JP2018031434A - Oil supply structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply structure which can supply oil to a spline connection portion without using an axial core oil passage which is formed at a rotating shaft coaxially therewith.SOLUTION: A lubricant supply oil passage 72 is formed in a position at a right side of a portion in which an outer spline 34 of a primary shaft 13 and an inner spline 45 of a gear 14 are engaged with each other, that is, a spline connection portion 71 in which the spline connection of the primary shaft 13 and the gear 14 is formed, and oil is supplied toward the spline connection portion 71 from the lubricant supply oil passage 72. Furthermore, a receiver 73 is arranged between the spline connection portion 71 and the lubricant supply oil passage 72. A weir part 75 extending to a rotation radial direction from an internal peripheral face of a boss 41 of the gear 14 is formed at the receiver 73.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a structure that is applied to a transmission or the like mounted on a vehicle and supplies oil to a portion where spline coupling is configured.

  In a vehicle such as an automobile, for example, a driving force from an engine is input to a transmission, and the driving force shifted by the transmission is transmitted to driving wheels via a differential.

  In a transmission, spline coupling is employed at many locations to couple two members so that they cannot rotate relative to each other. For example, in a belt-type continuously variable transmission (CVT), a spline connection is employed to connect a gear to a rotation shaft (for example, an output shaft) so as not to be relatively rotatable. Specifically, splines are formed on the outer peripheral surface of the rotating shaft and the inner peripheral surface of the gear, respectively, and the output gear is fitted on the portion where the spline of the rotating shaft is formed, and the spline of the gear rotates. By meshing with the spline of the shaft, the rotating shaft and the gear are spline-coupled so as not to rotate relative to each other.

  It is desirable to supply oil for lubrication (lubricating oil) to the portion where the spline of the rotating shaft and the spline of the gear mesh with each other, that is, the spline coupling portion constituting the spline coupling. In order to supply oil to the spline coupling portion, the rotation shaft is formed with a shaft oil passage extending on the shaft center and a supply oil passage communicating with the shaft oil passage. The supply oil passage is opened at the outer peripheral surface of the rotating shaft at a position facing the spline coupling portion. Thereby, oil can be supplied to the spline coupling portion from the shaft center oil passage through the supply oil passage, and the spline coupling portion can be lubricated with oil.

Japanese Patent Laying-Open No. 2015-145682

  However, in such a configuration, since it is necessary to use the shaft center oil passage for supplying oil to the spline coupling portion and to form the shaft center oil passage in the shaft center of the rotating shaft, the manufacturing cost increases. Also, if a clutch, primary pulley or secondary pulley sheave is installed around the rotating shaft, the center oil passage cannot be used to supply hydraulic pressure to the clutch or sheave, so supply hydraulic pressure to the clutch or sheave. The structure for doing so becomes complicated, and the manufacturing cost further increases.

  The objective of this invention is providing the oil supply structure which can supply oil to a spline coupling | bond part, without using the shaft center oil path formed in the shaft center of a rotating shaft.

  In order to achieve the above-mentioned object, the oil supply structure according to the present invention is configured such that the rotating shaft and the outer fitting member fitted on the rotating shaft are spline-coupled, and the oil is supplied to the spline coupling portion that constitutes the spline coupling. An oil supply path that is provided on one side in the rotation axis direction with respect to the spline coupling portion, and that supplies oil from the rotation axis direction toward the spline coupling portion, and the spline coupling portion and the oil supply path. And a receiver having a portion extending in the radial direction from the outer fitting member.

  According to this configuration, the oil is supplied from the oil supply path provided on one side in the rotation axis direction with respect to the spline coupling portion toward the spline coupling portion between the rotation shaft and the external fitting member. Therefore, oil can be supplied to the spline coupling portion without using the shaft center oil passage formed in the shaft center of the rotating shaft. Therefore, it is not necessary to form an axial oil passage in the axial center of the rotating shaft in order to supply oil to the spline coupling portion. Therefore, the manufacturing cost regarding the structure for supplying oil to the spline coupling portion can be reduced.

  When a mechanism including a hydraulically movable member (such as a piston) such as a clutch or a belt-type continuously variable transmission pulley is provided around the rotary shaft, the shaft center of the rotary shaft is used to supply hydraulic pressure to the movable member. An axial oil passage formed in the above can be used. As a result, the structure for supplying hydraulic pressure to the movable member can be simplified, and as a result, the manufacturing cost relating to the mechanism including the movable member can be reduced.

  Further, a receiver is provided between the spline coupling portion and the oil supply path, and a portion extending in the rotational radial direction from the outer fitting member is formed on the receiver. Therefore, when centrifugal force due to the rotation of the rotating shaft and the external fitting member acts on the oil supplied to the spline coupling portion, the portion extending in the rotational radial direction of the receiver becomes an oil weir that escapes (blows off) from the spline coupling portion. , Oil can be prevented from escaping from the spline connecting portion. Therefore, a good lubrication state of the spline coupling portion can be maintained.

  In addition, since the receiver is provided, the oil is stored in the lower end of the spline coupling portion while the rotating shaft and the external fitting member are stopped. Therefore, immediately after the rotation of the rotating shaft and the external fitting member, the stored oil can be spread to the spline coupling portion by centrifugal force, and the spline coupling portion can be lubricated with oil.

  Further, depending on the shape of the receiver, at the start of oil supply from the oil supply path, the oil supplied from the oil supply path toward the spline coupling part can be divided into the spline coupling part and the outside of the outer fitting member. . As a result, oil can be supplied also to the member disposed outside the outer fitting member, and the member can be lubricated with oil.

  The outer fitting member may be held by a member (such as a case) provided so as not to rotate via a bearing. In this case, a part of the oil supplied from the oil supply path toward the spline coupling portion can be supplied to the bearing, and the bearing can be lubricated with oil.

  According to the present invention, the oil can be supplied to the spline coupling portion without using the shaft oil passage formed in the shaft center of the rotating shaft. Cost can be reduced.

It is sectional drawing which shows a part of continuously variable transmission 1 to which the oil supply structure which concerns on one Embodiment of this invention was applied.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

<Main part configuration>
FIG. 1 is a cross-sectional view showing a part of a continuously variable transmission 1 to which an oil supply structure according to an embodiment of the present invention is applied. In FIG. 1, the hatching indicating the cross section is omitted.

  A belt-type continuously variable transmission (CVT) 1 is an example of a vehicle transmission, and is an endless belt between a primary pulley 11 on an input side and a secondary pulley (not shown) on an output side. 12 is wound around. The continuously variable transmission 1 is provided with a primary shaft 13 that supports the primary pulley 11, a gear 14 that transmits power input from a drive source such as a vehicle engine to the primary shaft 13, and the like.

  The primary pulley 11 includes a fixed sheave 21, a movable sheave 22, and a cylinder 23.

  The fixed sheave 21 has a hook shape projecting in the rotational radial direction from the central portion of the primary shaft 13 in the rotational axis direction, and is formed integrally with the primary shaft 13.

  The movable sheave 22 is provided on one side (left side in FIG. 1, hereinafter referred to as “left side”) with the belt 12 sandwiched between the fixed sheave 21. The movable sheave 22 is externally fitted to the primary shaft 13, and has a substantially cylindrical outer fitting portion 24 that is spline-coupled to the primary shaft 13 so as to be movable in the rotational axis direction and not to be relatively rotatable, and fixing of the outer fitting portion 24. A sheave body 25 that projects from the end on the sheave 21 side (right side in FIG. 1, hereinafter referred to as “right side”) in the radial direction is integrally formed. The belt 12 is sandwiched between the fixed sheave 21 and the sheave body 25 of the movable sheave 22.

  The cylinder 23 is fitted on the left end portion of the primary shaft 13 and is located on the left side with respect to the movable sheave 22. The cylinder 23 is integrally formed with a plate-like plate-like portion 26 extending in the rotational radial direction and a substantially cylindrical cylindrical portion 27 extending rightward from the outer peripheral end of the plate-like portion 26. The outer peripheral end of the movable sheave 22 is in liquid-tight contact with the inner peripheral surface of the cylindrical portion 27, and a piston chamber (hydraulic chamber) 28 is formed between the movable sheave 22 and the cylinder 23. .

  The left end portion of the primary shaft 13 is formed with a smaller diameter than the portion where the outer fitting portion 24 of the movable sheave 22 is fitted. Thereby, a step is generated on the outer peripheral surface of the primary shaft 13 between a portion where the outer fitting portion 24 of the movable sheave 22 is fitted and a left end portion (portion where the cylinder 23 is fitted). .

  A substantially annular plate-like stopper 32 is interposed between the surface 31 formed by the step and the plate-like portion 26 of the cylinder 23.

  On the outer peripheral surface of the primary shaft 13, a screw is cut on the left side of the portion where the plate-like portion 26 of the cylinder 23 is fitted. A lock nut 33 is screwed into the threaded portion. By tightening the lock nut 33, the plate-like portion 26 and the stopper 32 of the cylinder 23 are pressed against each other between the surface 31 and the lock nut 33, and the cylinder 23 and the stopper 32 are fixed to the primary shaft 13.

  The right end portion of the primary shaft 13 is formed with a smaller diameter than the portion between the right end portion and the fixed sheave 21. An outer spline 34 is formed on the outer peripheral surface of the right end portion formed in this small diameter.

  The gear 14 has a substantially cylindrical shape that surrounds the outer periphery of the web 42, a boss 41 that is formed in a substantially cylindrical shape, a web 42 that is formed in a substantially annular plate shape that extends in the rotational radial direction from the left end of the boss 41. A rim 44 having a large number of gear teeth 43 formed on the outer peripheral surface is integrally provided.

  An inner spline 45 corresponding to the outer spline 34 at the right end of the primary shaft 13 is formed on the inner peripheral surface of the boss 41. The right end portion of the primary shaft 13 is inserted into the boss 41, and the outer spline 34 of the primary shaft 13 and the inner spline 45 of the boss 41 are engaged with each other, whereby the primary shaft 13 and the gear 14 are spline-coupled.

  A cylindrical surface 51 is formed on the plate-like portion 26 of the cylinder 23 and has a cylindrical shape centering on the rotation axis of the primary shaft 13 and facing outward in the rotational radial direction. An inner ring (inner race) 53 of a bearing 52 is fitted on the cylindrical surface 51. An outer ring (outer race) 54 of the bearing 52 is held by a case 55 of the continuously variable transmission 1. Further, an inner ring 57 of a bearing 56 is fitted on the right end portion of the boss 41 of the gear 14. An outer ring 58 of the bearing 56 is held by the case 55. Thus, the primary shaft 13 and the gear 14 are supported by the case 55 via the two bearings 52 and 56.

  The primary shaft 13 is formed with an axial oil passage 61 extending on the rotation axis and a communication oil passage 62 extending between the axial oil passage 61 and the outer peripheral surface of the primary shaft 13. The shaft center oil passage 61 communicates with the piston chamber 28 of the primary pulley 11 via the communication oil passage 62. The shaft center oil passage 61 is opened at the right end surface of the primary shaft 13.

  In the case 55, a cylindrical projecting portion 63 centering on the rotation axis of the primary shaft 13 is formed to project to the left at a portion facing the primary shaft 13 from the right side. The tip of the protrusion 63 enters the inside of the right end of the primary shaft 13 and is connected to the primary shaft 13 via a substantially cylindrical plug 64. Inside the protrusion 63 is a sheave hydraulic supply oil passage 65, and oil (operating oil) for moving the movable sheave 22 is supplied from the valve body (not shown) to the sheave hydraulic supply oil passage 65. . The sheave hydraulic supply oil passage 65 communicates with the shaft center oil passage 61 via the plug 64, and the oil supplied to the sheave hydraulic supply oil passage 65 flows into the shaft center oil passage 61 through the plug 64, and the shaft It flows into the piston chamber 28 of the primary pulley 11 from the core oil passage 61 through the communication oil passage 62.

  Further, the case 55 has a position shifted in the radial direction of the primary shaft 13 and the gear 14 with respect to the protruding portion 63 (sheave hydraulic pressure oil passage 65), specifically, the outer spline 34 of the primary shaft 13 and the gear. A lubricating oil supply oil passage 72 is formed at a position on the right side of a spline coupling portion 71 in which a spline coupling between the primary shaft 13 and the gear 14 is formed. Oil (lubricating oil) for lubricating each part is supplied from the valve body to the lubricating oil supply oil path 72. The lubricating oil supply oil passage 72 is opened at the inner surface of the case 55, and the oil supplied from the valve body to the lubricating oil supply oil passage 72 is directed from the open end of the lubricating oil supply oil passage 72 toward the spline coupling portion 71. Discharged.

  A receiver 73 is interposed between the spline coupling portion 71 and the open end of the lubricating oil supply oil passage 72. The receiver 73 is press-fitted into the right end portion of the boss 41 of the gear 14 and is held by the boss 41. The receiver 73 integrally has a cylindrical pressure contact portion 74 that is in pressure contact with the inner peripheral surface of the boss 41, and a weir portion 75 that extends from the left end of the pressure contact portion 74 toward the rotation axis of the gear 14 in the rotation radial direction. ing. The dam portion 75 faces the spline coupling portion 71 with a space from the right side in the rotation axis direction, and a gap is generated between the spline coupling portion 71 and the dam portion 75.

<Effect>
According to the above configuration, the oil is supplied from the lubricating oil supply oil passage 72 provided on the right side in the rotation axis direction toward the spline coupling portion 71 between the primary shaft 13 and the gear 14. Therefore, the oil can be supplied to the spline coupling portion 71 without using the shaft center oil passage formed in the shaft center of the primary shaft 13. Therefore, oil can be supplied to the spline coupling portion 71 with a simple configuration, and the manufacturing cost relating to the structure for supplying oil to the spline coupling portion 71 can be reduced.

  Further, in order to supply oil (hydraulic pressure) to the piston chamber 28 of the primary pulley 11, the shaft center oil passage 61 formed in the shaft center of the primary shaft 13 can be used. As a result, it is possible to simplify the structure for supplying the oil to the piston chamber 28, and to reduce the manufacturing cost related to the continuously variable transmission 1.

  A receiver 73 is provided between the spline coupling portion 71 and the lubricating oil supply oil passage 72. The receiver 73 is formed with a weir 75 extending in the radial direction from the inner peripheral surface of the boss 41 of the gear 14. Therefore, when the centrifugal force due to the rotation of the primary shaft 13 and the gear 14 acts on the oil supplied to the spline coupling portion 71, the weir portion 75 of the receiver 73 becomes a dam for oil that comes off (sprays) from the spline coupling portion 71. Further, it is possible to suppress oil from escaping from the spline coupling portion 71. Therefore, a good lubrication state of the spline coupling portion 71 can be maintained.

  In addition, since the receiver 73 is provided, oil is stored in the lower end of the spline coupling portion 71 while the primary shaft 13 and the gear 14 are stopped. Therefore, immediately after the rotation of the primary shaft 13 and the gear 14 is started, the stored oil can be distributed to the spline coupling portion 71 by centrifugal force, and the spline coupling portion 71 can be lubricated with oil.

  Further, at the start of oil supply from the lubricating oil supply oil passage 72, the oil supplied from the lubricating oil supply oil passage 72 toward the spline coupling portion 71 hits the dam portion 75 of the receiver 73, and exceeds the dam portion 75, A flow of oil supplied to the spline coupling portion 71 from between the weir portion 75 and the right end surface of the primary shaft 13 and a pressure contact portion 74 from the weir portion 75 to the bearing 56 provided outside the gear 14. Oil flow is produced. As a result, not only the spline coupling portion 71 but also the bearing 56 can be supplied with oil, and the bearing 56 can be lubricated with oil.

<Modification>
As mentioned above, although one Embodiment of this invention was described, this invention can also be implemented with another form.

  For example, in the above-described embodiment, the structure for supplying oil to the spline coupling portion 71 between the primary shaft 13 and the gear 14 is taken up. However, the present invention is not limited to the primary shaft 13 provided in the continuously variable transmission 1. Spline coupling portion between the rotating shaft and an external fitting member such as a gear fitted on the rotating shaft, for example, a spline coupling portion or output between the secondary shaft supporting the secondary pulley and the clutch piston fitted on the secondary shaft The present invention can also be applied to a structure that supplies oil to a spline coupling portion between the shaft and an output gear that is externally fitted to the output shaft.

  In addition, various design changes can be made to the above-described configuration within the scope of the matters described in the claims.

13: Primary shaft (rotating shaft)
14: Gear (external fitting member)
34: Outer spline 45: Inner spline 71: Spline coupling part 72: Lubricating oil supply oil path 73: Receiver 75: Weir part (part extending in the radial direction)

Claims (1)

A structure in which a rotating shaft and an outer fitting member that is externally fitted to the rotating shaft are spline-coupled, and oil is supplied to a spline coupling portion that constitutes the spline coupling,
An oil supply path that is provided on one side in the rotation axis direction with respect to the spline coupling portion, and that supplies oil from the rotation axis direction toward the spline coupling portion;
An oil supply structure including a receiver that is provided between the spline coupling portion and the oil supply passage and has a portion extending in a rotational radial direction from the outer fitting member.

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