Source: https://patents.google.com/patent/JP5590098B2/en
Timestamp: 2019-12-12 01:42:58
Document Index: 13449726

Matched Legal Cases: ['art 11', 'art 11', 'art 11', 'art 11', 'art 21', 'art 21', 'art 11', 'art 21', 'art 11', 'art 41', 'art 42', 'art 43', 'arts 41', 'art 43', 'art 41', 'art 42', 'art 42', 'art 41', 'art 42', 'art 43', 'art 41', 'art 41', 'art 43', 'art 42', 'art 46', 'art 46', 'art 11', 'art 20', 'art 21', 'art 21', 'art 22', 'art)\n30', 'art 121', 'art 192']

JP5590098B2 - Continuously variable transmission - Google Patents
JP5590098B2
JP5590098B2 JP2012241120A JP2012241120A JP5590098B2 JP 5590098 B2 JP5590098 B2 JP 5590098B2 JP 2012241120 A JP2012241120 A JP 2012241120A JP 2012241120 A JP2012241120 A JP 2012241120A JP 5590098 B2 JP5590098 B2 JP 5590098B2
JP2012241120A
JP2014092175A (en
晃 日比野
有希 荒津
2012-10-31 Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
2012-10-31 Priority to JP2012241120A priority Critical patent/JP5590098B2/en
2014-05-19 Publication of JP2014092175A publication Critical patent/JP2014092175A/en
2014-09-17 Publication of JP5590098B2 publication Critical patent/JP5590098B2/en
The present invention includes a plurality of power transmission elements having a common rotation center axis and a plurality of rolling members arranged radially with respect to the rotation center axis, and is sandwiched between two of the power transmission elements. Further, the present invention relates to a traction drive type continuously variable transmission that continuously changes the speed ratio between input and output by tilting each rolling member.
Conventionally, as this type of continuously variable transmission, a transmission shaft serving as a rotation center, a plurality of power transmission elements capable of relative rotation with the central axis of the transmission shaft as a rotation central axis, and the rotation central shaft A ball planetary type is known that includes a plurality of radially arranged rolling members sandwiched between three of the power transmission elements. In this ball planetary continuously variable transmission, each rolling member is sandwiched between a first power transmission element and a second power transmission element arranged to face each other, and each rolling member is a third power transmission element. It is arrange | positioned on the outer peripheral surface. Patent Document 1 below discloses such a ball planetary continuously variable transmission. In the continuously variable transmission of Patent Document 1, an axial center oil passage and a radial oil passage are provided in a transmission shaft, and lubricating oil (traction oil) is supplied to the rolling member and each power transmission through these oil passages. Supply to the contact area with the element.
Special table 2008-516165 gazette
By the way, in a continuously variable transmission in operation, the lubricating oil supplied from the transmission shaft is guided outward in the radial direction by centrifugal force, so that an amount of lubrication corresponding to the difference between the supply amount and the discharge amount is obtained. Oil is stored in an annular state on the inner peripheral surface side of the case. Therefore, this continuously variable transmission has a power transmission element having a concentric outer peripheral surface facing the inner peripheral surface of the case and a rotating member connected to the power transmission element. When the transmission element or the like is immersed in a lubricating oil storage portion, a stirring resistance is generated between the power transmission element or the like and the case, which may cause a reduction in power transmission efficiency. The continuously variable transmission of Patent Document 1 includes a scraper for scraping the lubricant oil and returning it to the transmission shaft side. However, the structure is complicated and the scraped lubricant oil is removed from the transmission shaft. Therefore, the lubricating oil must resist the centrifugal force, and the stirring resistance may not be sufficiently reduced.
Accordingly, an object of the present invention is to provide a continuously variable transmission that can improve the disadvantages of the conventional example and reduce the stirring resistance by the lubricating oil.
To achieve the above object, the present invention provides first to fourth powers capable of relative rotation in the circumferential direction between a transmission shaft serving as a rotation center and a first rotation center shaft concentric with the transmission shaft. A first transmission element and a second rotation center axis are arranged on the outer peripheral surface of the third power transmission element in a radial manner around the first rotation center axis and arranged opposite to each other. And a rolling member that is sandwiched between the second power transmission elements and is tiltably held by the fourth power transmission element, and a gear that changes the transmission ratio between the input and output by tilting each of the rolling members. Lubricating oil is supplied into the housing from the radially inner side to the radially outer side, the device, the transmission shaft, the first to fourth power transmission elements, and the housing that houses the rolling member. A lubricating oil supply hole, wherein the housing is in an axial direction of the transmission shaft. At least one side wall of the housing, and, radially outward from the lubricating oil supply hole, a discharge hole for discharging the lubricating oil in the housing to the outside of the casing, wherein the discharge hole, the When viewed in the axial direction, a position intersecting the contact portion or the contact preliminary portion between the rolling member and the first and second power transmission elements, or a radial direction from the contact portion or the contact preliminary portion. It is characterized by being formed on the outside .
Here, a concentric first rotating shaft connected to the first power transmission element and a concentric second rotating shaft connected to the second power transmission element are arranged on one side wall side in the axial direction of the housing. When extending to the side, the discharge hole is preferably provided on the other side wall in the axial direction of the housing.
Moreover, it is desirable to provide a guide portion for guiding the lubricating oil in the housing to the discharge hole in the housing.
Further, when the lubricating oil in the casing is in an annular state on the radially outer side in the casing due to centrifugal force during operation, the discharge hole is in the annular lubricating oil when viewed in the axial direction. It is desirable to form at a position intersecting with the oil surface on the radially inner side or on the radially outer side with respect to the oil surface.
Further, when the lubricating oil in the casing is in an annular state on the radially outer side in the casing due to centrifugal force during operation, the radially inner oil surface in the annular lubricating oil is the first oil surface. And when the second hole is within a radial range from the respective contact portion between the second power transmission element and each of the rolling members to the guide surface of the lubricating oil in the guide portion, When viewed in the direction, it is desirable to form at a position that intersects the oil surface.
Further, it is desirable that the discharge hole communicates the inside of the casing with a transmission gear chamber in which a transmission gear of the transmission is accommodated.
In the continuously variable transmission according to the present invention, the lubricating oil in the housing is discharged out of the housing through the discharge hole. Therefore, in this continuously variable transmission, even if a centrifugal force acts on the lubricating oil in the casing, a member (first power transmission) having an inner peripheral face of the casing and an outer peripheral face facing the inner peripheral face. The amount of lubricating oil flowing in between the element and the second power transmission element) can be reduced. Therefore, in this continuously variable transmission, the stirring resistance of the member due to the lubricating oil can be reduced, and the member can be smoothly rotated, so that a reduction in power transmission efficiency can be suppressed. In addition, in this continuously variable transmission, it is possible to reduce the agitation resistance due to the lubricating oil of the member without enlarging the casing in the radial direction. Can also be planned.
FIG. 1 is a cross-sectional view showing an example of the configuration of a continuously variable transmission according to an embodiment of the present invention. FIG. 2 is a diagram illustrating one fixed disk portion of the carrier. FIG. 3 is a diagram for explaining the other fixed disk portion and the rotating disk portion of the carrier. FIG. 4 is a view of the inside of the transmission gear chamber in the continuously variable transmission as viewed in the direction of arrow A in FIG. FIG. 5 is a diagram illustrating the positions of the discharge holes. FIG. 6 is a diagram illustrating the position and shape of the discharge hole of the example. FIG. 7 is a diagram illustrating the positions and shapes of the discharge holes of the first modification. FIG. 8 is a cross-sectional view showing an example of the configuration of a continuously variable transmission of Modification 2 according to the present invention.
Embodiments of a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.
An embodiment of a continuously variable transmission according to the present invention will be described with reference to FIGS.
First, an example of a traction drive type continuously variable transmission according to the present embodiment will be described with reference to FIG. This continuously variable transmission includes a ball planetary continuously variable transmission mechanism corresponding to a traction planetary mechanism. Reference numeral 1 in FIG. 1 shows an example of a ball planetary continuously variable transmission in the present embodiment.
The continuously variable transmission mechanism of the present embodiment includes four power transmission elements having a common first rotation center axis R1, a plurality of rolling members arranged radially around the first rotation center axis R1, and 4 And a transmission shaft disposed at the rotation center of the two power transmission elements. The rolling member has a second rotation center axis R2 different from the first rotation center axis R1, and is on a tilt plane including its own second rotation center axis R2 and the first rotation center axis R1. Tilt operation is possible. In the following, unless otherwise specified, the direction along the first rotation center axis R1 is referred to as an axial direction, and the direction around the first rotation center axis R1 is referred to as a circumferential direction. Further, the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.
This continuously variable transmission mechanism clamps each rolling member with three of the four power transmission elements (first to third power transmission elements) and the remaining power transmission elements (fourth power transmission elements). Thus, each rolling member is held to be rotatable and tiltable. Each rolling member is arranged radially about the first rotation center axis R1. And each rolling member is clamped by the 1st and 2nd power transmission element arrange | positioned facing in the axial direction, and is arrange | positioned on the outer peripheral surface of a 3rd power transmission element.
The continuously variable transmission mechanism can transmit torque via the rolling members between the first to fourth power transmission elements. For example, the continuously variable transmission mechanism generates a traction force (tangential force) between the first to third power transmission elements and each rolling member, so that the first to third power transmission elements Torque (power) can be transmitted through each rolling member. The traction force is generated by pressing at least one of the first and second power transmission elements against each rolling member. Furthermore, in this continuously variable transmission mechanism, torque can be transmitted between the fourth power transmission element and each rolling member by allowing the fourth power transmission element to rotate.
In this continuously variable transmission mechanism, the second rotation center axis R2 of each rolling member is tilted with respect to the first rotation center axis R1 on the tilt plane, and each rolling member is tilted. The ratio of the rotational speed (number of rotations) between the input and output, that is, the speed ratio γ is changed.
In this continuously variable transmission mechanism, some of the first to fourth power transmission elements may be used as rotating elements that can rotate relative to the transmission shaft. Some of them are used as fixed elements that cannot rotate relative to the transmission shaft. In the case of the former configuration, any one of the first to fourth power transmission elements serves as a torque input unit, and another one serves as a torque output unit. On the other hand, in the case of the latter configuration, torque is transmitted through the respective rolling members between the three power transmission elements other than the fixed elements, so that any one of the three power transmission elements is A torque input section is provided, and another one is a torque output section. For this reason, in this continuously variable transmission mechanism, the ratio of the rotational speed (number of rotations) between the power transmission element serving as the input unit and the power transmission element serving as the output unit is the gear ratio γ. For example, the continuously variable transmission 1 is disposed on the power transmission path of the vehicle. In that case, the input part is connected to the power source side such as an engine (engine such as an internal combustion engine) or a rotating machine (electric motor or the like), and the output part is connected to the drive wheel side. Another transmission (for example, a stepped manual transmission or an automatic transmission) may be interposed between the continuously variable transmission 1 and the drive wheel side. In this continuously variable transmission 1, the rotational operation of each power transmission element when torque is input to the power transmission element as an input unit is referred to as positive drive, and when the power transmission element as an output unit is in positive drive. The rotation operation of each power transmission element when reverse direction torque is input is called reverse drive. For example, in the continuously variable transmission 1, according to the example of the preceding vehicle, when torque is input from the power source side to the power transmission element as an input portion and the power transmission element is rotated, such as acceleration. Becomes forward drive, and reverse drive occurs when torque in the direction opposite to that during forward drive is input from the drive wheel side to the rotating power transmission element as the output unit, such as deceleration.
Here, in the continuously variable transmission 1, the first and second power transmission elements function as a ring gear or the like as in the traction planetary mechanism. The third power transmission element and the fourth power transmission element function as a sun roller and a carrier in the traction planetary mechanism, respectively. The rolling member functions as a ball-type pinion in the traction planetary mechanism. Therefore, the continuously variable transmission 1 includes the first and second rotating members 10 and 20 as the first and second power transmission elements, the sun roller 30 as the third power transmission element, and the fourth power transmission element. A carrier 40, a planetary ball 50 as a rolling member, and a shaft 60 as a transmission shaft. The shaft 60 is fixed to a fixed portion of the continuously variable transmission 1 in the casing CAt or a vehicle body (not shown), and is a columnar or cylindrical fixed shaft configured not to rotate relative to the fixed portion. And In the continuously variable transmission 1, the reference position is a state in which the first rotation center axis R1 and the second rotation center axis R2 are parallel to each other on the tilt plane (state in FIG. 1). In addition, although the case where the carrier 40 is used as a fixed element is illustrated here (however, only the rotating disk portion 42 described later is allowed to rotate), the carrier 40 is a rotating element in various oil paths described later. This can also be applied.
The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis R1, and each planetary ball is opposed in the axial direction. 50 is interposed. In this example, both are circular members.
The continuously variable transmission 1 has contact portions P1 and P2 in which the first and second rotating members 10 and 20 and the planetary balls 50 are in point contact with each other (strictly, elliptical surface contact). . As will be described in detail later, each planetary ball 50 has an outer peripheral curved surface as a rolling surface, and is sandwiched between the first and second rotating members 10 and 20 on the outer peripheral curved surface. That is, each planetary ball 50 has contact portions P1 and P2 on its outer peripheral curved surface. On the other hand, the first and second rotating members 10 and 20 sandwich the planetary balls 50 from the radially outer side, and have contact portions P1 and P2 on the inner peripheral surfaces 10a and 20a, respectively. In the inner peripheral surfaces 10a and 20a, the contact portions P1 and P2 that are actually in contact with the planetary balls 50 and the contact portions P1 and P2 as the first and second rotating members 10 and 20 rotate. Are connected in the circumferential direction (hereinafter referred to as “contact preliminary portion”). That is, the contact preliminary portion is a portion that repeatedly contacts or leaves the planetary ball 50 as the first and second rotating members 10 and 20 rotate. The shapes of the contact portions P1, P2 and the contact spare portion of the first and second rotating members 10, 20 are, for example, a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 50, and the curvature of the outer peripheral curved surface thereof. Has a concave arc surface, a convex arc surface, a flat surface or the like having different curvatures. The shapes of the contact portions P1 and P2 and the contact preliminary portion of the first and second rotating members 10 and 20 are axial forces from the first and second rotating members 10 and 20 toward the planetary ball 50. When a (pressing force) is applied, a force (normal force) in a radially inner side and an oblique direction is applied to the planetary ball 50.
Here, in the state of the reference position, the first and second rotating members 10, 2 are arranged so that the shortest distances from the second rotation center axis R 2 to the contact portions P 1, P 2 and the contact preliminary portions are the same length. 20 inner peripheral surfaces 10a, 20a and outer peripheral curved surfaces of the planetary balls 50 are formed. Further, here, the inner circumferences of the first and second rotating members 10 and 20 are set so that the contact angles θ of the first and second rotating members 10 and 20 and the planetary balls 50 are the same. The outer peripheral curved surfaces of the surfaces 10a and 20a and each planetary ball 50 are formed. The contact angle θ is a line connecting the contact portions P1 and P2 or the contact spare portion with respect to the reference plane and the center of the planetary ball 50 (rotation center and tilt center, which corresponds to the center of gravity in the case of a sphere). It is an angle. The reference plane is a plane extending in the radial direction having the center of each planetary ball 50.
In this example, the first rotating member 10 is used as a torque input unit during positive driving, and the second rotating member 20 is used as a torque output unit during positive driving. In this continuously variable transmission 1, the side on which the first rotating member 10 serving as the input unit with respect to the reference plane is disposed is referred to as the torque input side, and the second unit serving as the output unit with respect to the reference plane. The side on which the rotating member 20 is disposed is referred to as a torque output side. In the axial direction, the direction from the output side to the input side is referred to as the torque input side direction, and the direction from the input side to the output side is referred to as the torque output side direction. An input shaft (first rotation shaft) 11 concentric with the first rotation member 10 is connected to the first rotation member 10, and an output shaft (first rotation) concentric with the second rotation member 20 is connected to the second rotation member 20. 2 rotation shafts) 21 are connected.
The input shaft 11 and the output shaft 21 extend together on either the torque input side or the output side. The illustrated input shaft 11 and output shaft 21 extend together on the torque input side where the first rotating member 10 and the like are disposed. The input shaft 11 includes a disk part 11a with which the first rotating member 10 is connected to the outer edge part, a cylindrical part 11b extending from the radially inner part of the disk part 11a toward the torque input side, Is provided. The disk part 11 a is arranged in the direction of torque input with respect to the first rotating member 10 and the carrier 40, and covers a first disk member 41 (described later) of the carrier 40 together with the first rotating member 10. On the other hand, the output shaft 21 has a first cylindrical portion 21a that covers the first and second rotating members 10 and 20 from the outer side in the radial direction, and an end of the first cylindrical portion 21a in the input side direction of torque as an outer edge. And a second cylindrical portion 21c extending from the radially inner portion of the disc portion 21b toward the torque input side. The 1st cylindrical part 21a is connected with the 2nd rotation member 20 via the annular member 22 fixed to the edge part of the output side direction of a torque. The disk part 21 b is arranged in the torque input side direction with respect to the disk part 11 a of the input shaft 11. The 2nd cylindrical part 21c covers the cylindrical part 11b of the input shaft 11 from a radial direction outer side.
The input shaft 11 and the output shaft 21 can rotate in the circumferential direction about the first rotation center axis R1. Further, the input shaft 11 and the output shaft 21 can relatively rotate in the circumferential direction via the bearing B1 and the thrust bearing TB between them. Further, the input shaft 11 and the output shaft 21 can rotate relative to the shaft 60 in the circumferential direction.
Between the input shaft 11 and the first rotating member 10, an axial force generator 71 that generates an axial force is provided. The axial force is a pressing force in the axial direction for pressing the first rotating member 10 against each planetary ball 50. Here, a torque cam is used as the axial force generator 71. Therefore, the axial force generating portion 71 is configured so that the engaging portion or the engaging member in the outer edge portion of the disk portion 11a is engaged with the engaging portion or the engaging member on the first rotating member 10 side, so that the input shaft 11 An axial force is generated between the first rotating member 10 and the first rotating member 10, and a rotational torque is transmitted to rotate them integrally. On the other hand, the continuously variable transmission 1 is also provided with an axial force generator 72 between the output shaft 21 and the second rotating member 20. The axial force generating unit 72 generates axial pressing force (axial force) for pressing the second rotating member 20 against each planetary ball 50, and a torque cam similar to the axial force generating unit 71 is used. The axial force generator 72 is connected to the output shaft 21 via the annular member 22.
The continuously variable transmission 1 has an axial force between the first rotating member 10 and each planetary ball 50, between the second rotating member 20 and each planetary ball 50, and between the sun roller 30 and each planetary ball 50. In the meantime, traction force can be generated during operation.
In the continuously variable transmission 1, the first rotating member 10 can be used as a torque output unit, and the second rotating member 20 can be used as a torque input unit. Is used as the output shaft, and the one provided as the output shaft 21 is used as the input shaft. When the sun roller 30 is used as a torque input unit or a torque output unit, an input shaft and an output shaft that are separately configured are connected to the sun roller 30.
The sun roller 30 is disposed concentrically with the shaft 60 and performs relative rotation in the circumferential direction with respect to the shaft 60. A plurality of planetary balls 50 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 is a rolling surface when the planetary ball 50 rotates. The sun roller 30 can roll (rotate) each planetary ball 50 by its own rotation, or it can rotate along with the rolling operation (spinning) of each planetary ball 50.
The sun roller 30 of the present embodiment is such that the contact portions with each planetary ball 50 are dispersed in two locations (first contact portion P3 and second contact portion P4) in the axial direction. The reason is that by reducing the contact pressure by dispersing the contact force between the sun roller 30 and the planetary ball 50, the spin loss can be reduced, the decrease in power transmission efficiency can be suppressed, and the durability can be improved. is there. The first contact portion P3 is provided on one of the axial directions around the reference plane. On the other hand, the 2nd contact part P4 is provided in the other of the axial direction centering on the reference plane. The first and second contact portions P3, P4 have the same distance from the center of each planetary ball 50 (the center of rotation and the tilt, which is equivalent to the center of gravity in the case of a sphere), and The shortest distance from the first rotation center axis R1 is also provided at the same position. In the first and second contact portions P3 and P4, the sun roller 30 and each planetary ball 50 are in point contact (strictly surface contact) with each other.
The sun roller 30 is divided into two rotating bodies (a first rotating body 31 and a second rotating body 32) capable of rotating in the circumferential direction with respect to the shaft 60, and a first contact portion P3 is provided on the first rotating body 31. At the same time, a second contact portion P4 is provided on the second rotating body 32. This is because the loss energy between the sun roller 30 and the planetary ball 50 is reduced by rotating the first and second rotating bodies 31 and 32 relative to each other in the circumferential direction, thereby suppressing reduction in power transmission efficiency. Because it can.
In the sun roller 30, the first rotating body 31 is disposed on one side in the axial direction centering on the reference plane, and the second rotating body 32 is disposed on the other side in the axial direction centering on the reference plane. The first and second rotating bodies 31 and 32 are attached to the shaft 60 via angular bearings AB and radial bearings RB, respectively, so that relative rotation in the circumferential direction with respect to the shaft 60 can be performed.
In the first contact portion P <b> 3, an oblique pressing force is applied from the first rotating body 31 to the planetary ball 50 in the axial direction on the second rotating body 32 side and radially outward. On the other hand, in the second contact portion P4, a pressing force in an oblique direction is applied to the planetary ball 50 from the second rotating body 32 in the axial direction on the first rotating body 31 side and radially outward. For this reason, the sun roller 30 has a conical portion in which the outer diameter is uniformly reduced as it approaches the second rotating body 32, and the outer diameter is equalized as it approaches the first rotating body 31. The 2nd rotary body 32 has a cone part which becomes small. The 1st contact part P3 and the 2nd contact part P4 are provided on the outer peripheral surface of each cone part. Moreover, you may substitute the cone part for the 1st rotary body 31 and the 2nd rotary body 32 to an arc-shaped cone part. The arc-shaped cone portion has a shape in which the outer diameter decreases in a parabolic shape as the other rotating body is approached. The 1st contact part P3 and the 2nd contact part P4 are provided on the outer peripheral surface of each arcuate cone part. The cone part and the arcuate cone part are formed on all or part of the outer peripheral surfaces of the first rotating body 31 and the second rotating body 32.
The planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30 around the support shaft 51. The planetary ball 50 is preferably a perfect spherical body, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. The support shaft 51 is penetrated through the center of the planetary ball 50 and supports the planetary ball 50 rotatably. For example, the planetary ball 50 can rotate relative to the support shaft 51 around the second rotation center axis R2 (that is, rotate) by a bearing such as a needle bearing disposed between the outer periphery of the support shaft 51 and the like. Both ends of the support shaft 51 are projected from the planetary ball 50.
The reference position of the support shaft 51 is the reference position shown in FIG. 1 described above, and is the position where the second rotation center axis R2 is parallel to the first rotation center axis R1. The support shaft 51 can swing (tilt) together with the planetary ball 50 between a reference position and a position tilted therefrom in the tilt plane. The tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane.
The carrier 40 supports each projecting portion of the support shaft 51 so as not to prevent the tilting motion of each planetary ball 50. The carrier 40 includes, for example, first to third disk portions 41, 42, and 43 that are arranged such that the center axis coincides with the first rotation center axis R1 and is opposed to each other in the axial direction. In the carrier 40, the first disk part 41 and the second disk part 42 are arranged with an interval in the axial direction, and the third disk part 43 is arranged close to one of them. In the carrier 40, the sun roller 30 and the planetary ball 50 are disposed between the two disk parts of the first to third disk parts 41, 42, and 43. In this illustration, the third disk part 43 is arranged between the first disk part 41 and the second disk part 42 and close to the second disk part 42, and the first disk part 41 and the third disk part 42 are arranged. The sun roller 30 and the planetary ball 50 are arranged between In the carrier 40, the third disk portion 43 is not necessarily provided.
In the carrier 40, one of the first and second disk portions 41, 42 is configured to be capable of relative rotation in the circumferential direction with respect to the shaft 60, and the other of the first and second disk portions 41, 42 is configured in the circumferential direction with respect to the shaft 60. Configure to prevent relative rotation. Further, the third disk portion 43 is configured so as not to be able to rotate relative to the shaft 60 in the circumferential direction. In this example, it is assumed that the first and third disk portions 41 and 43 cannot be rotated relative to the shaft 60, and the second disk portion 42 can be rotated relative to the shaft 60. The first disk portion 41 has an inner diameter side fixed to the outer diameter side of the shaft 60 with, for example, a screw member. The second disk portion 42 is attached on the inner diameter side to the outer diameter side of the shaft 60 via a bearing (not shown). The third disk part 43 is connected to the first disk part 41 by, for example, a plurality of support shafts (not shown). The first disk part 41 and the third disk part 43 have a bowl shape, and a part of the planetary ball 50 protrudes from the gap between the support shafts. The first and second rotating members 10 and 20 are in contact with the protruding portion of the planetary ball 50. Hereinafter, the first disk portion 41 is referred to as a first fixed disk portion 41, the second disk portion 42 is referred to as a rotating disk portion 42, and the third disk portion 43 is referred to as a second fixed disk portion 43.
In the continuously variable transmission 1, the first rotating member 10 and the second rotating member 20 are enclosed in a sealed casing CAt (excluding portions communicating with the outside by lubricating oil discharge holes 92 and 95 described later). The sun roller 30, the carrier 40, the planetary ball 50, the shaft 60, the axial force generators 71 and 72, the input shaft 11 and the output shaft 21 are accommodated. The shaft 60, the cylindrical portion 11b of the input shaft 11, and the second cylindrical portion 21c of the output shaft 21 are projected in the axial direction from the casing CAt while keeping the sealed state of the casing CAt.
Here, in the continuously variable transmission 1, when the tilt angle of each planetary ball 50 is the reference position, that is, 0 degrees, the first rotating member 10 and the second rotating member 20 have the same rotational speed (the same rotational speed). Rotation speed). That is, at this time, the rotation ratio (ratio of the rotation speed or the number of rotations) of the first rotation member 10 with respect to the second rotation member 20 is 1, and the speed ratio γ is 1. On the other hand, when each planetary ball 50 is tilted from the reference position, the shortest distance from the center axis (second rotation center axis R2) of the support shaft 51 to the contact portion P1 with the first rotation member 10 changes. In addition, the shortest distance from the central axis of the support shaft 51 to the contact portion P2 with the second rotating member 20 changes. Therefore, one of the first rotating member 10 and the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. For example, the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 50 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed). Therefore, in the continuously variable transmission 1, the rotation ratio (gear ratio γ) of the first rotating member 10 with respect to the second rotating member 20 can be changed steplessly by changing the tilt angle. When the speed is increased (γ <1), the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper and the lower planetary ball 50 is tilted clockwise on the paper. . Further, at the time of deceleration (γ> 1), the upper planetary ball 50 in FIG. 1 is tilted in the clockwise direction on the paper, and the lower planetary ball 50 is tilted in the counterclockwise direction on the paper.
The continuously variable transmission 1 is provided with a transmission that changes its speed ratio γ. Since the gear ratio γ changes as the tilt angle of the planetary ball 50 changes, a tilting device that tilts each planetary ball 50 is used as the speed change device. Here, the carrier 40 is provided with a function as a tilting device (transmission device).
First, the first and second fixed disk portions 41 and 43 are provided with radial guide portions 44 and 45 for each planetary ball 50. The radial guide portions 44 and 45 are guide portions that guide the end portion in the radial direction when a tilting force is applied to the end portion of the support shaft 51 protruding from the planetary ball 50. . The radial guide portion 44 is, for example, a guide groove or a guide hole whose longitudinal direction is the radial direction (FIG. 2). On the other hand, the radial guide portion 45 is a guide hole whose radial direction is the longitudinal direction (FIG. 3), and penetrates the support shaft 51. That is, in the first and second fixed disk portions 41 and 43, when viewed from the axial direction, the radial guide portions 44 and 45 are radially centered about the first rotation center axis R1. The respective radial guide portions 44 and 45 are formed at positions facing each other in the axial direction, and the second rotation center axis R2 is located on a substantially tilting plane regardless of the speed ratio γ. The support shaft 51 is held. The reason for “substantially” is that a slight gap is provided between the support shaft 51 and the width direction of the radial guide portions 44 and 45 for smooth tilting operation of the support shaft 51. FIG. 2 is a view of the first fixed disk portion 41 viewed in the axial direction from the planetary ball 50 side. FIG. 3 is a view of the rotating disk portion 42 and the second fixed disk portion 43 as viewed in the axial direction from the planetary ball 50 side.
As described above, the rotating disk portion 42 can rotate relative to the shaft 60 in the circumferential direction. For the relative rotation, an actuator (drive unit) such as an electric motor (not shown) is used. The driving force of the driving unit is transmitted to the rotating disk unit 42 through a gear group (hereinafter referred to as “transmission gear”) 81 such as a planetary gear mechanism. The transmission gear 81 is disposed on the side opposite to the extending direction in the axial direction of the input shaft 11 and the output shaft 21 (in this example, on the torque output side) and outside the casing CAt. In this example, as shown in FIGS. 1 and 4, a transmission gear 81 is disposed on the radially outer side of the shaft 60. The transmission gear 81 is disposed in a transmission gear chamber 82 (excluding portions communicating with the outside through lubricating oil discharge holes 92 and 93 described later) in a sealed casing CAg. The casing CAg constitutes a transmission gear chamber 82 by being attached to the casing CAt of the continuously variable transmission 1. The shaft 60 projects from the casing CAg in the axial direction while keeping the sealed state of the casing CAg.
On the other hand, the rotating disk part 42 is provided with a tilting force applying part 46 for each planetary ball 50. The tilting force applying unit 46 applies a tilting force to one end portion of the support shaft 51 protruding from the planetary ball 50 as the rotating disk unit 42 rotates. For example, the tilting force applying part 46 is a linear groove or hole whose longitudinal direction is inclined at a predetermined inclination angle with respect to the radial direction (FIG. 3). When viewed from the axial direction, a portion of the tilting force applying portion 46 overlaps a portion of the radial guide portion 45. The intersecting portion where the portions overlap each other moves in the radial direction as the rotating disk portion 42 rotates. One end of the support shaft 51 is supported at the intersection. Therefore, when the rotating disk portion 42 is rotated, a tilting force acts on one end portion of the support shaft 51 from the side wall surface of the tilting force applying portion 46, and the end portion is a radial guide. Guided in the radial direction by the portions 44 and 45. In the continuously variable transmission 1, this guiding operation is a tilting operation of the planetary ball 50.
Specifically, in the carrier 40, the tilting force corresponding to the relative rotation acts on one end portion of the support shaft 51 by relatively rotating the first fixed disk portion 41 and the rotating disk portion 42. . For example, when the rotary disk portion 42 is rotated in the clockwise direction in FIG. 3, the side wall pushes one end portion of the support shaft 51 along the radially outer side wall in the tilting force applying portion 46. To do. At this time, the pushing force becomes a tilting force, and one end portion of the support shaft 51 is moved radially inward by the radial guide portions 44 and 45, so that the speed ratio γ is shifted to the speed increasing side. . On the other hand, when the rotating disk portion 42 is rotated in the counterclockwise direction in FIG. 3, the side wall pushes one end of the support shaft 51 along the radially inner side wall of the tilting force applying portion 46. Move. At this time, the pushing force is a tilting force, and one end portion of the support shaft 51 is moved radially outward by the radial guide portions 44 and 45, so that the gear ratio γ is shifted toward the reduction side. Since the planetary ball 50 is sandwiched between the first rotating member 10, the second rotating member 20, and the sun roller 30, if it is a sphere, the center of gravity is centered when its tilting force is applied. Tilt.
In the continuously variable transmission 1, lubricating oil (so-called traction oil) is used for cooling each part (cooling object and lubrication object) and generating traction force. For example, the lubricating oil continues to be supplied from the oil pump 91 shown in FIG. The thick arrows shown in FIG. 1 represent the supply and discharge paths of the lubricating oil. At least one radial oil passage 62 is formed in the shaft 60, and lubricating oil in the axial center oil passage 61 is supplied from the radial oil passage 62 to each part of the continuously variable transmission 1. The radial oil passage 62 is an oil passage extending in the radial direction, and supplies the lubricating oil of the axial oil passage 61 from the radially inner side to the radially outer side into the casing CAt. . Therefore, the lubricating oil discharge hole in the radial oil passage 62 functions as a lubricating oil supply hole for supplying the lubricating oil into the casing CAt. For example, at least one radial oil passage 62 is formed on the shaft 60 on the reference plane (that is, radially inward of the sun roller 30). The radial oil passage 62 supplies the lubricating oil in the axial oil passage 61 to an annular gap S formed between the first rotating body 31 and the second rotating body 32. The gap S is preferably provided with a thickness in the axial direction so that the supplied lubricating oil can be stored.
Lubricating oil in the gap S is caused by an annular gap between the first rotating body 31 and the second rotating body 32 (hereinafter referred to as “annular oil”) due to the centrifugal force accompanying the rotation of the sun roller 30 and the pressure by the oil pump 91. It is referred to as a “path”.) 33 is discharged radially outward. The annular oil passage 33 is thinner in the axial direction than the gap S.
The lubricating oil discharged from the annular oil passage 33 hits the planetary ball 50 and is supplied between the sun roller 30 and the planetary ball 50 (particularly, the first and second contact portions P3 and P4). This lubricating oil mainly contributes to the cooling and lubrication of the sun roller 30 and the planetary ball 50 and the generation of traction force at the first and second contact portions P3 and P4.
Further, the lubricating oil discharged from the annular oil passage 33 flows radially outward from the gap between the adjacent planetary balls 50, and the first and second rotating members 10, 20 and the first output shaft 21. It is supplied to the inner peripheral surface of the cylindrical portion 21a. Between the first and second rotating members 10 and 20 and the planetary ball 50 (particularly the contact portions P1 and P2), the lubricant and the lubricant transmitted through the surface of the planetary ball 50 are supplied. These lubricating oils contribute to the cooling and lubrication of the first and second rotating members 10 and 20 and the generation of traction force at the contact portions P1 and P2. These lubricating oils are also supplied to the axial force generation units 71 and 72.
Lubricating oil in the casing CAt such as lubricating oil discharged from the annular oil passage 33 is stored in an annular state by centrifugal force on the radially outer side in the casing CAt during operation of the continuously variable transmission 1. The For example, in the continuously variable transmission 1, the amount of lubricating oil in the contact portions P <b> 1 and P <b> 2 is ensured while the annular lubricating oil hinders the rotating operation of the first rotating member 10 and the second rotating member 20. In order to prevent agitating resistance from occurring, the oil level of the annular lubricating oil should not be present radially inward of the contact portions P1 and P2 (that is, the oil surface is in the radial direction with the contact portions P1 and P2). The amount of lubricating oil in the casing CAt (that is, the relationship between the supply amount and the discharge amount) is adjusted so that it exists at the same position or radially outside the contact portions P1, P2. Therefore, in this continuously variable transmission 1, the lubricating oil may enter between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a of the output shaft 21, during which the lubricating oil If the oil enters, the lubricating oil becomes a factor of stirring resistance, which may hinder the rotation operation of the output shaft 21 and the second rotating member 20. In particular, conventionally, a through hole is formed in the first cylindrical portion 21a, and the lubricating oil easily flows between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a. Some are structured.
Therefore, the continuously variable transmission 1 is provided with at least one discharge hole 92 for discharging the lubricating oil in the casing out of the casing CAt. The discharge hole 92 is provided radially outside the above-described lubricating oil supply hole (that is, the discharge hole of the radial oil passage 62) , and when viewed in the axial direction, the planetary ball 50 and the first and second rotations. It is formed at a position intersecting the contact portions P1, P2 or the contact spare portion between the members 10 and 20 or radially outside the contact portions P1, P2 or the contact spare portion. In the illustrated output shaft 21, at least the first cylindrical portion is not provided with a through hole.
Specifically, the discharge hole 92 is a circular axial penetration provided in the side wall of either one of the casing CAt in the axial direction (one of the torque input side and the output side in the casing CAt). It is a hole.
In other words , in the continuously variable transmission 1, the peripheral edge of the pitch circle formed by the contact portions P1, P2 and the contact preliminary portion exists in the discharge hole 92 viewed in the axial direction, or the pitch circle The position of the discharge hole 92 is determined so that the discharge hole 92 when viewed in the axial direction is present on the outer side in the radial direction. When the peripheral edge of the pitch circle and the discharge hole 92 overlap, the lubricating oil supplied to the contact portions P1 and P2 can be discharged from the discharge hole 92 before being brought into an annular state by centrifugal force. Further, when the discharge hole 92 is provided on the radially outer side than the pitch circle, a part of the annular lubricating oil accumulated on the radially outer side in the casing CAt can be discharged from the discharge hole 92.
Further, when viewed in the axial direction, the discharge hole 92 may be formed at a position intersecting with a radially inner oil surface in the annular lubricating oil during operation or on a radially outer side than the oil surface. . That is, in the continuously variable transmission 1, the pitch diameter D2 at which the center of the discharge hole 92 is located and the diameter D3 of the discharge hole 92 are determined in accordance with the inner diameter D1 of the annular lubricating oil (FIGS. 5 and 6). ). The diameter D3 of the discharge hole 92 is an element related to the amount of lubricant discharged, and is further determined according to the amount of lubricant supplied into the housing CAt. The inner diameter D1 of the lubricating oil and the pitch diameter D2 of the discharge holes 92 are diameters centered on the first rotation center axis R1. Moreover, in FIG. 6, it has illustrated as what provides the two discharge holes 92. FIG.
Here, in the continuously variable transmission 1, the input shaft 11 and the output shaft 21 are arranged together on the torque input side. For this reason, the discharge hole 92 is formed on the side wall on the torque output side in the axial direction of the casing CAt.
Further, the continuously variable transmission 1 is provided with a guide portion that guides the lubricating oil in the casing CAt to the discharge hole 92. The illustrated guide portion guides a part of the annular lubricating oil accumulated outside in the radial direction in the housing CAt to the discharge hole 92. This guide portion is disposed close to the discharge hole 92 in the housing CAt. In this example, the annular member 22 is disposed near the discharge hole 92. Therefore, in the continuously variable transmission 1, the inner peripheral surface 22a of the annular member 22 is used as a guide surface for lubricating oil in the guide portion. In this continuously variable transmission 1, since a part of the annular lubricating oil is guided by the inner peripheral surface 22a, the oil surface of the annular lubricating oil should not be present radially outside the inner peripheral surface 22a. In other words, the amount of lubricating oil in the casing CAt is adjusted (that is, the oil surface is present at the same position in the radial direction as the inner peripheral surface 22a or on the inner side in the radial direction from the inner peripheral surface 22a). FIG. 5 illustrates a state where the oil surface and the inner peripheral surface 22a are flush with each other. Even in this case, the amount of the lubricating oil in the casing CAt is the same as the position of the annular lubricating oil surface in the radial direction with respect to the contact portions P1 and P2, or more radially than the contact portions P1 and P2. It is adjusted to exist outside.
Here, in the case where such a guide portion is provided, if the discharge hole 92 exists radially outside the oil surface of the annular lubricating oil during operation, the guide portion becomes an obstacle on the contrary. There is a possibility that a part of the lubricating oil cannot be guided to the discharge hole 92. Therefore, in this case, it is desirable that the discharge hole 92 is formed at a position that intersects the oil surface of the annular lubricating oil when viewed in the axial direction. In this case, the diameter D3 of the discharge hole 92 is formed to a size that satisfies the relationship "D3> | D1-D2 |".
The discharge hole 92 may be formed anywhere in the circumferential direction as long as the above conditions are satisfied.
In the continuously variable transmission 1 configured in this way, when the lubricating oil in the casing CAt is guided radially outward by centrifugal force during operation, a part of the lubricating oil in the annular state is obtained. It is discharged out of the housing CAt through the discharge hole 92. Therefore, in the continuously variable transmission 1, even if a centrifugal force acts on the annular lubricating oil, the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a of the output shaft 21 are not affected. The amount of lubricating oil flowing in between can be reduced as compared with the prior art. Therefore, in this continuously variable transmission 1, the stirring resistance of the output shaft 21 and the second rotating member 20 due to the lubricating oil can be reduced as compared with the conventional one, and the output shaft 21 and the second rotating member 20 can be smoothly rotated. Therefore, it is possible to suppress a decrease in power transmission efficiency. The effect of suppressing the reduction of the power transmission efficiency (that is, the effect of improving the power transmission efficiency) is substantially the same amount of suppression (improvement allowance) over the entire gear ratio γ. In the continuously variable transmission 1, the lubricating oil flows in through an annular gap g between the side wall surface of the casing CAt and the side wall surface of the annular member 22 facing each other.
Furthermore, in the continuously variable transmission 1, the casing CAt is expanded in the radial direction without increasing the distance between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a. The stirring resistance of the output shaft 21 and the like due to the lubricating oil can be reduced. For example, in order to widen the interval, it is necessary to expand the casing CAt outward in the radial direction. This is also apparent from Equation 1 below. Therefore, the continuously variable transmission 1 can suppress a decrease in power transmission efficiency without increasing the physique in the radial direction. Therefore, this continuously variable transmission 1 can also improve the mountability to a vehicle and suppress cost increase. In addition, “M” in the formula 1 indicates the magnitude of the stirring resistance. “R1” indicates the radius of the inner peripheral surface of the casing CAt, and “R2” indicates the radius of the outer peripheral surface of the first cylindrical portion 21a. “Μ” indicates the viscosity of the lubricating oil. “Ω” indicates the angular velocity of the output shaft 21, and “Lout” indicates the length of the first cylindrical portion 21 a in the axial direction.
By the way, this illustrated continuously variable transmission 1 is provided with a transmission gear 81 outside the torque output side of the casing CAt. Therefore, here, the lubricating oil discharged from the discharge hole 92 is used for cooling and lubricating the transmission gear 81. For this purpose, the discharge hole 92 is opened in the transmission gear chamber 82. Further, it is desirable that the discharge hole 92 is disposed above the transmission gear 81 in a state of being mounted on the vehicle. The discharge hole 92 may be provided on the side of the gear if the lubricating oil can be supplied to the tooth surface of the uppermost gear when the transmission gear 81 is mounted on the vehicle.
The lubricating oil used for cooling and lubricating the transmission gear 81 is guided to the lower part of the transmission gear chamber 82 by gravity. The casing CAg has a discharge hole 93 formed in the lower part when the vehicle is mounted (FIG. 1). Further, the discharge hole 93 is connected to the reserve tank 94 through an oil passage. Accordingly, the lubricating oil in the transmission gear chamber 82 is discharged out of the transmission gear chamber 82 through the discharge hole 93 and sent to the reserve tank 94. The lubricating oil in the reserve tank 94 is supplied again into the housing CAt by the oil pump 91.
In the continuously variable transmission 1, a lubricating oil discharge hole 95 is also formed in a lower portion of the casing CAt when the vehicle is mounted. The discharge hole 95 is communicated between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a of the output shaft 21. The discharge hole 95 is connected to the reserve tank 94 via an oil passage. For this reason, the lubricating oil that has entered between them is sent from the discharge hole 95 to the reserve tank 94. Therefore, the continuously variable transmission 1 can reduce the lubricating oil in the meantime through the discharge hole 95, and therefore can further reduce the stirring resistance of the output shaft 21 and the second rotating member 20 due to the lubricating oil, resulting in a decrease in power transmission efficiency. Can be further suppressed.
As described above, the continuously variable transmission 1 reduces the inflow of lubricating oil between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a of the output shaft 21 to transmit power. A decrease in efficiency can be suppressed. However, in order to suppress a decrease in power transmission efficiency, it is most desirable not to generate the stirring resistance of the output shaft 21 and the second rotating member 20 due to the lubricating oil in the meantime. Therefore, in the continuously variable transmission 1, the amount of lubricating oil flowing in between is reduced as much as possible.
Specifically, the inflow of the lubricating oil from the gap g is suppressed by narrowing the gap L (FIG. 5) of the gap g as a place where the lubricating oil flows into the gap as much as possible. Narrowing as much as possible in terms of structure means that the clearance L after considering the stacking tolerance based on the maximum dimensional tolerance of various components, the maximum assembly tolerance of various components, and the amount of deviation due to deflection of various components during operation. The output shaft 21 (mainly the annular member 22) is shrunk to the minimum value that does not come into contact with the casing CAt regardless of the stationary state or the operating state. As a result, the continuously variable transmission 1 can reduce the inflow amount of the lubricating oil entering between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first cylindrical portion 21a of the output shaft 21 as much as possible. Further, it is possible to suppress the generation of the stirring resistance of the output shaft 21 and the second rotating member 20 due to the lubricating oil in the meantime. In addition, even if the lubricating oil flows in the meantime, the infinitely variable transmission 1 has a small amount of inflow, and in combination with the draining effect of the lubricating oil by the lower discharge hole 95 described above, Generation | occurrence | production of the stirring resistance of the output shaft 21 grade | etc., By lubricating oil can be suppressed. Therefore, in the continuously variable transmission 1, it is possible to greatly suppress a decrease in power transmission efficiency due to such a stirring resistance.
In the above-described embodiment, the discharge hole 92 that connects the inside of the casing CAt and the transmission gear chamber 82 is a round hole. In this modification, in the continuously variable transmission 1 of the above-described embodiment, the discharge hole 92 is replaced with a discharge hole 96 formed by a long hole in the circumferential direction (FIG. 7). The discharge hole 96 is provided on one of the side walls in the axial direction of the housing CAt.
If the above-described guide portion (the inner peripheral surface 22a of the annular member 22) of the lubricating oil is not provided, the discharge hole 96 has a radially inner side in the annular lubricating oil during operation when viewed in the axial direction. It forms in the position which cross | intersects the oil level, or the radial direction outer side than the said oil level. On the other hand, if such a guide portion is provided, the discharge hole 96 is formed at a position intersecting with the oil surface of the annular lubricating oil when viewed in the axial direction. Therefore, also in this modification, the continuously variable transmission 1 can obtain the same effect as that of the embodiment.
In the embodiment described above, the input shaft 11 and the output shaft 21 are extended together on either the torque input side or the output side. The continuously variable transmission 100 of this modification is obtained by replacing the input shaft 11 and the output shaft 21 with an input shaft 111 and an output shaft 121, respectively, as shown in FIG. 8 in the continuously variable transmission 1 of the embodiment. . In FIG. 8, the transmission gear 81 and the like are not shown. For example, the transmission gear 81 and the like in this case are arranged in the housing CAt.
In the continuously variable transmission 100, the input shaft 111 extends to the torque input side, and the output shaft 121 extends to the torque output side. The input shaft 111 is equivalent to the input shaft 11 of the embodiment, and a disk portion 111a in which the first rotating member 10 is connected to an outer edge portion via an axial force generating portion 71, and the diameter of the disk portion 111a. A cylindrical portion 111b extending from the inner side portion toward the torque input side. On the other hand, the output shaft 121 includes a disk portion 121a and a cylindrical portion 121b equivalent to the input shaft 111, and has a shape facing each other in the axial direction with the reference plane as a boundary. The second rotating member 20 is connected to the outer edge portion of the disk portion 121a via the axial force generating portion 72. The disk portion 121 a covers the second and third disk members 42 and 43 of the carrier 40 together with the second rotating member 20. The cylindrical portion 121b extends from the radially inner portion of the disk portion 121a toward the torque output side.
In this continuously variable transmission 100, the cylindrical portion 111b of the input shaft 111 protrudes from the casing CAt in the torque input side while maintaining the sealed state of the casing CAt. Is projected from the casing CAt toward the torque output side while the casing CAt is kept sealed.
In the continuously variable transmission 100, the lubricating oil in the casing CAt such as the lubricating oil discharged from the annular oil passage 33 is sent radially outward by the centrifugal force during operation, and the first rotating member 10 and the second rotating member 10. From the space between the rotating member 20 and the inner peripheral surface of the casing CAt, an annular lubricating oil is formed. In the continuously variable transmission 100, between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first rotating member 10, and between the inner peripheral surface of the casing CAt and the outer peripheral surface of the second rotating member 20. If the lubricating oil flows into the oil, the lubricating oil in the meantime may cause a stirring resistance, which may hinder the rotational operation of the first rotating member 10 and the second rotating member 20.
Therefore, the continuously variable transmission 100 is provided with at least one discharge hole 192, 193 for the in-chamber lubricating oil for discharging a part of the annular lubricating oil to the outside of the casing CAt. The discharge holes 192 and 193 are provided on at least one of the torque input side and the output side. In the example of FIG. 8, discharge holes 192 and 193 are provided on both the torque input side and the output side.
The discharge hole 192 is formed as a through hole in the axial direction on the side wall of the housing CAt. On the other hand, the discharge hole 193 on the torque input side is formed as a through hole in the axial direction in the disk portion 111a. Further, the torque output side discharge hole 193 is formed as a through hole in the axial direction in the disk portion 121a. The discharge holes 192 and 193 may be round holes or long holes such as the discharge hole 92 of the embodiment or the discharge hole 96 of the first modification, and may have any shape. For example, when viewed in the axial direction, the discharge holes 192 and 193 are formed at positions intersecting with the oil surface on the radially inner side in the annular lubricating oil during operation or on the radially outer side with respect to the oil surface. Accordingly, a part of the annular lubricating oil during operation is discharged out of the casing CAt through the discharge holes 192 and 193. The discharged lubricating oil is sent to the reserve tank 94.
Here, in the continuously variable transmission 100, the disk portions 111a and 121a rotate relative to the casing CAt in the circumferential direction. Therefore, it is desirable to provide a plurality of discharge holes 192 and 193 in the circumferential direction in order to improve the discharge property of the lubricating oil to the outside of the casing CAt.
As described above, in the continuously variable transmission 100, when the lubricating oil in the casing CAt is guided radially outward by the centrifugal force during operation, a part of the lubricating oil in the annular state is obtained. It is discharged out of the casing CAt through the discharge holes 192 and 193. Therefore, in this continuously variable transmission 100, even if centrifugal force acts on the annular lubricating oil, the space between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first rotating member 10 and the casing CAt. The amount of lubricating oil flowing into the space between the inner peripheral surface of the second rotating member 20 and the outer peripheral surface of the second rotating member 20 can be reduced as compared with the conventional art. Therefore, in this continuously variable transmission 100, the agitation resistance of the first rotating member 10 and the second rotating member 20 due to lubricating oil can be reduced as compared with the prior art, and the first rotating member 10 and the second rotating member 20 can be made smoother. Since it can be rotated, the fall of power transmission efficiency can be suppressed.
Further, in the continuously variable transmission 100, the distance between the inner peripheral surface of the casing CAt and the outer peripheral surface of the first rotating member 10, and the distance between the inner peripheral surface of the casing CAt and the outer peripheral surface of the second rotating member 20 are included. Even if it does not spread, stirring resistance of the 1st rotation member 10 grade by the lubricating oil between these can be reduced. Therefore, the continuously variable transmission 100 can suppress a decrease in power transmission efficiency without increasing the physique in the radial direction. Therefore, also for this continuously variable transmission 100, it is possible to improve the mountability to the vehicle and to suppress the increase in cost.
By the way, in the above-described embodiment and the first modification, the round hole discharge hole 92 and the long hole discharge hole 96 are illustrated, but the discharge hole for communicating the inside of the housing CAt with the transmission gear chamber 82 is provided by these. It may be of any shape other than.
1,100 continuously variable transmission 10 first rotating member (first power transmission element)
DESCRIPTION OF SYMBOLS 11 Input shaft 11a Disk part 11b Cylindrical part 20 2nd rotation member (2nd power transmission element)
21 output shaft 21a first cylindrical part 21b disk part 21c second cylindrical part 22 annular member 22a inner peripheral surface (guide surface of guide part)
30 Sun Roller (third power transmission element)
33 annular oil passage 40 carrier (fourth power transmission element, fixed element)
50 Planetary ball (rolling member)
60 shaft (transmission shaft)
61 Axial oil passage 62 Radial oil passage 71, 72 Axial force generating portion 81 Transmission gear 82 Transmission gear chamber 91 Oil pump 92, 93, 95, 96 Discharge hole 94 Reserve tank 111 Input shaft 111a Disk portion 111b Cylindrical portion 121 Output shaft 121a Disc part 121b Cylindrical part 192, 193 Discharge hole CAg, CAt Housing g Gap P1, P2 Contact part R1 First rotation central axis R2 Second rotation central axis S Gap
A transmission shaft as a center of rotation;
First to fourth power transmission elements capable of relative rotation in the circumferential direction between each other having a first rotation center axis concentric with the transmission shaft;
A plurality of first and second rotating shafts having a second rotation center axis and arranged radially on the outer peripheral surface of the third power transmission element, with the first rotation center axis being opposed to each other. A rolling member sandwiched between power transmission elements and tiltably held by the fourth power transmission element;
A transmission that changes the speed ratio between the input and output by tilting each rolling member;
A housing for housing the transmission shaft, the first to fourth power transmission elements, and the rolling member;
A lubricating oil supply hole for supplying lubricating oil into the housing from the radially inner side toward the radially outer side;
The casing discharges the lubricating oil in the casing to the outside of the casing on at least one side wall of the casing in the axial direction of the transmission shaft and radially outside the lubricating oil supply hole. a discharge hole for,
When the discharge hole is viewed in the axial direction, the discharge hole intersects the contact portion or the contact preliminary portion between the rolling member and the first and second power transmission elements, or the contact portion or the contact. Forming radially outside the spare part,
A continuously variable transmission characterized by that.
A concentric first rotating shaft connected to the first power transmission element and a concentric second rotating shaft connected to the second power transmission element extend to one of the side walls in the axial direction of the housing. 2. The continuously variable transmission according to claim 1 , wherein, when being present, the discharge hole is provided in the other side wall in the axial direction of the housing .
The continuously variable transmission according to claim 1 or 2, wherein a guide portion for guiding the lubricating oil in the housing to the discharge hole is provided in the housing.
When the lubricating oil in the casing is in an annular state on the radially outer side in the casing due to centrifugal force during operation, the discharge hole is a radial direction in the annular lubricating oil when viewed in the axial direction. 4. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is formed at a position intersecting with an inner oil surface or radially outside the oil surface .
When the lubricating oil in the casing is in an annular state on the radially outer side in the casing due to centrifugal force during operation, and the oil surfaces on the radially inner side of the lubricating oil in the annular state are the first and first 2 in the radial direction from the respective contact portions between the power transmission element and each of the rolling members to the guide surface of the lubricating oil in the guide portion, the discharge hole extends in the axial direction. 4. The continuously variable transmission according to claim 3, wherein the continuously variable transmission is formed at a position intersecting with the oil level when viewed.
The continuously variable transmission according to any one of claims 1 to 5, wherein the discharge hole communicates the inside of the housing with a transmission gear chamber in which a transmission gear of the transmission is accommodated. .
JP2012241120A 2012-10-31 2012-10-31 Continuously variable transmission Active JP5590098B2 (en)
JP2012241120A JP5590098B2 (en) 2012-10-31 2012-10-31 Continuously variable transmission
US14/437,945 US9388896B2 (en) 2012-10-31 2013-09-24 Continuously variable transmission
PCT/JP2013/075772 WO2014069125A1 (en) 2012-10-31 2013-09-24 Stepless transmission
CN201380055451.9A CN104736893B (en) 2012-10-31 2013-09-24 Buncher
BR112015009135A BR112015009135A2 (en) 2012-10-31 2013-09-24 Continuously variable transmission
EP13851194.4A EP2916040A4 (en) 2012-10-31 2013-09-24 Stepless transmission
JP2014092175A JP2014092175A (en) 2014-05-19
JP5590098B2 true JP5590098B2 (en) 2014-09-17
ID=50627041
JP2012241120A Active JP5590098B2 (en) 2012-10-31 2012-10-31 Continuously variable transmission
US (1) US9388896B2 (en)
EP (1) EP2916040A4 (en)
JP (1) JP5590098B2 (en)
CN (1) CN104736893B (en)
BR (1) BR112015009135A2 (en)
WO (1) WO2014069125A1 (en)
JPS6350583B2 (en) * 1980-03-12 1988-10-11 Toyoda Machine Works Ltd
JPH10318357A (en) * 1997-05-16 1998-12-04 Jatco Corp Lubricating structure for transmission
DE19935959A1 (en) * 1999-07-30 2001-02-01 Zahnradfabrik Friedrichshafen Planet gearing with lubricating system varies lubricant level as function of planet stage speed via housing opening to return less oil than flung off gear assisted by passivating space in return.
JP4514044B2 (en) * 2005-02-15 2010-07-28 本田技研工業株式会社 Lubricating structure of hydrostatic continuously variable transmission
WO2012053366A1 (en) * 2010-10-19 2012-04-26 Ntn株式会社 Roller bearing
2012-10-31 JP JP2012241120A patent/JP5590098B2/en active Active
2013-09-24 BR BR112015009135A patent/BR112015009135A2/en active Search and Examination
2013-09-24 CN CN201380055451.9A patent/CN104736893B/en active IP Right Grant
2013-09-24 US US14/437,945 patent/US9388896B2/en active Active
2013-09-24 EP EP13851194.4A patent/EP2916040A4/en active Pending
2013-09-24 WO PCT/JP2013/075772 patent/WO2014069125A1/en active Application Filing
CN104736893A (en) 2015-06-24
EP2916040A1 (en) 2015-09-09
US9388896B2 (en) 2016-07-12
WO2014069125A1 (en) 2014-05-08
BR112015009135A2 (en) 2017-07-04
CN104736893B (en) 2017-04-05
EP2916040A4 (en) 2016-08-31
JP2014092175A (en) 2014-05-19
US20150323058A1 (en) 2015-11-12
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