JP6151223B2 - Bearing and rotating device or continuously variable transmission using the bearing - Google Patents

Description

  The present invention relates to a bearing including an inner ring, an outer ring, a rolling element, and a cage, and a rotating device or continuously variable transmission using the bearing.

  Conventionally, a cam portion coupling body as an input portion that rotates by transmitting a driving force from a driving source such as an engine provided in a vehicle, and an output shaft that is arranged in parallel with the rotation center axis of the cam portion coupling body, A plurality of turning radius adjusting mechanisms provided on the cam portion coupling body, a plurality of turning portions pivotally supported by the output shaft, and a rotation radius adjusting mechanism that is rotatably fitted at one end. There is known a four-bar linkage type continuously variable transmission having an input-side annular portion and a connecting rod connected to the swinging end of the swinging portion at the other end (for example, a patent Reference 1).

  In Patent Document 1, each turning radius adjusting mechanism includes a disc-shaped cam portion provided eccentrically with respect to the rotation center axis of the input shaft, and a rotating portion provided eccentrically on the cam portion and rotatably provided. And a pinion shaft provided integrally with a plurality of pinions in the axial direction. In addition, a one-way rotation prevention mechanism constituted by a one-way clutch is provided between the swinging portion and the output shaft. The one-way rotation prevention mechanism fixes the swinging portion to the output shaft when the swinging portion attempts to rotate relative to the output shaft, and causes the output shaft to rotate relative to the other side. Oscillates the rocking part.

  The cam part connection body is hollow by connecting through holes of the cam parts, and a pinion shaft is inserted into the inside. The inserted pinion shaft is exposed from the notch portion of each cam portion. The rotating part is provided with a receiving hole for receiving the cam part connecting body. Internal teeth are formed on the inner peripheral surface of the rotating part that forms the receiving hole.

  The internal teeth mesh with the pinion exposed from the notch portion of the cam portion coupling body. When the cam unit coupling body and the pinion are rotated at the same speed, the rotation radius of the rotating unit is maintained. If the rotational speeds of the cam unit coupling body and the pinion are made different, the rotation radius of the rotating unit is changed, and the gear ratio is changed.

  When the connecting part of the cam part is rotated and the rotating part is rotated, the input side annular part of the connecting rod rotates and the swinging end part of the swinging part connected to the other end of the connecting rod swings. Move. That is, a lever crank mechanism (motion conversion mechanism) is configured by the turning radius adjusting mechanism (cam portion, rotating portion, pinion), connecting rod, and swinging portion. Since the oscillating portion is provided on the output shaft via the one-way rotation prevention mechanism, the oscillating portion transmits the rotational driving force (torque) to the output shaft only when rotating to one side.

  The eccentric direction of the cam part of each turning radius adjusting mechanism is set so as to make a round around the rotation center axis of the cam part connecting body with different phases. Accordingly, the connecting rods externally fitted to the rotating parts cause the swinging parts to sequentially transmit torque to the output shaft via the one-way rotation preventing mechanism, so that the output shaft can be smoothly rotated.

  A connecting rod bearing is provided between the rotating portion and the input-side annular portion of the connecting rod.

JP 2013-19429 A

A bearing such as a connecting rod bearing may generate noise or vibration when the rolling element collides with the inner ring or the outer ring.
An object of this invention is to provide the bearing which can suppress generation | occurrence | production of a noise and a vibration in view of the above point.

[1] In order to achieve the above object, the present invention provides:
A bearing comprising an inner ring, an outer ring, a rolling element, and a cage that holds the rolling element,
The retainer is provided with a housing portion that houses the rolling elements, a piston chamber, and a communication passage that communicates the housing portion and the piston chamber.
The piston chamber is inserted so that the piston can come into contact with one of the inner ring and the outer ring , and is filled with fluid,
When the piston abuts against the one of the inner ring or the outer ring and is pushed into the piston chamber, the fluid flows into the accommodating portion through the communication path, and the rolling element is connected to the inner ring or the outer ring . It is pressed against the one side.

  According to the bearing of the present invention, when the piston contacts the inner ring or the outer ring and is pushed into the piston chamber, the fluid flows into the accommodating portion via the communication path, and the rolling element is pressed against the inner ring or the outer ring. As a result, when the rolling element comes into contact with the outer ring or the inner ring, the rolling element comes in contact with the fluid, and the fluid between the rolling element and the outer ring or the inner ring exerts a buffering action to suppress the generation of noise and vibration of the bearing. be able to.

[2] Also, the bearing of the present invention
A rotating part that rotates about an axis of rotation center arranged at a position different from the center;
A connecting part that is connected to the rotating part via the bearing between the rotating part and is rotatable about the center of the rotating part;
When using for a rotating device comprising
It is preferable that the piston chamber communicating with the housing portion via the communication path is disposed adjacent to the housing portion on the rotation direction side of the rotating portion.

  According to this configuration, the piston comes into contact with the inner ring or the outer ring before the rolling element. Therefore, noise and vibration can be further suppressed as compared with the case where the rolling element first contacts the inner ring or the outer ring.

[3] A specific example of the rotating device is a continuously variable transmission.
This continuously variable transmission
An input unit that is rotated by the driving force of the driving source for traveling;
An output shaft provided parallel to the rotation center axis of the input unit;
A rotating part that rotates together with the input part; a swing part provided on the output shaft; and a connecting rod as the connecting part that connects the rotary part and the swing part. A motion conversion mechanism that converts motion into a swing motion of the swing portion;
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A transmission portion that rotates by transmitting the driving force of the adjusting drive source; a pinion that is concentric with the rotation center axis; and a cam portion that is arranged eccentrically with respect to the rotation center axis. A rotation radius adjusting mechanism having a through hole for inserting the pinion, and capable of adjusting a rotation radius of the rotating portion by adjusting a relative phase between the pinion and the cam portion;
The gear ratio is changed by changing the turning radius of the rotating part.
The bearing is disposed between the rotating part and the connecting rod;
The piston chamber communicating with the housing portion via the communication path is disposed adjacent to the housing portion on the rotation direction side of the rotating portion.

Explanatory drawing which shows embodiment of the continuously variable transmission of this invention. Explanatory drawing which shows the motion conversion mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of the rotation part of this embodiment. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | swiveling part with respect to the change of the rotation radius of this embodiment. Sectional drawing which shows the bearing of this embodiment. FIG. 6A is a perspective view showing the cage of the present embodiment. FIG. 6B is an enlarged perspective view showing a part of the cage of the present embodiment. Explanatory drawing which shows the supply path | route of the fluid to the bearing of this embodiment. Explanatory drawing which shows the state with the wide space | interval between the inner ring | wheel and outer ring | wheel of the bearing of this embodiment. Explanatory drawing which shows the state where the space | interval between the inner ring | wheel and outer ring | wheel of the bearing of this embodiment is narrow.

  A continuously variable transmission according to an embodiment of the present invention includes a motion conversion mechanism including a lever crank mechanism (four-bar linkage mechanism), and a transmission ratio h (h = rotation speed of an input shaft / rotation speed of an output shaft) is infinite. It is a kind of transmission that can set the rotation speed of the output shaft to “0” by setting it to (∞), so-called IVT (Infinity Variable Transmission).

  Referring to FIG. 1, a continuously variable transmission 1 of a four-bar linkage mechanism type receives a driving force from a traveling drive source (not shown) such as an engine or an electric motor that is an internal combustion engine, so that a rotation center axis P1 is obtained. An input shaft 2 that rotates about the center, an output shaft 3 that is arranged in parallel to the rotation center axis P1, and that transmits rotational power to a drive wheel (not shown) of the vehicle via a differential gear (not shown), and a rotation center axis And six turning radius adjusting mechanisms 4 provided on P1. A propeller shaft may be provided instead of the differential gear.

  As shown in FIG. 2, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is provided with a notch hole 5b that opens in a direction eccentric to the rotation center axis P1 and communicates the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. .

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located closest to the driving source for traveling on the rotation center axis P1 is formed integrally with the input end 2a. In this way, the input shaft 2 (camshaft) is configured by the input end 2a and the cam disk 5.

  The input shaft 2 (camshaft) includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 (camshaft) is formed in a hollow shaft shape in which one end on the opposite side (left side in FIG. 1) to the driving source for driving is open and the other end is closed. As a method for integrally forming the cam disk 5 and the input end 2a, integral molding may be used, or the cam disk 5 and the input end 2a may be integrated by welding.

  The disc-shaped rotating disk 6 is provided with a receiving hole 6a for receiving the cam disk 5 in an eccentric state. In other words, a disc-shaped rotating disk 6 is rotatably fitted on each set of cam disks 5 in an eccentric state.

  As shown in FIG. 2, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance La between the rotation center axis P1 and the center point P2, and a center point P2 and a center point. It is eccentric with respect to the cam disk 5 so that the distance Lb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the input shaft 2, the pinion 70 is positioned concentrically with the rotation center axis P 1 and at a position corresponding to the inner teeth 6 b of the rotating disk 6 so that the pinion 70 can rotate relative to the input shaft 2. Has been placed. The pinion 70 is formed integrally with the pinion shaft 72. The pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling. In the present embodiment, the term “pinion 70” is defined as including the pinion shaft 72.

  The cam disk 5 is provided with a notch hole 5b that is located in the eccentric direction and allows the through hole 5a and the outer peripheral surface of the cam disk 5 to communicate with each other.

  The pinion 70 is exposed from the notch hole 5b, and the pinion 70 meshes with the internal teeth 6b through the notch hole 5b. The pinion shaft 72 is provided with a pinion bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input shaft 2 via the pinion bearing 74. The speed reduction mechanism 8 is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the speed reduction mechanism 8.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance La and the distance Lb are the same, so that the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  The continuously variable transmission 1 has a connecting rod 15 having an input-side annular portion 15a having a large diameter at one end and an output-side annular portion 15b having a smaller diameter than the diameter of the input-side annular portion 15a at the other end. Is provided.

  An input side annular portion 15a of the connecting rod 15 is externally fitted to the periphery of the rotary disk 6 via a connecting rod bearing 16 formed of a roller bearing. In addition, the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set. Six swing links 18 corresponding to the connecting rod 15 are provided on the output shaft 3 via a one-way clutch 17. The connecting rod bearing 16 of this embodiment corresponds to the bearing of the present invention.

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3. When the swing link 18 is about to rotate relative to the output shaft 3 in one direction, the swing link 18 is connected to the output shaft 3. The rocking link 18 is idled with respect to the output shaft 3 when it is fixed and tries to rotate relative to the other side.

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the output-side annular portion 15 b of the connecting rod 15 is provided below the swing link 18. The swing end portion 18a is provided with a pair of protruding pieces 18b protruding so as to sandwich the output-side annular portion 15b in the axial direction. The pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the output-side annular portion 15b. A connecting pin 19 is inserted into the insertion hole 18c and the output side annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.

  In the description of the embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 as the rotating radius of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. FIG. 3A shows a state where the eccentric amount R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.

  FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C shows a state in which the eccentric amount R1 is set to “small” which is further smaller than that in FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG.

  FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the continuously variable transmission 1 of the first embodiment, the radius of rotational motion on the input shaft 2 side can be adjusted by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  FIG. 4 shows changes in the swing range of the swing link 18 when the eccentric amount R1 (rotation radius) of the turning radius adjusting mechanism 4 is changed. 4A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 4B shows the swing range of the swing link 18 when the eccentric amount R1 is medium, and FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 4 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (motion conversion mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.

  When the input shaft 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

  Since the output side annular portion 15b of the connecting rod 15 is connected to a swing link 18 provided on the output shaft 3 via a one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.

  Further, the continuously variable transmission 1 of the present embodiment includes a control unit ECU that controls the adjustment drive source 14. The control unit ECU is an electronic unit composed of a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in the memory by the CPU, so that the eccentricity of the turning radius adjustment mechanism 4 is controlled. Serves to regulate the amount R1.

  When the rotational speed of the input shaft 2 connected to the input shaft 2 and the rotational speed of the pinion shaft 72 are the same, the rotating disk 6 rotates together with the cam disk 5. When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 72, the rotating disk 6 rotates the periphery of the cam disk 5 around the center point P <b> 2 of the cam disk 5.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance La and the distance Lb are the same, so that the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  As shown in FIG. 5, the connecting rod bearing 16 disposed between the rotary disk 6 and the input-side annular portion 15 a of the connecting rod 15 includes a ball-shaped rolling element 101, a cage 103 that holds the rolling element 101, and Is provided. In the present embodiment, the rotating disk 6 functions as an inner ring of the connecting rod bearing 16, and the input side annular portion 15 a functions as an outer ring of the connecting rod bearing 16.

  As shown in FIGS. 6A and 6B, the cage 103 has a receiving portion 103a formed so as to penetrate in the radial direction so as to receive the rolling elements 101, and the rotation direction of the rotary disk 6 with respect to the receiving portion 103a. A piston chamber 103b formed adjacent to the side and penetrating in the radial direction, and a communication passage 103c that communicates the accommodating portion 103a and the piston chamber 103b radially inward are provided.

  At both ends in the width direction of the inner peripheral surface of the cage 103, annular weir portions 103d that protrude inward in the radial direction are provided. As shown in FIG. 7, the weir 103d receives the lubricating oil supplied from the radially inner side of the connecting rod bearing 16 and guides the lubricating oil from the radially inner side to the housing 103a and the piston chamber 103b.

  FIG. 8 shows a state where the distance between the rotary disk 6 and the input side annular portion 15a is wide. At this time, lubricating oil is supplied to the accommodating portion 103a and the piston chamber 103b from the radially inner side. FIG. 9 shows a state where the distance between the rotary disk 6 and the input side annular portion 15a is narrow. Since the piston chamber 103b is provided adjacent to the accommodating portion 103a on the rotation direction side of the rotary disk 6, the piston chamber 103b shifts from a wide state to a narrow state between the rotary disk 6 and the input-side annular portion 15a. When doing so, the piston 105 contacts the input-side annular portion 15a earlier than the rolling element 101 and is pushed into the piston chamber 103b. When the piston 105 is pushed into the piston chamber 103b, the lubricating oil filled in the piston chamber 103b flows into the accommodating portion 103a in which the rolling elements 101 are accommodated via the communication path 103c.

  According to the continuously variable transmission 1 of the present embodiment, when the piston 105 comes into contact with the input-side annular portion 15a of the connecting rod 15 as an outer ring and is pushed into the piston chamber 103b, the fluid passes through the communication passage 103c. The ball-shaped rolling element 101 flows into the housing portion 103a and is pressed against the input-side annular portion 15a as an outer ring. As a result, when the rolling element 101 contacts the input-side annular portion 15a as the outer ring, the rolling element 101 comes into contact with the lubricating oil as a fluid, and the lubricating oil between the rolling element 101 and the input-side annular portion 15a as the outer ring is brought into contact. Has a buffering action, and can suppress the generation of noise and vibration of the connecting rod bearing 16, and can reduce so-called NVH (Noise, Vibration, Harshness).

  In the continuously variable transmission 1 of the present embodiment, the piston 105 is arranged in the rotational direction of the rotary disk 6 with respect to the rolling element 101. Prior to the rolling element 101, the piston 105 comes into contact with the input side annular portion 15a as an outer ring. Therefore, compared with the case where the rolling element 101 first contacts the input-side annular portion 15a as the outer ring, noise and vibration can be further suppressed, and so-called NVH (Noise, Vibration, Harshness) can be further reduced. Can do.

  Moreover, the connecting rod bearing 16 of this embodiment is comprised so that the piston 105 may contact the input side annular part 15a as an outer ring | wheel. As a result, when the interval between the input-side annular portion 15a as the outer ring and the rotary disk 6 as the inner ring becomes wide, the piston 105 pushed into the piston chamber 103b is moved radially outward by centrifugal force. Move to the side.

  In the connecting rod bearing 16 of the present embodiment, the piston chamber 103b provided so as to be adjacent to the housing portion 103a on the rotational direction side of the rotary disk 6 has been described. However, the bearing of the present invention is not limited to this, and although the reduction effect of noise and vibration is expected, the piston chamber is provided so as to be adjacent to the housing portion on the opposite side to the rotation direction of the rotation portion. In this case as well, noise and vibration can be suppressed as compared with the prior art.

  In the present embodiment, the piston 105 is abutted against the input-side annular portion 15a as the outer ring. However, the piston 105 of the present invention is configured to abut against the rotating disk 6 as the inner ring. May be. In this case, when the interval between the input side annular portion 15a as the outer ring and the rotary disk 6 as the inner ring becomes wide, the piston 105 pushed into the piston chamber 103b is pushed out of the piston chamber 103b, and the inner ring What is necessary is just to provide the urging mechanism which urges | biases to the rotating disk 6 side.

  In the present embodiment, the input end 2 a and the cam disk 5 constitute the input shaft 2, and the input shaft 2 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Explained. However, the input shaft as the input portion of the present invention is not limited to this, and for example, the input shaft can be configured as a hollow shaft having an insertion hole so that one end is opened, and the input shaft can be inserted into a disc-shaped cam disk. Thus, the through hole may be formed larger than that of the present embodiment, and the cam disk may be splined to the outer peripheral surface of the input shaft configured in the shape of a hollow shaft.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

  In the present embodiment, the input end 2a and the cam disk 5 constitute the input shaft 2 (camshaft) as the input portion, and the input shaft 2 is configured by the continuous through hole 5a of the cam disc 5. The thing provided with the insertion hole 60 to be described was demonstrated. However, the input shaft as the input portion of the present invention is not limited to this. For example, the input portion includes a hollow shaft-like input shaft having an insertion hole so that one end is opened and a plurality of disc-shaped cam disks. The through hole may be formed larger than the through hole of the first embodiment so that the input shaft can be inserted into the cam disk, and the cam disk may be splined to the outer peripheral surface of the input shaft.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. You may comprise with the two-way clutch (two-way clutch) comprised so that the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can be transmitted is switchable.

  In the present embodiment, the input unit is described as the input shaft 2 and the transmission unit is the pinion 70. However, the input unit and the transmission unit of the present invention are not limited thereto. For example, the input unit may be configured by the pinion 70 and the pinion shaft 72, and the transmission unit may be configured by the input shaft 2.

  Moreover, in this embodiment, the lever crank mechanism 20 was demonstrated as a motion conversion mechanism. However, the motion conversion mechanism of the present invention is not limited to this, and may have other configurations as long as it can convert the rotational motion of the rotating portion into the swinging motion of the swinging portion.

  In the present embodiment, a four-link mechanism type continuously variable transmission has been described as a specific example of the rotating device. However, the rotating device of the present invention is not limited to this, and the rotating unit that rotates about the rotation center axis arranged at a position different from the center and the rotating unit via the bearing of the present invention is interposed between the rotating unit and the rotating unit. Any other configuration may be used as long as it has a connecting portion that is connected to the shaft and is rotatable about the center of the rotating portion.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input shaft 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk (cam part)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Reduction mechanism (Planetary gear mechanism)
14 Driving source for adjustment (electric motor)
15 connecting rod 15a input side annular portion 15b output side annular portion 16 connecting rod bearing (bearing of the present invention)
17 One-way clutch 18 Swing link 18a Swing end 18b Projection piece 18c Insertion hole 19 Connection pin 20 Lever crank mechanism (motion conversion mechanism)
60 Insertion hole 70 Pinion 72 Pinion shaft 74 Pinion bearing 80 Case 101 Rolling body 103 Retainer 103a Housing portion 103b Piston chamber 103c Communication passage 103d Weir portion 105 Piston P1 Rotation center axis P2 Cam disk center point P3 Rotation disk center point La Distance Lb between P1 and P2 Distance R1 between P2 and P3 Eccentricity (distance between P1 and P3)

Claims (3)

A bearing comprising an inner ring, an outer ring, a rolling element, and a cage that holds the rolling element,
The retainer is provided with a housing portion that houses the rolling elements, a piston chamber, and a communication passage that communicates the housing portion and the piston chamber.
The piston chamber is inserted so that the piston can come into contact with one of the inner ring and the outer ring , and is filled with fluid,
When the piston abuts against the one of the inner ring or the outer ring and is pushed into the piston chamber, the fluid flows into the accommodating portion through the communication path, and the rolling element is connected to the inner ring or the outer ring . The bearing is pressed against the one side. A rotating device using the bearing according to claim 1,
A rotating part that rotates about an axis of rotation center arranged at a position different from the center;
A connecting portion that is connected to the rotating portion via the bearing between the rotating portion and is rotatable about the center of the rotating portion;
The rotating device, wherein the piston chamber communicating with the housing portion via the communication path is disposed adjacent to the housing portion on the rotation direction side of the rotating portion. A continuously variable transmission comprising the rotating device according to claim 2,
The continuously variable transmission is
An input unit that is rotated by the driving force of the driving source for traveling;
An output shaft provided parallel to the rotation center axis of the input unit;
The rotating unit that rotates together with the input unit, a swinging unit provided on the output shaft, and a connecting rod as the connecting unit that connects the rotating unit and the swinging unit; A motion conversion mechanism that converts the rotational motion of
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A transmission portion that rotates by transmitting the driving force of the adjusting drive source; a pinion that is concentric with the rotation center axis; and a cam portion that is arranged eccentrically with respect to the rotation center axis. A rotation radius adjusting mechanism having a through hole for inserting the pinion, and capable of adjusting a rotation radius of the rotating portion by adjusting a relative phase between the pinion and the cam portion;
The gear ratio is changed by changing the turning radius of the rotating part.
The bearing is disposed between the rotating part and the connecting rod;
The continuously variable transmission, wherein the piston chamber communicating with the housing portion via the communication path is disposed adjacent to the housing portion on a rotating direction side of the rotating portion.