JP6618959B2 - Oil supply structure - Google Patents

Description

  The present invention relates to an oil supply structure for supplying oil for lubrication to a clutch or the like disposed on the outer periphery of a rotating body.

  As an automatic transmission mounted on a vehicle, a continuously variable transmission (CVT), a stepped automatic transmission (AT), and the like are widely known.

  In an automatic transmission, a clutch for connecting a rotating element and another rotating element, a brake for braking the rotating element, a bearing, and the like are often used. There are also many parts where the gears mesh with each other and where the two members are splined together. In each of these parts, friction between members occurs, and therefore it is indispensable to supply oil for lubrication.

  For example, in order to supply oil to each part on the outer periphery of the rotating shaft (rotating body), the rotating shaft is formed with an axial oil passage extending on the axial center and a supply oil passage communicating with the axial oil passage. . The supply oil path is open at the peripheral surface of the rotating shaft, and the oil flowing through the shaft center oil path is discharged to the outer periphery of the rotating shaft through the supply oil path. As a result, oil flows from the rotary shaft to the outside in the radial direction, and the oil is supplied to each part on the outer periphery of the rotary shaft. As a result, it is possible to prevent the occurrence of wear and seizure at each part on the outer periphery of the rotating shaft.

Japanese Patent Laying-Open No. 2015-145682

  In an example of the conventional structure, the rotating shaft is rotatably supported by an annular member that surrounds the rotating shaft via a bearing. When a needle bearing having a configuration in which needle rollers are rotatably arranged in a circumferential direction on a cylindrical cage is adopted as the bearing, the bearing is in the direction of the rotation axis between the rotation shaft and the annular member. Not fixed to. Therefore, depending on the position of the bearing, the oil flow from the supply oil passage toward the outside of the annular member is blocked by the bearing, and there is a concern that a problem due to insufficient lubrication may occur in a portion where the oil is not sufficiently supplied. Further, since the oil flow toward the outside of the annular member is interrupted, there is a concern that the amount of oil flowing through another path increases and an oil supply portion becomes excessive. When oil is excessively supplied to the clutch and brake, drag loss due to shear resistance that the disk receives from the oil increases.

  The objective of this invention is providing the oil supply structure which can suppress that the flow of the oil which goes to the outer side of an annular member is interrupted | blocked by a movable member irrespective of the position of a movable member.

  In order to achieve the above object, an oil supply structure according to the present invention surrounds a rotating body having a cylindrical outer peripheral surface, and is concentric with the outer peripheral surface of the rotating body spaced apart from each other. An annular member having an inner peripheral surface, a movable member interposed between the outer peripheral surface of the rotating body and the inner peripheral surface of the annular member, and provided so as to be movable in the rotational axis direction of the rotating body, the annular member and the rotating axis And an opposed wall facing each other with a gap in the direction, and an oil passage through which oil flows is formed in the rotating body, and the oil path is located between the annular member and the facing wall on the outer peripheral surface of the rotating body. The movable member is opened at a position facing the rotational radial direction of the rotating body, and the movable member is formed with communication grooves that are opened at both ends in the rotational radial direction at least at the end on the opposite wall side.

  According to this structure, the annular member is provided on the outer periphery of the rotating body, and the outer peripheral surface of the rotating body and the inner peripheral surface of the annular member form a concentric cylinder centered on the rotation axis of the rotating body. Yes. An oil passage through which oil flows is formed in the rotating body. The oil passage is opened on the outer peripheral surface of the rotating body at a position facing the rotation radial direction (a position facing the annular member) and an opposing wall facing the annular member from the rotation axis direction. Therefore, the oil flowing through the oil passage is discharged from the open end of the oil passage to the outer periphery of the rotating body, and the released oil passes through the flow path between the annular member and the opposing wall to each part of the outer periphery (outside) of the annular member Supplied.

  A movable member is provided between the outer peripheral surface of the rotating body and the inner peripheral surface of the annular member so as to be movable in the rotation axis direction. When the movable member moves to the opposing wall side and is disposed at a position where it comes into contact with the opposing wall, the movable member is interposed between the open end of the oil passage and the flow path sandwiched between the annular member and the opposing wall. Communication grooves that are open to both sides in the rotational radial direction are formed at the end of the movable member on the opposite wall side. Therefore, even if the movable member is interposed between the open end of the oil passage and the flow passage sandwiched between the annular member and the opposing wall, the oil discharged from the open end of the oil passage passes through the communication groove in the rotational radial direction of the movable member. Spills out of the outside.

  Therefore, regardless of the position of the movable member, it is possible to prevent the movable member from blocking the flow of oil from the open end of the oil passage toward the flow path sandwiched between the annular member and the opposing wall. As a result, oil can be supplied to each part of the outer periphery of the annular member through the flow path, and occurrence of problems such as wear and seizure due to insufficient lubrication can be suppressed in each part.

  Moreover, since it can suppress that the supply of oil to other parts becomes excessive, the increase in the drag loss of a clutch and a brake by excessive supply of oil can be suppressed. As a result, the torque transmission efficiency of the transmission can be improved, and as a result, the fuel efficiency improvement effect of the vehicle on which the transmission is mounted can be exhibited.

  The rotating body may be a first rotating shaft extending in the direction of the rotating axis, and the annular member may be a second rotating shaft having at one end a recess into which one end of the first rotating shaft is inserted.

  The movable member is a needle bearing having a configuration in which needle-like rollers are arranged in a circumferential direction in a cylindrical cage and are rotatably held, and the communication groove may be formed in the cage of the needle bearing.

  The communication groove may be formed only at the end portion on the opposite wall side of the movable member, but may be formed at both the end portion on the opposite wall side and the opposite end portion.

  When the movable member is a needle bearing, it is preferable that communication grooves are formed at both ends of the cage. With this configuration, when the movable member is externally fitted to the rotating body, it is not necessary to consider which one end or the other end is directed to the opposing wall side, and the assembly workability of the movable member is improved.

  ADVANTAGE OF THE INVENTION According to this invention, it can suppress that the flow of the oil which goes to the outer side of an annular member is interrupted | blocked by a movable member irrespective of the position of a movable member. As a result, oil can be supplied to each part of the outer periphery of the annular member through the flow path, and occurrence of problems such as wear and seizure due to insufficient lubrication can be suppressed in each part. Further, an increase in drag loss of the clutch and brake due to excessive oil supply can be suppressed, and an effect of improving the fuel efficiency of the vehicle by improving the torque transmission efficiency of the transmission can be exhibited.

It is sectional drawing which shows a part of transmission with which the oil supply structure which concerns on one Embodiment of this invention was employ | adopted. It is a perspective view of a needle bearing.

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

<Transmission>
FIG. 1 is a sectional view showing a part of a transmission 1 in which an oil supply structure according to an embodiment of the present invention is adopted. In FIG. 1, the hatching indicating the cross section is omitted.

  FIG. 1 shows a part of a transmission 1 mounted on a vehicle. Specifically, the transmission 1 has a configuration of a continuously variable transmission in which a belt is wound around a primary pulley and a secondary pulley. FIG. 1 shows a secondary shaft 2 and an output shaft of the transmission 1. The structure of the connection part with 3 is shown. The secondary shaft 2 and the output shaft 3 are arranged on the same axis so as to be rotatable.

  In the following description, the output shaft 3 side with respect to the secondary shaft 2 is referred to as “right side”, and the secondary shaft 2 side with respect to the output shaft 3 is referred to as “left side”.

  The right end portion 11 of the secondary shaft 2 is formed with a recess 12 that is opened at the end face. The recess 12 has a left end portion of the output shaft 3 which is formed in a columnar shape having an outer diameter smaller than the inner diameter of the recess 12 of the secondary shaft 2 and is inserted into the recess 12. A needle bearing 13 is interposed between the inner peripheral surface of the recess 12 and the output shaft 3. The secondary shaft 2 and the output shaft 3 are connected via a needle bearing 13 so as to be relatively rotatable.

  In order to transmit power between the secondary shaft 2 and the output shaft 3, the transmission 1 is provided with a planetary gear mechanism 21. The planetary gear mechanism 21 includes a sun gear 22, a carrier 23, and a ring gear 24. The sun gear 22 is externally fitted to the right end portion 11 of the secondary shaft 2 and is splined to the secondary shaft 2. The carrier 23 is provided so as to be integrally rotatable with a brake hub 25 of the brake B1 that brakes / allows the rotation of the carrier 23. A plurality of pinion gears 26 are rotatably held on the carrier 23. Each pinion gear 26 meshes with the sun gear 22. The ring gear 24 has a substantially cylindrical shape that collectively surrounds the plurality of pinion gears 26, and meshes with each pinion gear 26 from the outside in the rotational radial direction.

  In order to directly couple / separate the sun gear 22 and the ring gear 24, the transmission 1 is provided with a clutch C1. In the clutch C1, a plurality of clutch plates 34 and clutch disks 35 are alternately arranged between a clutch drum 32 fixed to the output shaft 3 and a clutch hub 33 supported by the sun gear 22 so as not to rotate relative to each other. . The ring gear 24 is held on the clutch drum 32 so as not to be relatively rotatable. Each clutch plate 34 is supported by a clutch drum 32, and each clutch disk 35 is supported by a clutch hub 33. A clutch piston 36 is disposed inside the clutch drum 32 so as to be movable in the axial direction, and a piston chamber 37 is formed between the clutch drum 32 and the clutch piston 36. Further, a canceller 38 is disposed on the opposite side of the piston chamber 37 with the clutch piston 36 interposed therebetween, and a canceller chamber 39 is formed between the clutch piston 36 and the canceller 38. Further, a return spring 40 is interposed between the clutch piston 36 and the canceller 38 to urge them in a direction away from each other.

  Further, a thrust bearing 41 is interposed between the output shaft 3 and the sun gear 22 in order to receive differential rotation between the output shaft 3 and the sun gear 22 in the released state of the clutch C1. The thrust bearing 41 includes an annular retainer 43 that holds a plurality of rolling elements 42, and an annular plate-shaped thrust trace 44 that is disposed on the sun gear 22 side, that is, the left side with respect to the retainer 43. . The thrust trace 44 contacts the right end of the sun gear 22 and faces the secondary shaft 2 and the needle bearing 13 from the right side. A gap 45 is provided between the right end of the secondary shaft 2 and the thrust trace 44.

<Oil supply structure>
A shaft center oil passage 51 is formed at the left end of the output shaft 3. The shaft center oil passage 51 extends on the rotation axis of the output shaft 3 to the left end surface of the output shaft 3 and is opened at the left end surface. It communicates with the space created between the left end face.

  The output shaft 3 is formed with a canceller discharge oil passage 52 that allows the canceller chamber 39 and the shaft center oil passage 51 to communicate with each other. Further, a communication oil passage 53 that communicates with the shaft center oil passage 51 is formed in the output shaft 3. The communication oil passage 53 is on the right side of the needle bearing 13 and at a position (facing position) facing the gap 45 between the right end of the secondary shaft 2 and the thrust trace 44 in the rotational radial direction (a position facing). It is open at the outer peripheral surface.

  When the oil pressure in the piston chamber 37 increases due to the supply of oil, the clutch piston 36 receives the oil pressure and moves, and the clutch piston 36 presses the clutch plate 34. Due to this pressing, the clutch plate 34 and the clutch disk 35 are pressed against each other (the clutch C1 is engaged), and the sun gear 22 and the ring gear 24 are brought into a directly connected state in which they rotate together.

  On the other hand, oil is always supplied to the canceller chamber 39. In a state where the sun gear 22 and the ring gear 24 are rotating together, a centrifugal force acts on the oil in the canceller chamber 39, and centrifugal hydraulic pressure is generated in the canceller chamber 39. With this centrifugal oil pressure, the centrifugal oil pressure generated in the piston chamber 37 can be canceled (cancelled). Therefore, when the supply of oil (hydraulic pressure) to the piston chamber 37 is stopped, the clutch piston 36 moves smoothly to the right due to the urging force of the return spring 40.

  The oil supplied to the canceller chamber 39 flows out from the canceller discharge oil passage 52 to the shaft center oil passage 51. Part of the oil flowing through the shaft center oil passage 51 flows through the communication oil passage 53 and is discharged from the open end of the communication oil passage 53 to the outer periphery of the output shaft 3.

  Part of the oil discharged from the communication oil passage 53 flows between the outer peripheral surface of the output shaft 3 and the thrust trace 44, and flows between the clutch hub 33 and the canceller 38, and the clutch plate 34 and the clutch disk. 35 and the like.

  For spline coupling between the right end portion 11 of the secondary shaft 2 and the sun gear 22, splines 61 and 62 are formed on the outer peripheral surface of the right end portion 11 of the secondary shaft 2 and the inner peripheral surface of the sun gear 22, respectively. Further, the sun gear 22 is formed with a lateral hole 63. The lateral hole 63 extends through the sun gear 22 in the rotational radial direction across the inner peripheral surface and the outer peripheral surface of the sun gear 22.

  A part of the oil discharged from the communication oil passage 53 flows through the gap 45 between the right end of the secondary shaft 2 and the thrust race 44, flows between the right end portion 11 of the secondary shaft 2 and the sun gear 22, and the sun gear. 22 is supplied to the left side. Part of the oil supplied to the left side of the sun gear 22 flows between the lock nut 64 disposed on the left side of the sun gear 22 and the sun gear 22 and is supplied to the pinion gear 26 and the bearing 65 disposed on the left side thereof. Is done.

  A shaft center oil passage 67 is formed in the support shaft 66 inserted through the pinion gear 26. The shaft center oil passage 67 is opened at the left end surface of the support shaft 66. The support shaft 66 is further formed with a communication oil passage 68 communicating with the shaft center oil passage 67. The communication oil path 68 is opened at the outer peripheral surface of the support shaft 66. An oil guide plate 69 is provided on the left side of the support shaft 66. The oil guide plate 69 has a substantially annular plate shape, and an outer peripheral end portion thereof is fixed to the carrier 23, and an inner peripheral end portion extends in the rotation radial direction with a space from the left end surface of the support shaft 66. . Part of the oil supplied to the left side of the sun gear 22 enters between the left end surface of the support shaft 66 and the oil guide plate 69, flows through the shaft center oil passage 67 and the communication oil passage 68, and supports the pinion gear 26. Supplied between the shaft 66.

  Part of the oil discharged from the communication oil passage 53 passes through the gap 45 between the right end of the secondary shaft 2 and the thrust trace 44, then flows through the lateral hole 63 and is supplied to the right side of the pinion gear 26.

  FIG. 2 is a perspective view of the needle bearing 13.

  The needle bearing 13 includes a cylindrical cage 71 and a plurality of needle-shaped needle rollers 72 that are rotatably held by the cage 71. The plurality of needle rollers 72 are arranged at equal intervals in the circumferential direction of the cage 71. With such a configuration, the needle bearing 13 is movable in the rotation axis direction (left-right direction) between the right end portion 11 of the secondary shaft 2 and the output shaft 3. Therefore, as shown in FIG. 1, the needle bearing 13 may come into contact with the thrust trace 44 from the left side, and the needle bearing 13 may be in a state of facing the open end of the communication oil passage 53 in the rotational radial direction.

  In this case, in the retainer 71 of the needle bearing 13, the oil flow from the open end of the communication oil passage 53 toward the gap 45 between the right end of the secondary shaft 2 and the thrust trace 44 is not blocked by the needle bearing 13. As shown in FIG. 2, a plurality of communication grooves 73 are formed at one end and the other end in the axial direction. The communication groove 73 is recessed in a substantially semicircular shape from the end surface of the cage 71 and is open on both sides in the rotational radial direction.

<Effect>
As described above, the communication grooves 73 are formed at both ends of the retainer 71 of the needle bearing 13 so as to be opened on both sides in the rotational radial direction. Therefore, even if the needle bearing 13 is interposed between the open end of the communication oil passage 53 and the gap 45 between the secondary shaft 2 and the thrust trace 44, the secondary shaft 2 and the thrust trace 44 are It can suppress that the oil flow which goes to the clearance gap 45 between is interrupted | blocked by the needle bearing 13. FIG. As a result, oil can be supplied to each part of the outer periphery of the secondary shaft 2 through the gap 45, and it is possible to suppress occurrence of problems such as wear and seizure due to insufficient lubrication in each part.

  Further, since the oil released from the open end of the communication oil passage 53 flows through the gap 45, it is possible to suppress an excessive amount of oil flowing between the outer peripheral surface of the output shaft 3 and the thrust trace 44. Further, an increase in drag loss of the clutch C1 due to excessive supply of oil can be suppressed. As a result, the torque transmission efficiency of the transmission 1 can be improved, and as a result, the fuel efficiency improvement effect of the vehicle on which the transmission 1 is mounted can be exhibited.

  Since the communicating grooves 73 are formed at both ends of the retainer 71 of the needle bearing 13, one end or the other end of the needle bearing 13 is fitted when the needle bearing 13 is fitted onto the output shaft 3. It is no longer necessary to consider which one is directed to the thrust trace 44 side, and the assembly workability of the needle bearing 13 is improved.

  Further, in the configuration in which the communication grooves 73 are formed at both ends of the cage 71, the facing area between the cage 71 and the secondary shaft 2 and the output shaft 3 is small. The flow resistance of the oil flowing between the second shaft 3 is reduced, and the flow of oil from between the retainer 71 and the secondary shaft 2 and the output shaft 3 to the gap 45 can be secured.

  Furthermore, by adjusting the cross-sectional area of the communication groove 73, the amount of oil flowing between the outer peripheral surface of the output shaft 3 and the thrust trace 44 and the amount of oil flowing through the gap 45 can be adjusted. The amount of oil supplied to each part can be set appropriately.

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

  For example, the configuration in which the communication groove 73 is formed at both ends of the cage 71 of the needle bearing 13 is taken up. However, the communication groove 73 is formed only at the right side (thrust trace 44 side) of the cage 71. It may be.

  In addition, the configuration in which the thrust trace 44 is opposed to the right end portion 11 of the secondary shaft 2 with a space is taken up. The two right end portions 11 may be opposed to each other with an interval.

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

2: Secondary shaft (annular member)
3: Output shaft (rotating body)
11: Right end (annular member)
13: Needle bearing (movable member)
44: Thrust trace (opposite wall)
53: Communication oil passage (oil passage)
73: Communication groove

Claims (1)

A rotating body having a cylindrical outer peripheral surface;
An annular member having an inner peripheral surface surrounding the periphery of the rotating body and concentrically spaced from the outer peripheral surface of the rotating body;
A movable member interposed between the outer peripheral surface of the rotating body and the inner peripheral surface of the annular member, and provided so as to be movable in the rotation axis direction of the rotating body;
Including the annular member and an opposing wall facing each other at an interval in the rotational axis direction,
The annular member is an end portion on one side of a first shaft extending in the rotation axis direction,
A concave portion that is opened at the end surface is formed at the end portion on the one side of the first shaft,
The rotating body is an end portion on the other side opposite to the one side of the second shaft extending in the rotation axis direction, and is inserted into the recess.
The rotating body extends on the rotation axis to the end surface on the other side of the second shaft and communicates with an axial oil passage that is opened at the end surface, and the axial oil passage. an oil passage that the oil from the road flows are formed,
The oil passage is opened at a position facing the rotational radial direction of the rotating body with respect to the space between the annular member and the opposing wall on the outer peripheral surface of the rotating body,
An oil supply structure in which the movable member is formed with communication grooves that are open at both ends in the rotational radial direction at least at the end on the opposite wall side.

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