaces are formed in a tapered shape in which the distance between each pair gradually decreases toward the inner side in the radial direction in order to restrict the movement of the rolling elements toward the inner ring side. The bearing according to claim 1 or 2. A continuously variable transmission comprising the bearing according to any one of claims 1 to 3, wherein the input driving force is continuously shifted and output.
An input shaft to which the driving force is input;
An output shaft that is arranged in parallel with the input shaft and outputs a shifted driving force;
A lever crank mechanism swingably attached to the output shaft, and a lever crank mechanism for converting the rotational motion of the input shaft into the swing motion of the swing link;
Provided between the swing link and the output shaft, the swing link is connected to the output shaft by being engaged when the swing link rotates in one predetermined direction. A one-way clutch that disconnects the swing link from the output shaft by being disengaged when the swing link rotates in the other direction;
The lever crank mechanism is eccentric with respect to the input shaft and is rotated integrally with the input shaft, an eccentric disk that is rotatable with respect to the rotary member, and the input shaft. An adjustment mechanism for adjusting the amount of eccentricity of the eccentric disk with respect to the input shaft by changing the relative angle of the rotating body, one end of which is rotatably connected to the eccentric disk, and the other end is A connecting rod rotatably connected to the moving link;
The connecting rod has an annular portion that fits outside the eccentric disk via the bearing,
The outer ring of the bearing is provided in the annular portion of the connecting rod;
The continuously variable transmission according to claim 1, wherein the inner ring of the bearing is provided on an outer peripheral portion of the eccentric disk.

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