JP6280756B2 - Power transmission device for vehicle - Google Patents

Description

  The present invention relates to a vehicle power transmission device.

  Patent Document 1 discloses a structure in which a general one-way clutch is refueled from within a shaft.

  Patent Document 2 discloses a continuously variable transmission that converts the rotation of the input shaft connected to the engine into the reciprocating motion of the connecting rod, and converts the reciprocating motion of the connecting rod into the rotational motion of the output shaft by a one-way clutch. Has been.

Japanese Patent No. 3507999 Specification JP 2012-1048 A

  For example, as shown in FIG. 13, the one-way clutch used in the conventional continuously variable transmission is basically disposed coaxially with the inner peripheral surface 22 a of the annular outer member 22 and the outer member 22. A roller 25 is disposed in an annular space formed between the cylindrical inner member 23 and an outer circumferential surface that is bent in a wave shape. The roller 25 is urged by an engagement spring 24 fixed to the support rod 33.

  When the one-way clutch transmits torque, the one-way clutch is engaged when the roller 25 is engaged in a wedge-shaped space formed between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23. Torque can be transmitted between the outer member 22 and the inner member 23.

  In a state where the engaged state is released, the roller 25 rotates together with the inner member 23, and differential rotation with different rotational speeds occurs between the outer member 22 and the inner member 23. At this time, the contact between the roller 25 and the outer member 22 becomes a sliding resistance and becomes a main factor of energy loss of the one-way clutch, and generates heat.

  Since the connecting rod of the continuously variable transmission power transmission unit reciprocates at a high speed, the one-way clutch repeats engagement and disengagement in a short cycle, and it is required to improve the engagement response. When lubrication between the roller 25 and the outer member 22 is insufficient when the difference in speed of differential rotation increases and the sliding resistance increases, the energy loss of the one-way clutch also increases, and the gap between the roller 25 and the outer member 22 increases. The amount of heat generated at the contact portion increases, and the function of the one-way clutch deteriorates.

  For this reason, it is necessary to concentrate and supply lubricating oil to the contact part between the roller 25 (rolling element) and the outer member 22 (outer peripheral member) for cooling.

  The present invention has been made in view of the above problems, and has a fuel supply structure capable of efficiently cooling by supplying lubricating oil to a contact portion where a calorific value increases due to contact between a rolling element and an outer peripheral member. The purpose is to provide a power transmission device.

In order to achieve the above object, the present invention described in claim 1 is a transmission that shifts the rotation of the input shaft (11) connected to the rotation shaft of the drive source and transmits it to the output shaft (12). T)
An eccentric mechanism (15, 16, 17, 18) in which the amount of eccentricity from the axis of the input shaft (11) is variable;
An input side fulcrum (O) rotating with the input shaft (11);
A one-way clutch (21) connected to the output shaft (12);
An output side fulcrum (P) provided on the outer peripheral member (22) of the one-way clutch;
A connecting rod (19) connected to both ends of the input side fulcrum (O) and the output side fulcrum (P) and reciprocating in accordance with the amount of eccentricity of the eccentric mechanism (15, 16, 17, 18);
A vehicle power transmission device comprising:
The one-way clutch (21)
An inner peripheral member (23) that is coaxially rotatable inside the outer peripheral member (22) and is connected to the output shaft (12);
A rolling element (25) that rolls between the outer peripheral member (22) and the inner peripheral member (23);
A housing member (33, 36) for housing the rolling element (25);
With
Lubricating holes (50) are provided on the side surfaces (36) of the housing members (33, 36) in parallel with the axial direction of the output shaft (12),
At the reference position (DP) where the rolling element (25) starts to engage between the outer peripheral member (22) and the inner peripheral member (23), the rolling element (25) from the lubricating hole (50). And lubricating oil is supplied between the outer peripheral member (22) ,
When the rolling element (25) is at the reference position (DP) at which the engagement starts, the lubrication hole (50) has an outer peripheral surface of the rolling element (25) and an inner periphery of the outer peripheral member (22). vehicle power transmission apparatus, wherein it is proposed that you have provided so as to be positioned between the surface (22a).

Further, in the present invention described in claim 2, in addition to the configuration of claim 1, the plurality of one-way clutches (21) are disposed adjacent to each other in the axial direction of the output shaft (12),
The housing members (36, 33) are arranged so as to rotate integrally with the output shaft (12),
On the inner peripheral member (23), a rolling surface (23a) on which the rolling element (25) is disposed is provided,
The rolling elements arranged on the rolling surface (23a) are arranged such that the phase indicating the arrangement interval is shifted for each adjacent one-way clutch (21),
The lubricating holes for supplying lubricating oil to the rolling elements disposed on the rolling surfaces (23a) on the side surfaces (36) of the accommodating members (33, 36) of the one-way clutch (21). (50) is provided, and the vehicle power transmission device is proposed.

Further, in the present invention described in claim 3, in addition to the configuration of claim 2, the lubrication for supplying lubricating oil to the rolling elements (25) arranged according to the phase indicating the arrangement interval. In the hole (50)
An oil supply pipe (51) extending in the axial direction from a side surface (36) of a housing member (33, 36) of another adjacent one-way clutch is inserted,
A vehicle power transmission device is proposed in which lubricating oil is supplied to the rolling elements (25) via the oil supply pipe (51).

According to the configuration of the first aspect, the vehicle can be efficiently cooled by supplying the lubricating oil to the contact portion between the rolling element and the outer peripheral member by supplying the side oil, and the vehicle has excellent lubricating performance. A power transmission device can be provided.
Moreover, according to the structure of Claim 1, by supplying lubricating oil to the contact part between a rolling element and an outer peripheral member, it can cool efficiently and the power transmission device for vehicles excellent in lubrication performance is provided. Provision becomes possible.

  According to the second aspect of the present invention, lubricating oil can be smoothly supplied to the one-way clutch that is not disposed at the shaft end.

  According to the third aspect of the present invention, it is possible to provide a vehicular power transmission device that can supply the lubricating oil more reliably to the lubrication target roller and can improve the lubricating performance. Is possible.

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 figure explaining the state change of a one-way clutch. The figure explaining the 1st oil supply structure which concerns on embodiment. The figure explaining the 1st oil supply structure which concerns on embodiment. The figure explaining the 1st oil supply structure which concerns on embodiment. The figure explaining the 2nd oil supply structure which concerns on embodiment. The figure explaining the modification of the 2nd oil supply structure which concerns on embodiment. The figure which illustrates the conventional one-way clutch.

  Hereinafter, embodiments of the present invention will be exemplarily described in detail with reference to FIGS. However, the components described in this embodiment are merely examples, and the technical scope of the present invention is determined by the scope of the claims, and is not limited by the following individual embodiments. Absent.

  With reference to FIG. 1, the structure of the power train of the motor vehicle in which the continuously variable transmission of this embodiment is mounted will be described. 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. The continuously variable transmission T shifts the rotation of the input shaft 11 connected to the rotation shaft of the drive source and transmits it to the output shaft 12.

  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 has a plurality of power transmission units U having the same structure (six examples are illustrated in the embodiment) stacked in the axial direction. It is a thing. 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. The continuously variable transmission T of the vehicle power transmission device includes eccentric mechanisms 15, 16, 17, 18 in which the amount of eccentricity from the axis of the input shaft 11 is variable, an input side fulcrum O that rotates together with the input shaft 11, and an output The eccentric mechanism 15 is connected to both ends of the one-way clutch 21 connected to the shaft 12, the output side fulcrum P provided on the outer peripheral member (outer member 22) of the one-way clutch, the input side fulcrum O, and the output side fulcrum P. , 16, 17 and 18, a connecting rod 19 that reciprocates according to the amount of eccentricity. The one-way clutch 21 is rotatably disposed coaxially inside the outer peripheral member (outer member 22), and has an inner peripheral member (inner member 23) connected to the output shaft 12, an outer peripheral member (outer member 22), and an inner peripheral member. A rolling element (roller 25) that rolls between (inner member 23), an accommodation member (inner race of ball bearing 34, support rod 33) that accommodates the rolling element (roller 25), and an accommodation member. A biasing portion (engagement spring 24) fixed to the support rod 33 and biasing the rolling element (roller 25) to a wedge portion formed between the outer peripheral member (outer member 22) and the inner peripheral member (inner member 23). And).

  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.

  Next, the structure of the one-way clutch and the state change of the one-way clutch will be described with reference to FIGS. 7A and 7B.

  As shown in FIG. 7A, the one-way clutch 21 of the present embodiment basically includes a circular inner peripheral surface 22 a of an annular outer member 22 and a cylindrical inner member disposed coaxially within the outer member 22. The roller 25 is disposed in an annular space formed between the outer circumferential surface 23a (rolling surface) that bends in a wavy shape. In order to form a wedge-shaped space with which the roller 25 engages between the inner peripheral surface 22a of the outer member 22 and the outer peripheral surface 23a of the inner member 23, the outer peripheral surface 23a (rolling) Surface) has a peripheral surface inclined with respect to the circular inner peripheral surface 22a of the outer member 22.

  An annular groove 22c is formed in the inner peripheral surface 22a of the outer member 22, and an annular ring spring 39 is disposed in the annular groove 22c. The ring spring 39 abuts on the circumferential surface of the roller 25 and urges toward the outer circumferential surface 23 a of the inner member 23.

  The connecting rod 19 is connected to protrusions 22b, 22b provided on the outer periphery of the outer member 22 via pins 19c and clips 40, 40. The output shaft 12 is coupled to the inner peripheral portion of the inner member 23 so as not to be relatively rotatable.

  The one-way clutch 21 includes an engagement spring 24 that urges the roller 25 in the circumferential direction of the annular space, and a support rod 33 that supports the engagement spring 24. The support rod 33 is fixed to inner races of ball bearings 34 and 34 (angular bearings).

  The engagement spring 24 is composed of a single elastic plate, and one end side of the engagement spring 24 is fixed to the support rod 33 by welding or the like, and a biasing portion that biases the roller 25 is formed on the other end side. When the urging portion comes into contact with the roller 25, the engagement spring 24 generates a pressing force. The roller 25 is biased by the pressing force of the engagement spring 24, and the engagement spring 24 pushes the roller 25 back to a position indicating a state immediately before the one-way clutch is engaged. The roller 25 can roll on the outer peripheral surface 23 a (rolling surface) of the inner member 23 by the urging force of the engagement spring 24. 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 inner race 36 of the ball bearings 34, 34 constitutes a housing member for housing the roller 25. On the side surface of the inner race 36 of the ball bearing 34, a lubricating hole 50 for supplying lubricating oil between the roller 25 and the outer member 22 is provided in parallel with the axial direction of the output shaft 12. From the lubrication hole 50 at the reference position where the roller 25 (rolling element) starts engagement between the outer member 22 (outer peripheral member) and the inner member 23 (inner peripheral member) (position in the Data Point state: DP position). Lubricating oil can be supplied between the roller 25 (rolling element) and the outer member 22 (outer peripheral member).

  The inner member 23 is held by the outer member 22 by shims and clips arranged on both sides of the ball bearings 34, 34.

  The ball bearing 34 has a plurality of balls 37 disposed between an outer ring 35 and an inner ring (inner race) 36. The outer ring 35 is formed at the axial end of the outer member 22, and the inner ring (inner race) 36 is formed of a separate member and is fixed to the outer periphery of the inner member 23. There are two types of ball bearings 34, one is a single row, and the two ball bearings 34, 34 located at both axial ends of the six one-way clutch 21 are a single row, and the other balls Since the bearing 34 is shared by the two adjacent one-way clutches 21 and 21, it becomes a double row.

  In the two single-row ball bearings 34, 34 positioned at both axial ends of the one-way clutch 21 and the other double-row ball bearings 34, the roller 25, the outer member 22, In between, a lubricating hole 50 for supplying lubricating oil is provided. The lubricating hole 50 constitutes an oil supply structure for supplying lubricating oil to a contact portion where the amount of heat generated increases due to contact between the roller 25 and the outer member 22.

  An axial spring 38 is disposed between one ball bearing 34 and the other ball bearing 34, and a plurality of protrusions 38 a protruding from the inner periphery of the axial spring 38 abuts elastically on the end surface of the roller 25. .

  Next, referring to FIG. 7B, the state change of the one-way clutch 21 will be described. FIG. 7B (A) shows a reference point DP (Datum Point state) of the one-way clutch 21, that is, a state immediately before the one-way clutch 21 is engaged (engagement start state). The DP position is a reference point for starting engagement at which the roller 25 starts engaging. Hereinafter, the DP position is also referred to as an engagement start point (reference point). In the DP state, the urging portion of the engagement spring 24 abuts on the outer peripheral surface of the roller 25 and urges the roller 25 in a direction to be engaged between the inner peripheral surface 22 a of the outer member 22 and the outer peripheral surface 23 a of the inner member 23. At this time, 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 this DP state, the roller 25 is subjected to the arrow A by the biasing force received from the engagement spring 24 and the frictional force received from the outer member 22 and the inner member 23. The one-way clutch 21 is engaged as shown in FIG. 7B by moving in the direction and engaging in a 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.

  When the outer member 22 rotates relative to the inner member 23 in the arrow B direction from the engaged state of the one-way clutch 21 shown in FIG. 7B (B), the roller 25 is caused by the frictional force received from the outer member 22 and the inner member 23. 7B (C) by moving in the direction of arrow B against the urging force received from the engagement spring 24 and detaching 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. As shown, the one-way clutch 21 is disengaged. This state is called a damping state, and the roller 25 rotates in the direction of arrow B while compressing the urging portion 24a of the engagement spring 24. The roller 25 moves from the inner peripheral surface 22a of the outer member 22 or the outer peripheral surface 23a of the inner member 23. Get away. Thereafter, the roller 25 is urged by the engagement spring 24 and quickly returns to the DP state shown in FIG. 7B (A).

  Next, with reference to FIG. 3 thru | or FIG. 6, the power transmission effect | action of the continuously variable transmission of this embodiment is demonstrated. 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). At this time, the eccentric disk 18 with respect to 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 six power transmission units U juxtaposed are shifted from each other by 60 °, so that the six power transmission units U alternately transmit the driving force. In other words, any one of the six one-way clutches 21 is always in an engaged state, so that the output shaft 12 can be continuously rotated.

(First oiling structure)
Next, the first oil supply structure of the one-way clutch 21 will be described with reference to FIGS. FIG. 8A is a view showing a cross section of the outer member 22 of the one-way clutch 21 when six power transmission units U are overlapped in the axial direction. A lubrication hole 50 for supplying lubricating oil is provided between the outer member 22 and the outer member 22. Lubricating oil flows through the lubricating holes 50 between adjacent one-way clutches.

  FIG. 8B is a diagram showing a positional relationship among the outer member 22, the roller 25, the inner member 23, and the lubrication hole 50. In FIG. 8B, the roller 25 is at a position (engagement start point (reference point)) in a DP (Datum Point) state indicating a state immediately before the one-way clutch 21 is engaged. At this position, the surface of the roller 25 is not in contact with the inner peripheral surface of the outer member 22. At the position where the roller 25 is at the engagement start point (reference point), the lubricating hole 50 is provided at a position between the surface (outer peripheral surface) of the roller 25 and the inner peripheral surface of the outer member 22.

  FIG. 9A is a diagram showing the outer member 22 of the one-way clutch 21 when six power transmission units U are stacked in the axial direction. A lubrication hole 50 for supplying lubricating oil is provided between the outer member 22 and the outer member 22. FIG. 9B is a diagram schematically showing the flow of the lubricating oil supplied from the lubricating hole 50 shown in FIG. The lubricating oil supplied from the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing on the left end LL1 side is supplied in the direction of the arrow toward the right side in the figure, and the roller 25-1 in the state immediately before engagement is supplied. Supplied to the surface. Lubricating oil flowing on the surface of the roller 25-1 flows in from a lubricating hole 50 provided on the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25-2 in a state immediately before the engagement. Supplied to the surface. Then, the lubricating oil flowing on the surface of the roller 25-2 flows from the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25- in the state immediately before the engagement. 3 surface.

  Further, the lubricating oil supplied from the lubricating hole 50 provided on the side surface of the inner race 36 of the ball bearing on the right end RR1 side is supplied in the direction of the arrow toward the left side in the figure, and the roller 25- 4 is supplied to the surface. Lubricating oil flowing on the surface of the roller 25-4 flows in from a lubrication hole 50 provided on the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25-5 in a state just before engagement. Supplied to the surface. The lubricating oil flowing on the surface of the roller 25-5 flows in from a lubricating hole 50 provided on the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25- in a state immediately before the engagement. 6 is supplied to the surface.

  The supply of the lubricating oil is not limited to the case where it is supplied from the end portion (LL1, RR1) side to the central portion (L2, R2) side of the configuration in which six one-way clutches are overlapped. It is also possible to supply from the central part (L2, R2) side toward the end part (LL1, RR1) side.

  For example, the lubricating oil supplied from the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing on the center portion L2 side is supplied in the direction of the arrow toward the left side in the figure, and the roller 25 in a state immediately before engagement. -3 surface. Lubricating oil flowing on the surface of the roller 25-3 flows into the lubricating hole 50 provided on the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25-2 in the state immediately before the engagement Supplied to the surface. Then, the lubricating oil flowing on the surface of the roller 25-2 flows from the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25- in the state immediately before the engagement. 1 surface.

  Further, the lubricating oil supplied from the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing on the central portion R2 side flows in the direction of the arrow toward the right side in the drawing, and the roller 25 in a state immediately before the engagement. -6 supplied to the surface. Lubricating oil flowing on the surface of the roller 25-6 flows from a lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25-5 in a state immediately before the engagement. Supplied to the surface. Lubricating oil flowing on the surface of the roller 25-5 flows into the lubricating hole 50 provided in the side surface of the inner race 36 of the ball bearing shared with the adjacent one-way clutch, and the roller 25-4 in the state immediately before the engagement. Supplied to the surface.

  FIG. 10 is a schematic diagram showing the positional relationship between the roller 25 and the lubrication hole 50 three-dimensionally. A lubrication hole 50 is provided for each roller 25. The circumferential position of the lubrication hole 50 in the inner race 36 corresponds to the position of the engagement start point (reference point) of the roller 25. The radial position of the lubrication hole 50 in the inner race 36 corresponds to the position between the surface (outer peripheral surface) of the roller 25 and the inner peripheral surface of the outer member 22. According to the oil supply structure in which the lubrication hole 50 is provided at this position, the lubricant oil can be supplied between the roller 25 and the outer member 22 immediately before the engagement, and the contact portion where the heat generation amount is increased by the contact. Since the lubricating oil can be supplied, the contact portion can be efficiently cooled.

(Second oil supply structure)
Next, the second oil supply structure of the one-way clutch 21 will be described with reference to FIG. FIG. 11A is a view showing a cross section of the outer member 22 of the one-way clutch 21 when six power transmission units U are overlapped in the axial direction. A lubrication hole 50 for supplying lubricating oil is provided between the outer member 22 and the outer member 22.

  FIG. 11B is a diagram showing the arrangement of the rollers 25 of each one-way clutch, and the arrangement interval (phase) of the rollers 25 is shifted by each one-way clutch. In the leftmost one-way clutch 21-1, the arrangement of two rollers is thinned between the roller 25 and a roller indicated by a broken line.

  The arrangement interval (phase) of the rollers 25 of the one-way clutch 21-2 is shifted by one roller relative to the arrangement interval of the rollers 25 of the leftmost one-way clutch 21-1. Further, the arrangement interval (phase) of the rollers 25 of the one-way clutch 21-3 is shifted by two rollers with respect to the arrangement interval of the rollers 25 of the one-way clutch 21-1.

  Further, the arrangement interval (phase) of the rollers 25 of the one-way clutch 21-5 is shifted by one roller with respect to the arrangement interval of the rollers 25 of the one-way clutch 21-4 at the right end. Further, the arrangement interval (phase) of the rollers 25 of the one-way clutch 21-6 is shifted by two rollers from the arrangement interval of the rollers 25 of the one-way clutch 21-4.

  Lubricating oil supplied from the lubricating hole 50a is supplied to the roller 25 of the one-way clutch 21-1, and lubricating oil supplied from the lubricating hole 50b is supplied to the roller 25 of the one-way clutch 21-2 and from the lubricating hole 50c. The supplied lubricating oil is supplied to the roller 25 of the one-way clutch 21-3. Since the roller arrangement interval (phase) is shifted by the one-way clutches 21-1, 21-2, 21-3, the one-way clutches 21-2, 21-3 that are not arranged at the shaft end when viewed from the left end side are used. The lubricating oil can be smoothly supplied without passing through the roller of the adjacent one-way clutch.

  The lubricating oil supplied from the lubricating hole 50d is supplied to the roller 25 of the one-way clutch 21-4, and the lubricating oil supplied from the lubricating hole 50e is supplied to the roller 25 of 21-5, from the lubricating hole 50f. The supplied lubricating oil is supplied to the roller 25 of the one-way clutch 21-6. Since the roller arrangement interval (phase) is shifted by the one-way clutch 21-4, 21-5, 21-6, the one-way clutch 21-5, 21-6 not arranged at the shaft end when viewed from the right end side. The lubricating oil can be smoothly supplied without passing through the roller of the adjacent one-way clutch.

  The above is an example in the case of supplying the lubricating oil from the end side to the center side of the configuration in which six one-way clutches are overlapped, but the same applies when the lubricating oil is supplied from the center side to the end side. It is.

  For example, the lubricating oil supplied from the central lubricating hole 50i is supplied to the roller 25 of the one-way clutch 21-3, and the lubricating oil supplied from the lubricating hole 50h is supplied to the roller 25 of the one-way clutch 21-2. The lubricating oil supplied from the lubricating hole 50g is supplied to the roller 25 of the one-way clutch 21-1. Since the roller arrangement intervals (phases) are shifted by the one-way clutches 21-1, 21-2, and 21-3, with respect to the one-way clutches 21-2 and 21-1 that are not arranged at the shaft ends when viewed from the center side. The lubricating oil can be smoothly supplied without passing through the roller of the adjacent one-way clutch.

  The lubricating oil supplied from the central lubricating hole 50m is supplied to the roller 25 of the one-way clutch 21-6, and the lubricating oil supplied from the lubricating hole 50k is supplied to the roller 25 of the one-way clutch 21-5. The lubricating oil supplied from the lubricating hole 50j is supplied to the roller 25 of the one-way clutch 21-4. Since the roller arrangement interval (phase) is shifted by the one-way clutches 21-4, 21-5, 21-6, with respect to the one-way clutches 21-5, 21-4 that are not arranged at the shaft ends when viewed from the center side. The lubricating oil can be smoothly supplied without passing through the roller of the adjacent one-way clutch.

(Modification of second oil supply structure)
FIG. 12 is a view showing a modification of the second oil supply structure shown in FIG. An oil supply pipe 51a extending in the axial direction is inserted into each of the lubrication holes (50a, 50b, 50c in FIG. 11) for supplying the lubricant from the left end side to the center side of the configuration in which six one-way clutches are overlapped. ing. Lubricating oil is supplied from each of the oil supply pipes 51a to the rollers of the one-way clutches 21-1, 21-2, and 21-3.

  An oil supply pipe 51c extending in the axial direction is inserted into each of the lubrication holes (50d, 50e, 50f in FIG. 11) for supplying the lubricant from the right end side to the center side. Lubricating oil is supplied from each of the oil supply pipes 51c to the rollers of the one-way clutches 21-4, 21-5, and 21-6.

  Furthermore, a lubrication hole (lubricating holes 50g, 50h, 50i in FIG. 11) for supplying lubricating oil from the center side to the left end side of the configuration in which six one-way clutches are overlapped and lubrication from the center side to the right end side An oil supply pipe 51b extending in the axial direction is inserted into a lubrication hole for supplying oil (lubrication holes 50j, 50k, 50m in FIG. 11). Lubricating oil is supplied to the rollers of the one-way clutches 21-3, 21-2, 21-1, and the one-way clutches 21-6, 21-5, 21-4 from each of the oil supply pipes 51b.

  The lubricating hole 50 for supplying lubricating oil to the roller 25 arranged according to the phase indicating the arrangement interval is output from the side surface (inner race 36) of the housing member (33, 36) of another adjacent one-way clutch. Oil supply pipes 51a, 51b, 51c extending in the axial direction of the shaft 12 are inserted, and lubricating oil is supplied to the respective rollers 25 through the oil supply pipes 51a, 51b, 51c.

  By using the oil supply pipes 51a, 51b, and 51c, it becomes possible to supply the lubricant more reliably to the roller to be supplied with oil, and it is possible to improve the lubrication performance.

  According to the second oil supply structure and its modification, in the state immediately before the engagement, the lubricant oil can be supplied between the roller 25 and the outer member 22, and the contact portion where the heat generation amount is increased by the contact is lubricated. Since oil can be supplied, it is possible to efficiently cool the contact portion, and it is possible to provide a vehicle power transmission device that is excellent in lubrication performance.

  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.

  In FIG. 7A, the configuration in which the support rod 33 is fixed to the inner race of the ball bearing is described as the configuration of the storage member that stores the roller 25, but the present embodiment is not limited to this example. For example, the housing member may be constituted by a pair of annular members made of an annular plate member and a cage that is arranged at equal intervals in the circumferential direction and connected to each other by the support rod 33. Is possible. In this case, the engagement spring 24 may be fixed to the support rod 33 disposed in the cage.

  Further, the one-way clutch 21 of the present embodiment can be applied to any use other than the continuously variable transmission T. The continuously variable transmission T according to the embodiment includes six power transmission units U, but the number of power transmission units U is not limited to six. 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.

Claims (3)

A transmission (T) that shifts the rotation of the input shaft (11) connected to the rotation shaft of the drive source and transmits it to the output shaft (12),
An eccentric mechanism (15, 16, 17, 18) in which the amount of eccentricity from the axis of the input shaft (11) is variable;
An input side fulcrum (O) rotating with the input shaft (11);
A one-way clutch (21) connected to the output shaft (12);
An output side fulcrum (P) provided on the outer peripheral member (22) of the one-way clutch;
A connecting rod (19) connected to both ends of the input side fulcrum (O) and the output side fulcrum (P) and reciprocating in accordance with the amount of eccentricity of the eccentric mechanism (15, 16, 17, 18);
A vehicle power transmission device comprising:
The one-way clutch (21)
An inner peripheral member (23) that is coaxially rotatable inside the outer peripheral member (22) and is connected to the output shaft (12);
A rolling element (25) that rolls between the outer peripheral member (22) and the inner peripheral member (23);
A housing member (33, 36) for housing the rolling element (25);
With
Lubricating holes (50) are provided on the side surfaces (36) of the housing members (33, 36) in parallel with the axial direction of the output shaft (12),
At the reference position (DP) where the rolling element (25) starts to engage between the outer peripheral member (22) and the inner peripheral member (23), the rolling element (25) from the lubricating hole (50). And lubricating oil is supplied between the outer peripheral member (22) ,
When the rolling element (25) is at the reference position (DP) at which the engagement starts, the lubrication hole (50) has an outer peripheral surface of the rolling element (25) and an inner periphery of the outer peripheral member (22). surface (22a) and the vehicle power transmission apparatus characterized by that provided so as to be positioned between the. The plurality of one-way clutches (21) are disposed adjacent to each other in the axial direction of the output shaft (12),
The housing members (36, 33) are arranged so as to rotate integrally with the output shaft (12),
On the inner peripheral member (23), a rolling surface (23a) on which the rolling element (25) is disposed is provided,
The rolling elements arranged on the rolling surface (23a) are arranged such that the phase indicating the arrangement interval is shifted for each adjacent one-way clutch (21),
The lubricating holes for supplying lubricating oil to the rolling elements disposed on the rolling surfaces (23a) on the side surfaces (36) of the accommodating members (33, 36) of the one-way clutch (21). (50) is provided. The power transmission device for vehicles of Claim 1 characterized by the above-mentioned. In the lubricating hole (50) for supplying lubricating oil to the rolling elements (25) arranged according to the phase indicating the arrangement interval,
An oil supply pipe (51) extending in the axial direction from a side surface (36) of a housing member (33, 36) of another adjacent one-way clutch is inserted,
Lubricating oil is supplied to the said rolling element (25) via the said oil supply pipe (51). The power transmission device for vehicles of Claim 2 characterized by the above-mentioned.