JP2014222097A - Vehicle power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a drive load of an oil pump by changing a ratio of oil supplied to an input shaft and an output shaft.SOLUTION: When an input shaft 12 connected to an engine E is rotated, an eccentric disk 19 of each variable speed unit 14 is eccentrically rotated. When a connecting rod 33 with one end thereof connected to the eccentric disk 19 is reciprocated, an output shaft 13 is rotated through a one-way clutch 36 to which the other end of the connecting rod 33 is connected. When eccentricity of the eccentric disk 19 is changed, a transmission gear ratio is changed along with a change in a stroke of reciprocal motion of the connecting rod 33. A flow rate regulation mechanism 54 which is installed on an output shaft side oil passage 53 supplying oil discharged from an oil pump 51 to a side of the output shaft 13 regulates a flow rate of the oil in a manner that reduces the flow rate of the oil as the eccentricity of the eccentric disk 19 gets smaller (as the transmission gear ratio gets larger), thereby minimizing a load of the oil pump 51 with the flow rate of the oil supplied to the output shaft side oil passage 53 reduced in accordance with a reduction in a rotation speed of the output shaft 13.

Description

  The present invention provides an input-side fulcrum in which each of a plurality of transmission units that transmit rotation of an input shaft connected to a drive source to an output shaft rotates eccentrically with the input shaft, and a one-way clutch connected to the output shaft The present invention relates to a vehicle power transmission device including an output side fulcrum provided on an outer member of the one-way clutch, and a connecting rod that is connected to both ends of the input side fulcrum and the output side fulcrum and reciprocates.

  In such a vehicle power transmission device, oil discharged from the oil pump is supplied to one end of an oil passage formed in the axial direction inside the input shaft and the output shaft, and the oil is bent by the torque transmission. Patent Document 1 below discloses a method of lubricating a lubricated portion such as a bearing or a one-way clutch arranged on the outer periphery of an input shaft and an output shaft while supplying the oil passage toward the other end of the oil passage. It is. This vehicle power transmission device uses an oil oil to compensate for a decrease in the amount of oil supplied due to the bending due to a decrease in the transmission torque when the input side fulcrum has a large amount of eccentricity, thereby reducing the bending of the input shaft and the output shaft. Increasing the pump discharge rate, conversely, offsetting the increase in oil supply due to the deflection due to increased transmission torque and increased deflection of the input and output shafts when the eccentricity of the input fulcrum is small Therefore, the oil pump discharge amount is reduced.

JP 2012-251618 A

  By the way, in such a vehicle power transmission device, when the eccentric amount of the input side fulcrum decreases, the gear ratio increases and the rotational speed of the output shaft decreases, and when the eccentric amount becomes zero, the gear ratio becomes infinite. Even if is rotating, the output shaft stops rotating (geared neutral state). In such a state, lubricated parts such as bearings and one-way clutches arranged on the outer periphery of the output shaft require little oil, but in the conventional one, oil is supplied to the input shaft and the output shaft at a constant ratio. Therefore, there is a problem that the amount of oil supplied to the output shaft becomes excessive and the driving load of the oil pump increases unnecessarily.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to reduce the oil pump driving load by changing the ratio of the amount of oil supplied to the input shaft and the output shaft.

  In order to achieve the above object, according to the first aspect of the present invention, each of the plurality of transmission units that transmit the rotation of the input shaft connected to the drive source to the output shaft is rotated together with the input shaft. The input side fulcrum, the one-way clutch connected to the output shaft, the output-side fulcrum provided on the outer member of the one-way clutch, and both ends connected to the input-side fulcrum and the output-side fulcrum to reciprocate. A power transmission device for a vehicle including a connecting rod, wherein an oil pump, an input shaft side oil passage for supplying oil discharged from the oil pump to the input shaft side, and oil output by the oil pump are output to the vehicle An output shaft side oil passage to be supplied to the shaft side, and a flow rate restriction mechanism for restricting a flow rate of the oil in the output shaft side oil passage. The vehicle power transmission device and limits so that the flow rate of about oil amount is reduced is reduced is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the flow rate limiting mechanism limits the oil flow rate to zero when the eccentricity amount is zero. A vehicle power transmission device is proposed.

  According to the invention described in claim 3, in addition to the configuration of claim 1 or claim 2, the flow rate limiting mechanism includes an eccentric cam fixed to the input shaft and an outer periphery of the eccentric cam. A mission that surrounds an outer periphery of the input shaft, an eccentric disc that is rotatably supported, a speed change shaft that is relatively rotatably disposed within the input shaft, and that rotates the eccentric disc relative to the eccentric cam. A hollow cone member that is slidably supported by the case in the axial direction and has a cone surface formed on the inner periphery thereof, a spring member that urges the hollow cone member toward the large diameter side, and the hollow cone member A vehicular power transmission device comprising: a blocking member that changes a flow passage cross-sectional area of the output shaft side oil passage; and a drive member that is provided on the eccentric disk and contacts the cone surface. Proposed

  According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, the drive member is provided on each of the two eccentric disks whose phases in the eccentric direction are shifted from each other by 180 °. A vehicle power transmission device is proposed.

  According to a fifth aspect of the present invention, in addition to the configuration of the third or fourth aspect, the eccentric disk is a member constituting the input side fulcrum. Is proposed.

  According to the invention described in claim 6, in addition to the configuration of claim 1 or claim 2, the flow rate limiting mechanism includes an eccentric cam fixed to the input shaft and a relative position inside the eccentric cam. An eccentric disk that is rotatably supported, a transmission shaft that is relatively rotatably disposed inside the input shaft and that rotates the eccentric disk relative to the eccentric cam, and a part of the oil passage on the output shaft side. And an oil hole that passes through the eccentric disk in the axial direction and an oil groove that forms a part of the output shaft side oil passage and is formed in an arc shape in the eccentric cam and communicates with the oil hole. A vehicle power transmission device is proposed in which the amount of overlap between the oil hole and the oil groove is changed by relative rotation of the eccentric cam and the eccentric disk.

  The second eccentric cam 18 ′ and the third eccentric cam 18 ″ of the embodiment correspond to the eccentric cam of the present invention, and the eccentric disk 19 of the embodiment corresponds to the input side fulcrum of the present invention. The second eccentric disk 19 ′ and the third eccentric disk 19 ″ correspond to the eccentric disk of the present invention, the pin 37 of the embodiment corresponds to the output side fulcrum of the present invention, and the engine E of the embodiment corresponds to the present invention. Corresponds to the driving source.

  According to the configuration of claim 1, when the input shaft connected to the drive source rotates, the input side fulcrum of each transmission unit rotates eccentrically, and when the connecting rod having one end connected to the input side fulcrum reciprocates, the connecting The output shaft rotates through a one-way clutch to which the other end of the rod is connected. When the eccentric amount of the input side fulcrum changes, the stroke of the reciprocating motion of the connecting rod changes and the gear ratio is changed. The flow rate limiting mechanism provided in the output shaft side oil passage that supplies the oil discharged from the oil pump to the output shaft side is such that the flow rate of the oil decreases as the eccentric amount of the input side fulcrum decreases (as the gear ratio increases). Therefore, as the rotational speed of the output shaft decreases, the flow rate of the oil supplied to the output shaft side oil passage decreases, and the load on the oil pump is minimized.

  According to the second aspect of the present invention, the flow rate limiting mechanism limits the oil flow rate to zero when the amount of eccentricity is zero, so that the oil to the output shaft side when the output shaft stops rotating. By stopping the supply of the oil pump, the load of the oil pump can be further reduced.

  According to the third aspect of the present invention, when the speed change shaft that is relatively rotatable inside the input shaft is rotated, the amount of eccentricity of the eccentric disc that rotates relative to the eccentric cam changes, and the eccentric disc is provided on the eccentric disc. The amount of eccentricity of the driving member changes. As a result, the hollow cone member with which the drive member abuts on the inner cone surface moves in the axial direction while balancing with the elastic force of the spring member, and the blocking member provided on the hollow cone member becomes the output shaft side oil. By changing the flow path cross-sectional area of the path, the flow rate of oil flowing through the output shaft side oil path changes according to the gear ratio.

  According to the fourth aspect of the present invention, since the drive member is provided on each of the two eccentric disks whose phases in the eccentric direction are shifted from each other by 180 °, the drive member can be smoothly moved without twisting the hollow cone member. .

  According to the fifth aspect of the present invention, since the eccentric disk is a member constituting the input side fulcrum, the drive member can be operated using the existing eccentric disk without providing a special eccentric disk.

  According to the sixth aspect of the present invention, when the speed change shaft that is rotatably arranged inside the input shaft is rotated, the eccentric disk rotates relative to the eccentric cam, and the oil hole that penetrates the eccentric disk in the axial direction. When the amount of overlap with the oil groove formed in the arc shape in the eccentric cam changes, the flow rate of the oil flowing through the output shaft side oil passage changes according to the gear ratio.

1 is an overall perspective view of a vehicle power transmission device. FIG. (First embodiment) The partially broken perspective view of the principal part of the power transmission device for vehicles. (First embodiment) FIG. 3 is a sectional view taken along line 3-3 in FIG. 1. (First embodiment) FIG. 4 is an enlarged view of part 4 of FIG. 3. (First embodiment) FIG. 5 is a sectional view taken along line 5-5 of FIG. (First embodiment) The figure which shows the shape of an eccentric disk. (First embodiment) The figure which shows the relationship between the eccentric amount of an eccentric disk, and a gear ratio. (First embodiment) The figure which shows the state of the eccentric disk in TD gear ratio and UD gear ratio. (First embodiment) FIG. 5 is a cross-sectional view of the flow restriction mechanism corresponding to FIG. 4. (Second Embodiment) FIG. 5 is a cross-sectional view of the flow restriction mechanism corresponding to FIG. 4. (Third embodiment) FIG. 11 is a view taken along line 11-11 in FIG. 10. (Third embodiment) The exploded view of the component of a flow restriction mechanism. (Third embodiment)

First embodiment

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 5, a transmission case 11 of a continuously variable transmission T for an automobile includes a case body 11A, a right cover 11B coupled to the right side surface of the case body 11A, and a left side surface of the case body 11A. And a left cover 11C coupled to An input shaft 12 and an output shaft 13 are supported in parallel to each other on the case body 11A, and the rotation of the input shaft 12 connected to the engine E is performed via the six transmission units 14..., The output shaft 13 and the differential gear D. Transmitted to the drive wheel. A variable speed shaft 15 sharing an axis L with the input shaft 12 is fitted into the hollow formed input shaft 12 via seven needle bearings 16 so as to be relatively rotatable. Since the structure of the six transmission units 14 is substantially the same, the structure will be described below with one transmission unit 14 as a representative.

  The transmission unit 14 includes a pinion 17 provided on the outer peripheral surface of the transmission shaft 15, and the pinion 17 is exposed from an opening 12 a formed in the input shaft 12. A disc-shaped eccentric cam 18 divided into two in the direction of the axis L is splined to the outer periphery of the input shaft 12 so as to sandwich the pinion 17. The center O1 of the eccentric cam 18 is eccentric with respect to the axis L of the input shaft 12 by a distance d. Further, the six eccentric cams 18 of the six transmission units 14 are offset in phase by 60 ° from each other.

  On the outer peripheral surface of the eccentric cam 18, a pair of eccentric recesses 19 a and 19 a formed on both end surfaces in the axis L direction of the disc-shaped eccentric disk 19 are rotatably supported via a pair of needle bearings 20 and 20. . The center O1 of the eccentric recesses 19a, 19a (that is, the center O1 of the eccentric cam 18) is shifted from the center O2 of the eccentric disk 19 by a distance d. That is, the distance d between the axis L of the input shaft 12 and the center O1 of the eccentric cam 18 and the distance d between the center O1 of the eccentric cam 18 and the center O2 of the eccentric disk 19 are the same.

  A pair of crescent-shaped guide portions 18a and 18a are provided on the split surface of the eccentric cam 18 divided into two in the direction of the axis L so as to be coaxial with the center O1 of the eccentric cam 18. The tooth tips of the ring gear 19b formed so as to communicate between the bottoms of the recesses 19a and 19a slidably contact the outer peripheral surfaces of the guide portions 18a and 18a of the eccentric cam 18. Then, the pinion 17 of the transmission shaft 15 meshes with the ring gear 19b of the eccentric disk 19 through the opening 12a of the input shaft 12.

  The right end side of the input shaft 12 is directly supported by the right wall of the case body 11 </ b> A of the mission case 11 via the ball bearing 21. A cylindrical portion 18b provided integrally with one eccentric cam 18 positioned on the left end side of the input shaft 12 is supported on the left wall of the case body 11A of the transmission case 11 via a ball bearing 22, The left end side of the input shaft 12 splined to the inner periphery of the eccentric cam 18 is indirectly supported by the mission case 11.

  The speed change actuator 23 that changes the speed ratio of the continuously variable transmission T by rotating the speed change shaft 15 relative to the input shaft 12 is supported by the transmission case 11 so that the motor shaft 24a is coaxial with the axis L. A motor 24 and a planetary gear mechanism 25 connected to the electric motor 24 are provided. The planetary gear mechanism 25 includes a carrier 27 that is rotatably supported by an electric motor 24 via a needle bearing 26, a sun gear 28 that is fixed to the motor shaft 24a, and a plurality of two stations that are rotatably supported by the carrier 27. A pinion 29, a first ring gear 30 splined to the shaft end of the hollow input shaft 12 (strictly speaking, the cylindrical portion 18b of the one eccentric cam 18), and a spline to the shaft end of the transmission shaft 15 And a second ring gear 31 coupled thereto. Each double pinion 29 includes a first pinion 29a having a large diameter and a second pinion 29b having a small diameter. The first pinion 29a meshes with the sun gear 28 and the first ring gear 30, and the second pinion 29b has a second ring gear. Mesh with 31.

  On the outer periphery of the eccentric disk 19, an annular portion 33 a on one end side of the connecting rod 33 is supported via a roller bearing 32 so as to be relatively rotatable.

  The output shaft 13 is supported on the case body 11A of the mission case 11 by a pair of ball bearings 34 and 35, and a one-way clutch 36 is provided on the outer periphery thereof. The one-way clutch 36 includes a ring-shaped outer member 38 pivotally supported at the tip of the rod portion 33b of the connecting rod 33 via a pin 37, and an inner member disposed inside the outer member 38 and fixed to the output shaft 13. 39 and a plurality of rollers 41 arranged in a wedge-shaped space formed between the inner circular arc surface of the outer member 38 and the outer peripheral plane of the inner member 39 and biased by a plurality of springs 40. … And.

  As shown in FIGS. 6 and 8, since the center O1 of the eccentric recesses 19a and 19a (that is, the center O1 of the eccentric cam 18) is shifted from the center O2 of the eccentric disk 19 by a distance d, the outer circumference of the eccentric disk 19 And the inner periphery of the eccentric recesses 19a, 19a are non-uniform in the circumferential direction, and crescent-shaped thinning recesses 19c, 19c are formed at portions where the interval is large.

  Next, the operation of one transmission unit 14 of the continuously variable transmission T will be described.

  As is clear from FIGS. 5 and 7A to 7D, when the input shaft 12 is rotated by the engine E when the center O2 of the eccentric disk 19 is eccentric with respect to the axis L of the input shaft 12. As the annular portion 33a of the connecting rod 33 rotates eccentrically around the axis L, the rod portion 33b of the connecting rod 33 reciprocates.

  As a result, when the connecting rod 33 is pulled back and forth in the process of reciprocating movement, the rollers 41 urged by the springs 40 bite into the wedge-shaped space between the outer member 38 and the inner member 39, and the outer member 38 and the inner member 39 are coupled via the rollers 41... So that the one-way clutch 36 is engaged and the movement of the connecting rod 33 is transmitted to the output shaft 13. On the other hand, when the connecting rod 33 is reciprocated, the rollers 41 are pushed out of the wedge-shaped space between the outer member 38 and the inner member 39 while compressing the springs 40. As the inner members 39 slip each other, the one-way clutch 36 is disengaged and the movement of the connecting rod 33 is not transmitted to the output shaft 13.

  Thus, since the rotation of the input shaft 12 is transmitted to the output shaft 13 for a predetermined time while the input shaft 12 rotates once, the output shaft 13 rotates intermittently when the input shaft 12 rotates continuously. Although the eccentric amounts ε of the eccentric disks 19 of the six transmission units 14 are all the same, the phases in the eccentric direction are shifted by 60 ° from each other, so that the six transmission units 14 of the input shaft 12 By alternately transmitting the rotation to the output shaft 13, the output shaft 13 rotates continuously.

  At this time, as the eccentric amount ε of the eccentric disk 19 increases, the reciprocating stroke of the connecting rod 33 increases, and the one-time rotation angle of the output shaft 13 increases, and the transmission ratio of the continuously variable transmission T decreases. Conversely, the smaller the eccentric amount ε of the eccentric disk 19, the smaller the reciprocating stroke of the connecting rod 33, the smaller the rotation angle of the output shaft 13, and the higher the gear ratio of the continuously variable transmission T. When the eccentric amount ε of the eccentric disk 19 becomes zero, the connecting rod 33 stops moving even when the input shaft 12 rotates, so the output shaft 13 does not rotate, and the gear ratio of the continuously variable transmission T is maximized ( Infinity).

  When the transmission shaft 15 does not rotate relative to the input shaft 12, that is, when the input shaft 12 and the transmission shaft 15 rotate at the same speed, the transmission ratio of the continuously variable transmission T is maintained constant. In order to rotate the input shaft 12 and the transmission shaft 15 at the same speed, the electric motor 24 may be rotationally driven at the same speed as the input shaft 12. The reason is that the first ring gear 30 of the planetary gear mechanism 25 is connected to the input shaft 12 and rotates at the same speed as the input shaft 12. When the electric motor 24 is driven at the same speed, the sun gear 28 and the first ring gear 30 are driven. Rotate at the same speed, the planetary gear mechanism 25 is locked and rotates as a whole. As a result, the input shaft 12 and the transmission shaft 15 connected to the first ring gear 30 and the second ring gear 31 that rotate integrally are integrated and rotate at the same speed without relative rotation.

  When the rotational speed of the electric motor 24 is increased or decreased with respect to the rotational speed of the input shaft 12, the first ring gear 30 coupled to the input shaft 12 and the sun gear 28 connected to the electric motor 24 rotate relative to each other. The carrier 27 rotates relative to the first ring gear 30. At this time, the gear ratio of the first ring gear 30 and the first pinion 29a meshing with each other is slightly different from the gear ratio of the second ring gear 31 and the second pinion 29b meshing with each other. And the transmission shaft 15 connected to the second ring gear 31 rotate relative to each other.

  When the transmission shaft 15 rotates relative to the input shaft 12 in this manner, the eccentric recesses 19 a and 19 a of the eccentric disk 19 in which the ring gear 19 b is engaged with the pinion 17 of each transmission unit 14 are integrated with the input shaft 12. The cam 18 rotates while being guided by the guide portions 18a, 18a, and the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 changes.

  FIG. 7A shows a state where the speed ratio is minimum (speed ratio: TD). At this time, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the axis L of the input shaft 12. To a center O1 of the eccentric cam 18 and a maximum value equal to 2d, which is the sum of the distance d from the center O1 of the eccentric cam 18 to the center O2 of the eccentric disk 19. As shown in FIGS. 7B and 7C, when the transmission shaft 15 rotates relative to the input shaft 12, the eccentric disk 19 rotates relative to the eccentric cam 18 integral with the input shaft 12. Furthermore, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is gradually decreased from the maximum value 2d, and the transmission ratio is increased. When the transmission shaft 15 further rotates relative to the input shaft 12, the eccentric disk 19 further rotates relative to the eccentric cam 18 integral with the input shaft 12, and finally, as shown in FIG. The center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentricity ε becomes zero, the transmission gear ratio is maximized (infinite) (transmission ratio: UD), and power is transmitted to the output shaft 13. Blocked.

  Next, the lubricating structure of the continuously variable transmission T will be described.

  As shown in FIGS. 3 and 4, an oil pump 51 such as a trochoid pump is provided on the outer periphery of the right end of the input shaft 12, and this oil pump 51 removes oil stored at the bottom of the transmission case 11 from an intake port 51a. Inhaled and discharged from the discharge port 51b. The suction port 51a is connected to an input shaft side oil passage 52 formed in the right cover 11B, the case main body 11A and the left cover 11C, and an oil passage 24b formed in the motor shaft 24a of the electric motor 24 of the transmission actuator 23. And communicates with an oil passage 15 a formed inside the transmission shaft 15. Therefore, the oil discharged from the oil pump 51 is lubricated to the needle bearings 16 through the plurality of oil holes 15b branched in the radial direction from the oil passage 15a of the transmission shaft 15, and then scattered outward in the radial direction by centrifugal force. Then, the lubricated parts such as the needle bearings 20 and the roller bearings 32 are lubricated.

  Further, an output shaft side oil passage 53 branched from the input shaft side oil passage 52 is formed on the split surface of the right cover 11B, and the output shaft side oil passage 53 surrounds the output shaft 13 with the right cover 11B. It communicates with a plurality of oil passages 13a formed in the output shaft 13 through the formed annular groove 11a. Therefore, the oil discharged from the oil pump 51 is supplied from the output shaft side oil passage 53 to the oil passages 13a of the output shaft 13 through the annular groove 11a, and passes through the plurality of oil holes 13b branched in the radial direction therefrom. Then, the lubricated parts such as the one-way clutch 36 are lubricated.

  The flow rate of oil flowing through the output shaft side oil passage 53 is limited by the flow rate limiting mechanism 54. The flow restriction mechanism 54 includes a hollow cone member 55 disposed inside the case main body 11A so as to surround the outer periphery of the input shaft 12. The hollow cone member 55 is a substantially cylindrical member having a conical cone surface 55a formed on the inner periphery, and a guide protrusion 55b protruding from the left end is slidable in the axis L direction in a guide groove 11b formed in the case body 11A. The guide protrusion 55c protruding from the right end is slidably fitted in the guide groove 11c formed in the case body 11A in the direction of the axis L, and is attached to the right side by a spring member 56 disposed at the bottom of the guide groove 11b. Be forced. A blocking member 57 protruding from the tip of the right guide protrusion 55 c passes through the output shaft side oil passage 53. The blocking member 57 has a step and the outer diameter is changed. In the illustrated state, the flow path of the output shaft side oil passage 53 is opened to the maximum, and when the right side is moved from this state, the output shaft side oil passage 53 is opened. The flow path is gradually throttled until it is completely closed.

  The hollow cone member 55 is not completely cylindrical, and a portion facing the output shaft 13 is partially opened, and six connecting rods pass from the inside to the outside of the hollow cone member 55 through the open portion. 33 ... passes.

  Among the six transmission units 14..., For example, the eccentric disks 19 and 19 of the second and fifth transmission units 14 from the right side are each pair of drives that project in a disk shape radially outward from the outer periphery thereof. Members 58 and 58 are provided. That is, the pair of drive members 58 are fixed to both side surfaces of each eccentric disk 19 so as to sandwich the annular portion 33a of the roller bearing 32 and the connecting rod 33. The center of the disk-shaped drive member 58 coincides with the center O2 of the eccentric disk 19, and the outer peripheral surfaces of the pair of drive members 58 are inclined along the cone surface 55 a of the hollow cone member 55. Since the cone surface 55a of the hollow cone member 55 increases in diameter toward the right side, the diameter of the drive member 58 of the second transmission unit 14 from the right is the same as the diameter of the drive member 58 of the fourth transmission unit 14 from the right. Is bigger than.

  In the present embodiment, the drive member 58 is provided on the eccentric disk 19 of the second and fifth transmission units 14 from the right side, but the transmission unit 14 provided with the drive member 58 is optional. However, it is desirable to select two transmission units 14 in which the eccentric disks 19 are out of phase with each other by 180 °. The reason is that if the two eccentric disks 19 are 180 ° out of phase with each other, the drive member 58 of one eccentric disk 19 and the drive member 58 of the other eccentric disk 19 sandwich the axis L. This is because it is possible to prevent the hollow cone member 55 from being damaged by contacting the cone surface 55a on both sides.

  3 and 4 show a state in which the eccentric amount ε of the eccentric discs 19 is maximum and the gear ratio is TD, and the outer peripheral surface of the drive member 58 that protrudes to the outside in the radial direction is the hollow cone member. The hollow cone member 55 slides to the left in the direction of the axis L while compressing the spring member 56 by contacting the cone surface 55a of 55 and pressing it outward in the radial direction. As a result, the stepped portion of the blocking member 57 is disengaged from the output shaft side oil passage 53 and the output shaft side oil passage 53 is opened to the maximum, so that a sufficient amount of oil can be supplied to the output shaft 13. it can.

  When the eccentric amount ε of the eccentric disk 19 decreases from this state and the transmission gear ratio changes to the UD side, the drive member 58 moves so as to approach the axis L, so that the hollow cone member is generated by the elastic force of the spring member 56. 55 slides to the right in the direction of the axis L. As a result, the stepped portion of the blocking member 57 enters the output shaft side oil passage 53 and the flow path of the output shaft side oil passage 53 is gradually narrowed, so that the flow rate of oil supplied to the output shaft 13 is reduced. It gradually decreases. When the eccentric amount ε of the eccentric disks 19 becomes zero and the output shaft 13 stops rotating, the blocking member 57 completely closes the output shaft side oil passage 53, so that the oil is supplied to the output shaft 13. No longer done.

  As described above, according to the present embodiment, when the amount of eccentricity ε of the eccentric disks 19 increases, the gear ratio decreases, and the rotational speed of the output shaft 13 increases, the oil supplied to the output shaft 13 increases. When the amount of oil automatically increases and, conversely, the amount of eccentricity ε of the eccentric disk 19 decreases, the transmission ratio increases, and the rotational speed of the output shaft 13 decreases, the oil supplied to the output shaft 13 Since the amount automatically decreases, it becomes possible to always supply the minimum necessary oil to the output shaft 13, and to reduce the fuel consumption of the engine E by minimizing the driving load of the oil pump 51. it can.

Second embodiment

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the eccentric disks 19 and 19 of the two transmission units 14 and 14 of the continuously variable transmission T are used, and the drive member 58 is provided thereon to operate the flow restriction mechanism 54. In the second embodiment, a flow restriction mechanism 54 is provided separately from the transmission units 14.

  That is, the flow restricting mechanism 54 is provided at the right end portion of the transmission case 11 and can be relatively rotated on the outer periphery of the pair of second eccentric cams 18 ′ and 18 ′ fixed on the outer periphery of the input shaft 12. And a pair of second eccentric disks 19 'and 19' fitted to the outer periphery of the input shaft 12 and meshed with second ring gears 19b 'and 19b' of the pair of second eccentric disks 19 'and 19'. Second pinions 17 'and 17' are provided.

  A drive member 58 is integrally provided on the outer periphery of the second eccentric disk 19 ′, and these drive members 58 abut against the cone surface 55 a of the hollow cone member 55. The hollow cone member 55 is biased to the right by a spring member 56, and a blocking member 57 that enters the output shaft side oil passage 53 is provided at the right end of the hollow cone member 55. The phases of the two second eccentric disks 19 ′ and 19 ′ in the eccentric direction are shifted from each other by 180 °.

  The operation of the second embodiment is the same as that of the first embodiment. When the amount of eccentricity ε of the second eccentric disks 19 ′ and 19 ′ decreases and the drive member 58 moves radially inward, the second embodiment The cone member 55 moves to the right side by the elastic force of the spring member 56, and the blocking member 57 narrows the flow path of the output shaft side oil passage 53 to reduce the flow rate of oil supplied to the output shaft 13.

  According to the present embodiment, since it is not necessary to cover the six transmission units 14 with the hollow cone member 55, not only can the size be reduced, but there is no possibility of interference with the connecting rods 33. In addition, it is not necessary to form an opening in the hollow cone member 55.

Third embodiment

  Next, a third embodiment of the present invention will be described with reference to FIGS.

  In the third embodiment, as in the second embodiment, the flow restriction mechanism 54 is provided at the right end of the transmission case 11 independently of the transmission unit 14 of the continuously variable transmission T. Is different from the second embodiment.

  That is, the flow restricting mechanism 54 is rotatably fitted in a recess 11d formed in a circle centered on the axis L on the transmission case 11 and rotates integrally with the input shaft 12, and a third eccentric cam 18 ″. An annular third eccentric disc fitted into a support hole 18c formed eccentrically from the axis L inside the three eccentric cam 18 ″ and rotatably supported by a needle bearing 59 and a pair of thrust bearings 60, 60. 19 ″, and a ring gear 19b ″ that meshes with a pinion 17 ″ fixed to the input shaft 12 is formed at the center of the third eccentric disk 19 ″, and one oil penetrating both sides thereof A hole 19d is formed.

  On the other hand, arc-shaped oil grooves 18d and 18d centering on the center of the third eccentric disk 19 ″ are formed on the two inner surfaces of the third eccentric cam 18 ″ facing both side surfaces of the third eccentric disk 19 ″. The oil grooves 18d, 18d have a central angle of 180 °, and the groove width is gradually narrowed from one end side to the other end side. The oil passage 53 communicates with the oil groove 18d through the annular groove 18e on the right outer periphery of the third eccentric cam 18 ″ and the oil hole 18f, and the downstream output shaft side oil passage 53 is on the left side of the third eccentric cam 18 ″. The oil groove 18d communicates with the outer circumferential groove 18e and the oil hole 18f.

  Therefore, when the eccentric amount ε of the eccentric disk 19 of the transmission unit 14 is large, that is, when the speed ratio is small and the rotation speed of the output shaft 13 is large, the oil discharged from the oil pump 51 is the upstream output shaft side oil. Road 53 → Right annular groove 18e → Right oil hole 18f → Right oil groove 18d → Oil hole 19d → Left oil groove 18d → Left oil hole 18f → Left annular groove 18e → Downstream output shaft side oil At this time, both ends of the oil hole 19d of the third eccentric disk 19 ″ communicate with the wide portions of the pair of oil grooves 18d, 18d of the third eccentric cam 18 ″. The oil flow rate is increased and a sufficient amount of oil is supplied to the output shaft 13.

  On the other hand, when the eccentric amount ε of the eccentric disk 19 of the transmission unit 14 decreases, the third eccentric disk 19 ″ rotates relative to the third eccentric cam 18 ″, and the oil hole 19d of the third eccentric disk 19 ″ The third eccentric cam 18 ″ communicates with the narrow portions of the pair of oil grooves 18d, 18d, and the flow rate of the oil supplied to the output shaft 13 gradually decreases by reducing the flow rate of the oil there. When the amount of eccentricity ε becomes zero, the oil hole 19d of the third eccentric disk 19 ″ and the pair of oil grooves 18d, 18d of the third eccentric cam 18 ″ are not communicated, and the supply of oil to the output shaft 13 is stopped. The

  As described above, according to the third embodiment, it is possible to achieve the same operational effects as those of the second embodiment.

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

  For example, the drive source of the present invention is not limited to the engine E of the embodiment, and may be another drive source such as an electric motor.

11 Transmission case 12 Input shaft 13 Output shaft 14 Transmission unit 15 Transmission shaft 18 Eccentric cam 18 'Second eccentric cam (Eccentric cam)
18 ″ 3rd eccentric cam (Eccentric cam)
18d Oil groove 19 Eccentric disc (input side fulcrum)
19 'Second eccentric disk (eccentric disk)
19 ″ Third Eccentric Disc (Eccentric Disc)
19d Oil hole 33 Connecting rod 36 One-way clutch 37 Pin (output side fulcrum)
38 Outer member 51 Oil pump 52 Input shaft side oil passage 53 Output shaft side oil passage 54 Flow rate limiting mechanism 55 Hollow cone member 55a Cone surface 56 Spring member 57 Blocking member 58 Drive member E Engine (drive source)
ε Eccentricity

Claims (6)

Each of the plurality of transmission units (14) for transmitting the rotation of the input shaft (12) connected to the drive source (E) to the output shaft (13) is an input side fulcrum that rotates eccentrically with the input shaft (12). 19), a one-way clutch (36) connected to the output shaft (13), an output side fulcrum (37) provided on an outer member (38) of the one-way clutch (36), and the input side fulcrum ( 19) and a connecting rod (33) reciprocatingly connected at both ends to the output side fulcrum (37),
An oil pump (51), an input shaft side oil passage (52) for supplying the oil discharged from the oil pump (51) to the input shaft (12) side, and the oil discharged from the oil pump (51) An output shaft side oil passage (53) to be supplied to the output shaft (13) side, and a flow rate restriction mechanism (54) for restricting the flow rate of oil in the output shaft side oil passage (53),
The vehicular power transmission device, wherein the flow rate limiting mechanism (54) limits the oil flow rate to be smaller as the eccentric amount (ε) of the input fulcrum (19) is smaller.   The vehicle power transmission device according to claim 1, wherein the flow rate limiting mechanism (54) limits the flow rate of the oil to zero when the eccentricity (ε) is zero.   The flow restricting mechanism (54) includes an eccentric cam (18, 18 ') fixed to the input shaft (12) and an eccentric disk supported on the outer periphery of the eccentric cam (18, 18') so as to be relatively rotatable. (19, 19 ') and a speed change mechanism which is disposed in the input shaft (12) so as to be relatively rotatable and rotates the eccentric disk (19, 19') relative to the eccentric cam (18, 18 '). A hollow cone member (55) supported axially slidably in the transmission case (11) so as to surround the outer periphery of the shaft (15) and the input shaft (12) and having a cone surface (55a) formed on the inner periphery. ), A spring member (56) for urging the hollow cone member (55) toward the large diameter side, and a flow path of the output shaft side oil passage (53) provided on the hollow cone member (55). A blocking member (57) for changing the cross-sectional area; The vehicle power transmission device according to claim 1 or 2, further comprising a drive member (58) provided on a core disk (19, 19 ') and abutting against the cone surface (55a). .   The power for a vehicle according to claim 3, wherein the drive member (58) is provided on each of the two eccentric disks (19, 19 ') whose phases in the eccentric direction are shifted from each other by 180 °. Transmission device.   The vehicle power transmission device according to claim 3 or 4, wherein the eccentric disk (19) is a member constituting the input side fulcrum. The flow restricting mechanism (54) includes an eccentric cam (18 ″) fixed to the input shaft (12) and an eccentric disk (19 ″) supported relatively rotatably inside the eccentric cam (18 ″). A transmission shaft (15) that is relatively rotatably disposed inside the input shaft (12) and rotates the eccentric disk (19 ″) relative to the eccentric cam (18 ″), and the output shaft side. A part of the oil passage (53), an oil hole (19d) passing through the eccentric disk (19 ″) in the axial direction, and a part of the output shaft side oil passage (53) are formed, and the eccentricity An oil groove (18d) formed in an arc shape on the cam (18 ″) and communicating with the oil hole (19d);
The overlap amount of the oil hole (19d) and the oil groove (18d) is changed by relative rotation of the eccentric cam (18 ") and the eccentric disk (19"). Item 3. The vehicle power transmission device according to Item 2.

Images