JP2018059528A - Oil supply structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply structure capable of simplifying the machining (forming) of a lateral hole on a first gear spline-coupled with a rotor.SOLUTION: A sun gear 22 is externally fitted with a secondary shaft 2, and is spline-coupled with the secondary shaft 2. The sun gear 22 is formed with a toothless portion 63 made by missing a part of a spline 62 over the whole length in a rotary axial direction. The sun gear 22 is formed with a lateral hole 68 communicating with a space on a right side of a pinion gear 26 while penetrating between an inner peripheral surface and an outer peripheral surface. At a part opposing to the lateral hole 68 between the secondary shaft 2 and the sun gear 22 in a rotary diametrical direction, an oil collection space 67 is formed by missing the whole circumferential of the spline of the sun gear 22.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an oil supply structure.

  For example, 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 brake for braking the rotating element, a clutch for connecting the rotating element and another rotating element, and the like are often used. The clutch and brake must absorb the differential rotation between the rotating elements, and require oil supply for lubrication in order to prevent seizure due to the absorption of the differential rotation. Further, in the automatic transmission, a bearing is used to hold the rotating element rotatably in a case that accommodates the automatic transmission. This bearing must absorb the differential rotation between the case and the rotating element, and requires oil supply for lubrication to prevent seizure due to absorption of the differential rotation.

  For example, in the configuration shown in FIG. 3, a planetary gear mechanism 303 is provided to transmit power from the first rotating shaft 301 to the second rotating shaft 302.

  The carrier 304 of the planetary gear mechanism 303 is provided so as to rotate integrally with a brake hub 306 of a brake 305 that brakes / allows rotation of the carrier 304. A plurality of pinion gears 307 are rotatably held on the carrier 304. Each pinion gear 307 meshes with the sun gear 308 of the planetary gear mechanism 303. The sun gear 308 is fitted on the first rotating shaft 301 and is spline-coupled to the first rotating shaft 301. The ring gear 309 of the planetary gear mechanism 303 collectively surrounds the plurality of pinion gears 307 and meshes with each pinion gear 307.

  In addition, a clutch 311 is provided to directly couple / separate the sun gear 308 and the ring gear 309 of the planetary gear mechanism 303. In the clutch 311, a plurality of clutch plates 314 and clutch disks 315 are alternately arranged between a clutch drum 312 fixed to the second rotating shaft 302 and a clutch hub 313 supported by the sun gear 308 so as not to rotate relative to each other. Yes. The ring gear 309 is held on the clutch drum 312 so as not to be relatively rotatable. Each clutch plate 314 is supported by a clutch drum 312, and each clutch disk 315 is supported by a clutch hub 313. A clutch piston 316 is disposed inside the clutch drum 312 so as to be movable in the axial direction, and a piston chamber 317 is formed between the clutch drum 312 and the clutch piston 316. A canceller 318 is disposed on the opposite side of the piston chamber 317 with the clutch piston 316 interposed therebetween, and a canceller chamber 319 is formed between the clutch piston 316 and the canceller 318. Further, a return spring 320 is interposed between the clutch piston 316 and the canceller 318 to urge them in a direction away from each other.

  An axial center oil passage 321 is formed at the end of the second rotation shaft 302 on the first rotation shaft 301 side (left side in FIG. 2, hereinafter referred to as “left side”). The second rotating shaft 302 is formed with a canceller discharge oil passage 322 that allows the canceller chamber 319 and the shaft center oil passage 321 to communicate with each other. Further, a communication oil passage 323 communicating with the shaft center oil passage 321 is formed in the second rotating shaft 302. The communication oil passage 323 is at a position on the second rotation shaft 302 side (right side in FIG. 2, hereinafter referred to as “right side”) with respect to the bearing 324 interposed between the first rotation shaft 301 and the second rotation shaft 302. The second rotary shaft 302 is open at the outer peripheral surface.

  When the oil pressure in the piston chamber 317 increases due to the supply of oil, the clutch piston 316 receives the oil pressure and moves, and the clutch piston 316 presses the clutch plate 314. Due to this pressing, the clutch plate 314 and the clutch disk 315 are brought into pressure contact (the clutch 71 is engaged), and the sun gear 308 and the ring gear 309 are brought into a directly connected state in which they rotate together.

  On the other hand, oil is always supplied to the canceller chamber 319. Thereby, the oil flows through the canceller chamber 319, the canceller discharge oil passage 322, and the axial center oil passage 321. A part of the oil flowing through the axial oil passage 321 flows through the communication oil passage 323 and flows out to the right side of the bearing 324, and the remaining oil flows between the first rotating shaft 301 and the second rotating shaft 302. It flows out into the space that is created between.

  In a state where the sun gear 308 and the ring gear 309 rotate as a unit, centrifugal force acts on the oil in the canceller chamber 319, and centrifugal oil pressure is generated in the canceller chamber 319. With this centrifugal oil pressure, the centrifugal oil pressure generated in the piston chamber 317 can be canceled (cancelled). Therefore, when the supply of oil (hydraulic pressure) to the piston chamber 317 is stopped, the clutch piston 316 smoothly moves to the right side by the urging force of the return spring 320.

  A part of the oil flowing out from the communication oil passage 323 to the position on the right side of the bearing 324 flows between the clutch hub 313 and the canceller 318 and is supplied to the clutch plate 314, the clutch disk 315, and the like.

  A part of the oil flowing out from the communication oil passage 323 flows between the first rotating shaft 301 and the sun gear 308. On the inner peripheral surface of the sun gear 308, as shown in FIG. 4, a part of the spline 331 is missing (missing teeth) over the entire length in the rotation axis direction, thereby forming a missing tooth part 332 through which oil can circulate. ing. As a result, the oil pipe resistance between the first rotating shaft 301 and the sun gear 308 is lowered, and the oil is passed to the left side of the sun gear 308 through the first rotating shaft 301 and the sun gear 308 (mainly the toothless portion 332). Is well supplied. The oil flows between the lock nut 333 disposed on the left side of the sun gear 308 and the sun gear 308 and is supplied to the pinion gear 307 and the bearing 334 disposed on the left side thereof.

  Further, the sun gear 308 is formed with a lateral hole 335 penetrating in the rotational radial direction at the same position in the circumferential direction as the missing tooth portion 332. As a result, part of the oil flowing through the missing tooth portion 332 flows through the lateral hole 335 and is supplied to the right side of the pinion gear 307.

Japanese Patent Laying-Open No. 2015-145682

  However, in such a configuration, since it is necessary to match the positions of the lateral holes 335 and the missing tooth portions 332 in the circumferential direction, the processing of the lateral holes 335 is difficult, and the manufacturing cost of the sun gear 308 is increased.

  An object of the present invention is to provide an oil supply structure that can simplify processing (formation) of a lateral hole in a first gear that is spline-coupled to a rotating body.

  In order to achieve the above object, in the oil supply structure according to the present invention, the rotating body and the first gear fitted to the rotating body are spline-coupled, and the first gear rotates a part of the spline. A missing tooth portion formed by omission over the entire length in the axial direction, and a horizontal hole penetrating between the inner peripheral surface and the outer peripheral surface are formed, and the first gear passes between the rotating body and the first gear through the missing tooth portion. Oil is supplied to one side in the rotational axis direction of the meshing second gear, and oil is supplied to the other side in the rotational axis direction of the second gear through a horizontal hole from between the rotary body and the first gear. An oil sump space is formed in a portion facing the lateral hole in the radial direction between one gear and the first gear spline being lost over the entire circumference.

  According to this configuration, the first gear is fitted on the rotating body and is splined to the rotating body. The first gear is formed with a missing tooth portion by missing a part of the spline over the entire length in the rotation axis direction. Oil is supplied to the one side in the rotation axis direction of the second gear that meshes with the first gear from between the rotating body and the first gear through a missing tooth portion. Further, the first gear is formed with a horizontal hole communicating with the space on the other side in the rotation axis direction of the second gear so as to penetrate between the inner peripheral surface and the outer peripheral surface. On the other side in the rotation axis direction of the second gear, oil is supplied from between the rotating body and the first gear through a lateral hole.

  An oil sump space is formed in the portion facing the lateral hole between the rotating body and the first gear in the rotational radial direction by removing the spline of the first gear over the entire circumference. Therefore, oil can be supplied from the oil reservoir space to the horizontal hole. Therefore, it is possible to eliminate the need to match the circumferential positions of the lateral hole and the missing tooth portion, and the processing of the lateral hole in the first gear is simplified. As a result, the manufacturing cost of the first gear can be reduced.

  In the oil sump space, not only the spline of the first gear but also the spline of the rotating body may be missing over the entire circumference.

  According to the present invention, it is possible to eliminate the necessity of matching the circumferential positions of the lateral hole and the missing tooth portion, and the processing of the lateral hole in the first gear is simplified, thereby reducing the manufacturing cost of the first gear. Can do.

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 sectional drawing which shows a part of sun gear, and shows a cross section when a sun gear is cut | disconnected by the plane which crosses a rotation axis of a sun gear and passes a horizontal hole. It is sectional drawing which shows the conventional oil supply structure. It is sectional drawing which shows a part of conventional sun gear, and shows a cross section when a sun gear is cut | disconnected by the plane which passes through a horizontal hole orthogonally to the rotating shaft line of a sun gear.

  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 employed. 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 cylindrical inner peripheral surface centered on the rotation axis of the secondary shaft 2.

  The left end portion of the output shaft 3 is formed in a cylindrical shape having an outer diameter smaller than the inner diameter of the concave portion 12 of the secondary shaft 2 and is inserted into the concave portion 12. A bearing 13 is interposed between the inner peripheral surface of the recess 12 and the output shaft 3, and the secondary shaft 2 and the output shaft 3 are connected via the 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.

<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, is opened at the left end surface thereof, and is connected to the secondary shaft 2 and the output shaft 3 within the recess 12 of the secondary shaft 2. 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 opened on the outer peripheral surface of the output shaft 3 at a position on the right side of the bearing 13.

  When the oil pressure in the piston chamber 37 increases due to the supply of oil, the clutch piston 36 moves by receiving the oil pressure, and the clutch piston 36 presses the clutch plate 34. Due to this pressing, the clutch plate 34 and the clutch disc 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. As a result, the oil flows through the canceller chamber 39, the canceller discharge oil passage 52 and 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 flows out to the right side of the bearing 13.

  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.

  A part of the oil that flows out from the communication oil passage 53 to the position on the right side with respect to the bearing 13 flows between the clutch hub 33 and the canceller 38 and is supplied to the clutch plate 34, 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. As shown in FIG. 2, a part of the spline 62 of the sun gear 22 is missing (missing teeth) over the entire length in the rotation axis direction on the inner peripheral surface of the sun gear 22 to form a missing tooth part 63. ing.

  Further, the spline 61 is missing (not formed) at the rightmost end portion 66 having a constant width from the right end of the right end portion 11 of the secondary shaft 2, and correspondingly, the spline 61 on the inner peripheral surface of the sun gear 22 is correspondingly omitted. The spline 62 is missing (not formed) at a portion facing the right end portion 66. Thus, an oil sump space 67 is formed between the rightmost end portion 66 of the secondary shaft 2 and the inner peripheral surface of the sun gear 22 by removing the splines 61 and 62 over the entire circumference.

  Further, a lateral hole 68 is formed in the sun gear 22 at a position facing the oil reservoir space 67 in the rotational radial direction. The lateral hole 68 passes through the sun gear 22 in the radial direction so as to straddle the inner peripheral surface and the outer peripheral surface of the sun gear 22.

  A part of the oil flowing out from the communication oil passage 53 is supplied to the oil reservoir space 67 and flows between the right end portion 11 of the secondary shaft 2 and the sun gear 22 from the oil reservoir space 67. Since the toothless portion 63 is formed on the inner peripheral surface of the sun gear 22, the oil flows through the toothless portion 63 between the right end portion 11 of the secondary shaft 2 and the sun gear 22. Go down. As a result, the oil is satisfactorily supplied to the left side of the sun gear 22. 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.

  A part of the oil flowing out from the communication oil passage 53 is supplied to the oil reservoir space 67, flows from the oil reservoir space 67 through the horizontal hole 68, and is supplied to the right side of the pinion gear 26.

<Effect>
As described above, the sun gear 22 is externally fitted to the secondary shaft 2 and is splined to the secondary shaft 2. The sun gear 22 is formed with a missing tooth portion 63 by missing a part of the spline 62 over the entire length in the rotation axis direction. On the left side of the pinion gear 26 that meshes with the sun gear 22, oil is supplied from between the secondary shaft 2 and the sun gear 22 through the missing tooth portion 63. Further, the sun gear 22 is formed with a lateral hole 68 communicating with the space on the right side of the pinion gear 26 so as to penetrate between the inner peripheral surface and the outer peripheral surface. Oil is supplied to the right side of the pinion gear 26 from between the secondary shaft 2 and the sun gear 22 through the lateral hole 68.

  An oil sump space 67 is formed in the portion facing the horizontal hole 68 between the secondary shaft 2 and the sun gear 22 in the rotational radial direction by removing the spline of the sun gear 22 over the entire circumference. Therefore, oil can be supplied from the oil reservoir space 67 to the horizontal hole 68. Therefore, it is not necessary to match the positions of the lateral holes 68 and the tooth missing portions 63 in the circumferential direction, and the processing of the lateral holes 68 in the sun gear 22 is simplified. As a result, the manufacturing cost of the sun gear 22 can be reduced.

<Modification>
While one embodiment of the present invention has been described above, the present invention can be implemented in other forms.

  For example, in the above-described embodiment, both the spline 61 of the secondary shaft 2 and the spline 62 of the sun gear 22 are omitted over the entire circumference between the rightmost end portion 66 of the secondary shaft 2 and the inner peripheral surface of the sun gear 22. Although the oil sump space 67 is formed, only the spline 62 of the sun gear 22 may be omitted, and the spline 61 of the secondary shaft 2 may be formed.

  Moreover, although the transmission 1 has the configuration of a continuously variable transmission, not only the continuously variable transmission, but also a transmission having a configuration of a stepped automatic transmission (AT), The present invention can be widely applied to various types of transmissions. Furthermore, the present invention can be applied to mechanisms other than the transmission.

  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 (rotating body)
22: Sun gear (first gear)
26: Pinion gear (second gear)
62: Spline 63: Missing tooth part 67: Oil sump space 68: Side hole

Claims (1)

The rotating body and the first gear fitted on the rotating body are spline-coupled,
The first gear is formed with a missing tooth portion by missing a part of the spline over the entire length in the rotation axis direction, and a lateral hole penetrating between the inner peripheral surface and the outer peripheral surface,
Oil is supplied to the one side in the rotational axis direction of the second gear that meshes with the first gear from the gap between the rotating body and the first gear,
Oil is supplied from the space between the rotating body and the first gear to the other side in the rotational axis direction of the second gear through the lateral hole,
Between the rotating body and the first gear, an oil sump space is formed in a portion facing the lateral hole in the rotational radial direction by dropping the spline of the first gear over the entire circumference. Oil supply structure.

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