JP2009222178A - Lubricating structure of planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating structure of a planetary gear device capable of stably securing a lubricating oil quantity to a pinion gear, and capable of reducing a dimension in the axial direction of a radial bearing. <P>SOLUTION: A sun gear 41 is integrally formed on an input shaft 3, and a stepped recessed part 33 having a large diameter part and a small diameter part is formed at a shaft end of the input shaft, and one end of a lubricating oil passage 34 is opened in the recessed part 33. A shaft 45 fitted to the recessed part 33 of the input shaft is formed in an axial part of a carrier 44, and an axial oil passage 70 and an inside oil passage 71 in the radial direction are formed in the carrier 44. A ball beating 57 is arranged between the large diameter part of the recessed part 33 and the shaft part 45. A seal ring 58 is arranged between the small diameter part of the recessed part 33 and the shaft part 45. Most of lubricating oil supplied via the lubricating oil passage 34 is supplied to the pinion gear 43 via the axial oil passage 70 and the inside oil passage 71 of the carrier 44. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

The present invention relates to a lubricating structure of a planetary gear device used for an automatic transmission, a continuously variable transmission, and the like, and more particularly to an oil passage structure of lubricating oil to a pinion gear.

A planetary gear device is widely used as a forward / reverse switching mechanism for an automatic transmission for a vehicle or a continuously variable transmission. As such a planetary gear device, Patent Document 1 discloses a device in which a sun gear is used as an input element, a ring gear is used as an output element, and a driving force input to the sun gear is transmitted to the ring gear via a pinion gear supported by a carrier. Has been.

FIG. 7 shows the planetary gear device disclosed in Patent Document 1. A sun gear 101 is splined to the input shaft 100, and a pinion gear 103 that meshes with the sun gear 101 is supported by a carrier 105 via a pinion shaft 104. The pinion gear 103 is also engaged with the ring gear 106. A bearing mounting portion 105 a extending axially forward (engine side) and a shaft supporting portion 105 b extending rearward are integrally formed on the inner diameter portion of the carrier 105, and the bearing mounting portion 105 a and the shaft supporting portion 105 b are connected to the bush 107. Is rotatably supported on the input shaft 100. A ball bearing 108 is attached between the bearing attachment portion 105 a and the sun gear 101.

A multi-plate brake 111 is interposed between the carrier plate 109 connected to the carrier 105 via the pinion shaft 104 and the case 110. The multi-plate brake 111 is fastened and released by a piston 112 disposed in the case 110. A multi-plate clutch 113 is interposed between the carrier plate 109 and the sun gear 101. The multi-plate clutch 113 is fastened and released by a piston 115 disposed on the pump cover 114. When the multi-plate clutch 113 is released and the multi-plate brake 111 is engaged, the rotation of the input shaft 100 is reversed, decelerated and transmitted to the ring gear 106, and a forward traveling state is set. On the other hand, when the multi-plate brake 111 is released and the multi-plate clutch 113 is engaged, the carrier 105 and the sun gear 101 rotate together, so that the input shaft 100 and the ring gear 106 rotate together to enter the reverse travel state.

In the case of the planetary gear device, the pinion gear 103 or the needle bearing 116 provided between the pinion gear 103 and the pinion shaft 104 needs to be constantly lubricated. Therefore, the lubrication hole 100a provided in the shaft center portion of the input shaft 100 is required. Supplying lubricating oil to The supplied lubricating oil passes through the radial hole 100b formed in the input shaft 100, lubricates the bush 107, and is formed in the inner hole 105c formed in the radial direction in the carrier 105 and the pinion shaft 104. The pinion gear 103 is lubricated through the oil hole 104a. The oil that has lubricated the pinion gear 103 then flows in the radial direction by centrifugal force to lubricate the multi-plate brake 111. Further, in order to lubricate the ball bearing 108, another radial hole 100c communicating with the lubrication hole 100a is formed in the input shaft 100.

In the above planetary gear device, since the carrier 105 is supported on the outer peripheral surface of the input shaft 100 via the bush 107, the load of the carrier 105 always acts on the bush 107, and the bush 107 tends to wear over time. When the bush 107 is worn, the amount of lubricating oil leaked through the bush 107 increases, and the amount of lubricating oil to the pinion gear 103 may be insufficient. A ball bearing 108 is mounted between the bearing mounting portion 105a of the carrier 105 and the sun gear 101. Since the input shaft 100 and the bearing mounting portion 105a exist on the inner diameter side of the ball bearing 108, the input In order to secure the shaft diameter of the shaft 100 and the thickness of the bearing mounting portion 105a, there is a drawback that the radial dimension of the ball bearing 108 increases.
JP 2007-113683 A

The present invention has been made to solve the above problems, and provides a lubricating structure for a planetary gear device that can stably secure the amount of lubricating oil to the pinion gear and can reduce the radial dimension of the radial bearing. The purpose is to do.

To achieve the above object, according to the present invention, in a planetary gear device having a sun gear as an input element and a ring gear or a carrier as an output element, the sun gear is integrally formed with the input shaft, and a large diameter is formed at the shaft end of the input shaft. A stepped concave portion having a portion and a small diameter portion is formed, and a shaft portion fitted to the concave portion of the input shaft is formed in the shaft center portion of the carrier, and the large diameter portion of the concave portion and the shaft portion are A radial bearing is disposed therebetween, a seal ring is disposed between the small-diameter portion of the recess and the shaft portion, and a lubricating oil passage having one end opened in the recess is formed in the shaft center portion of the input shaft. A shaft center oil passage formed in the shaft center portion of the shaft portion of the carrier and communicating with the lubricating oil passage of the input shaft is formed, and a radial inner oil passage communicating with the carrier in the shaft center oil passage is formed. Formed and fed through the lubricating oil passage Namerayu, via the axial oil passage and the internal oil passage of the carrier to provide a lubricating structure of a planetary gear unit, characterized in that to be supplied to the pinion gear supported on said carrier.

The lubricating oil supplied to the lubricating oil passage of the input shaft flows into the recess. Since the seal ring restricts the flow to the radial bearing side, most of the oil flowing into the recess is supplied to the pinion gear via the carrier center oil passage and the internal oil passage, and the pinion gear is forcibly lubricated. Therefore, there is no shortage of lubricating oil amount to the pinion gear. Since the positional relationship between the input shaft and the carrier is defined by a radial bearing, no load is applied to the seal ring, and there is no change in the amount of lubricating oil due to wear or the like.

Since the radial bearing is disposed between the input shaft and the carrier and the sun gear is integrally formed on the input shaft, the positional relationship between the sun gear and the carrier, and hence the sun gear and the pinion gear is also stabilized. Therefore, gear wear and gear noise can be effectively reduced. A radial bearing is arrange | positioned between the large diameter part internal peripheral surface of the stepped recessed part of an input shaft, and the axial part outer peripheral surface of a carrier. In other words, since only the shaft portion of the carrier exists on the inner diameter side of the radial bearing, the inner diameter dimension of the radial bearing can be made smaller than before, and a small radial bearing can be used. The radial bearing may be a bearing in which rolling elements are arranged between the inner race and the outer race, and may be a roller bearing in addition to a ball bearing.

A part of the lubricating oil supplied via the lubricating oil passage may be supplied to the radial bearing via the joint portion of the seal ring. Since the seal ring has a C-shaped structure with a part opened, the amount of lubricating oil applied to the radial bearing can be reduced to a specified amount by specifying the size of the joint portion.

It is desirable to form a sun gear at the shaft end of the input shaft and to form a radial bearing radially inward of the sun gear. When the sun gear is integrally formed on the input shaft, there is a thick portion on the inner diameter side of the sun gear. By using this thick portion, a stepped recess is formed, and a radial bearing is arranged in this recess, thereby providing a space. A radial bearing can be arranged efficiently.

According to the present invention, a stepped recess is formed at the shaft end of the input shaft, the shaft of the carrier is fitted into the recess, and a radial bearing is disposed between the large diameter portion of the recess and the shaft. Since the seal ring is disposed between the small diameter portion of the recess and the shaft portion, the amount of oil to the radial bearing can be reduced by being shielded by the seal ring of the lubricant supplied to the lubricating oil passage of the input shaft. Unlike the bush, the seal ring does not receive the support load of the carrier, so that the leak amount does not change with time. Most of the lubricating oil that has flowed into the recess is supplied to the pinion gear via the carrier center oil passage and the internal oil passage, so that the situation where the amount of lubricating oil in the pinion gear is insufficient can be solved.

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]
FIG. 1 is a skeleton diagram of an example of a continuously variable transmission to which a planetary gear device according to the present invention is applied. This embodiment is an FF horizontal type continuously variable transmission for an automobile, which is roughly driven by an engine output shaft 1 via a torque converter 2 and the rotation of the input shaft 3 is switched between forward and reverse. 10 is transmitted to the forward / reverse switching mechanism 4, the drive pulley 11, the driven pulley 21, and the continuously variable transmission A comprising the V belt 15 wound between both pulleys, and the power of the driven shaft 20 is transmitted to the output shaft 32. The differential device 30 is configured. The input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole. The V belt 15 used in this embodiment is a known metal belt composed of a pair of endless tension bands and a large number of blocks supported by these tension bands.

As shown in FIG. 2, each part constituting the continuously variable transmission is accommodated in a transmission case 5. An oil pump 6 is disposed between the torque converter 2 and the forward / reverse switching mechanism 4. The oil pump 6 includes a pump body 7 fixed to the transmission case 5, a pump cover 8 fixed to the pump body 7, and a pump gear 9 housed between the pump body 7 and the pump cover 8. It consists of The pump gear 9 is driven by the pump impeller 2 a of the torque converter 2. The turbine runner 2b of the torque converter 2 is connected to the input shaft 3, and the stator 2c is supported by the pump cover 8 via the one-way clutch 2d.

The forward / reverse switching mechanism 4 includes a planetary gear unit 40, a reverse brake 50, and a direct coupling clutch 60. The sun gear 41 of the planetary gear device 40 is formed integrally with the input shaft 3 as an input rotation member, and the ring gear 42 is connected to the drive shaft 10 as an output rotation member by a spline. The planetary gear device 40 is a single pinion system, the reverse brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5, and the direct clutch 60 is provided between the carrier 44 and the sun gear 41. . When the direct clutch 60 is released and the reverse brake 50 is engaged, the rotation of the input shaft 3 is reversed and decelerated and transmitted to the drive shaft 10 to enter the forward traveling state. Conversely, when the reverse brake 50 is released and the direct coupling clutch 60 is engaged, the carrier 44 and the sun gear 41 of the planetary gear device 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly coupled to each other, and the reverse traveling state is established. It becomes. The specific structure of the forward / reverse switching mechanism 4 will be described later.

The drive pulley 11 of the continuously variable transmission A includes a fixed sheave 11a integrally formed on the drive shaft 10, a movable sheave 11b supported on the drive shaft 10 so as to be axially movable and integrally rotatable. And a hydraulic servo 12 provided behind the movable sheave 11b. Shift control is performed by controlling the hydraulic pressure to the hydraulic servo 12. The driven pulley 21 includes a fixed sheave 21a integrally formed on the driven shaft 20, a movable sheave 21b supported on the driven shaft 20 so as to be axially movable and integrally rotatable, and behind the movable sheave 21b. And a hydraulic servo 22 provided. By controlling the hydraulic pressure of the hydraulic servo 22, a belt thrust necessary for torque transmission is given.

One end portion of the driven shaft 20 extends toward the engine side, and the output gear 27 is fixed to this one end portion. The output gear 27 meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.

Here, the specific structure of the forward / reverse switching mechanism 4 will be described in detail with reference to FIGS. The sun gear 41 is formed integrally with the shaft end portion of the input shaft 3. A clutch hub 61 of the direct coupling clutch 60 is fixed on the input shaft 3 and in front of the sun gear 41 (engine side), and an inner diameter portion of the inner clutch plate 62 of the direct coupling clutch 60 is formed on the outer periphery of the clutch hub 61. The spline is engaged. A stepped recess 33 having a large-diameter portion 33 a and a small-diameter portion 33 b is formed at the shaft end of the input shaft 3 and inside the sun gear 41 in the radial direction.

The ring gear 42 includes a disk-shaped flange portion 42a and a drum portion 42b having a gear portion on the inner periphery, and has a bag structure with one end closed. The inner peripheral end of the flange portion 42 a is splined to the drive shaft 10. The other axial end of the drum portion 42b is an open end.

A stepped shaft portion 45 projecting toward the input shaft 3 is integrally projected on the shaft center portion of the carrier 44, and the shaft portion 45 is fitted in the recess 33 of the input shaft 3. A ball bearing 57, which is an example of a radial bearing, is fitted between the large diameter portion 33 a of the recess 33 and the large diameter portion 45 a of the shaft portion 45. Since the ball bearing 57 is disposed on the inner diameter side of the sun gear 41, the tilt of the carrier 44 can be effectively suppressed even if a moment caused by the meshing reaction force between the sun gear 41 and the pinion gear 43 acts on the carrier 44. A seal ring 58 is disposed between the small diameter portion 33 b of the concave portion 33 and the small diameter portion 45 b of the shaft portion 45. As shown in FIG. 5, the seal ring 58 is a C-shaped ring having an abutment portion 58a. The shape of the joint portion 58a is not limited to FIG. A circumferential groove 45c is formed on the outer peripheral surface of the small diameter portion 45b of the shaft portion 45, and a seal ring 58 is fitted in the circumferential groove 45c. Due to the radial spring force of the seal ring 58, the seal ring 58 is in contact with the inner peripheral surface of the small diameter portion 33 b of the recess 33. The abutment portion 58a is not limited to being cut obliquely.

A plurality of columnar portions 44a (see FIG. 2) protruding in the axial direction are integrally formed on the carrier 44, and a carrier plate 46 is fitted and fixed to the outer periphery of the distal end portion of these columnar portions 44a. A pinion shaft 47 is bridged and fixed between the carrier 44 and the carrier plate 46. As shown in FIG. 4, one end of the pinion shaft 47 inserted into the carrier 44 is prevented from rotating so as to have a predetermined phase with respect to the carrier 44 by a roller pin 49 press-fitted from the outside in the radial direction of the carrier 44. And is secured. That is, the opening end of the oil hole 47 a formed inside the pinion shaft 47 is positioned so as to correspond to the opening end of the internal oil passage 71 formed radially inside the carrier 44. The pinion gear 43 is rotatably supported on the pinion shaft 47 via a needle bearing 48, and each pinion gear 43 is disposed in the circumferential space between the columnar portions 44a.

The carrier plate 46 is integrally formed with a cylindrical portion 46a that protrudes in the axial direction toward the front side (engine side). The outer peripheral portion of the outer clutch plate 63 of the direct coupling clutch 60 is formed on the inner peripheral portion of the cylindrical portion 46a. Is in spline engagement, and the inner diameter portion of the inner brake plate 51 of the reverse brake 50 is spline engaged with the outer peripheral portion of the cylindrical portion 46a. As described above, the cylindrical portion 46 a serves as the brake hub of the reverse brake 50 and the clutch drum of the direct coupling clutch 60.

The piston 53 of the reverse brake 50 is slidably disposed on the inner wall of the transmission case 5. By supplying hydraulic pressure between the piston 53 and the transmission case 5, the piston 53 moves forward. The outer brake plate 52 and the inner brake plate 51 can be fastened. As a reaction force member that supports the end portion of the outer brake plate 52 pressed by the pressure of the piston 53, a cylindrical stopper portion 8a is integrally projected from the pump cover 8 that is a stationary member.

A piston 64 having a U-shaped cross section is disposed on the rear surface side (planetary gear device side) of the pump cover 8, and the direct coupling clutch 60 is fastened by the piston 64. A thrust bearing 65 that allows relative rotation is disposed between the outer clutch plate 63 and the piston 64. The thrust bearing 65 is fitted and held on the inner diameter side of the cylindrical portion 46 a of the carrier plate 46 by a bearing retainer 66. The thrust bearing 65 effectively transmits the axial pressure of the piston 64 to the outer clutch plate 63 and prevents the piston 64 from rotating with the outer clutch plate 63. Since the side surface of the carrier plate 46 is located behind the outer clutch plate 63, the end portion of the outer clutch plate 63 pushed by the piston 64 can be supported by the carrier plate 46.

A spring retainer 67 is disposed on the outer peripheral side surface of the piston 64, and a return spring 55 is disposed between the outer peripheral end of the spring retainer 67 and the reverse brake piston 53. The springs 55 also serve as return springs for both the direct clutch piston 64 and the reverse brake piston 53, and an appropriate number of springs 55 are provided on the outer peripheral side of the outer brake plate 52 of the reverse brake 50. Since the reverse brake 50 and the direct clutch 60 are not operated at the same time, one type of spring 55 can serve as both return springs.

Here, the lubricating structure of the planetary gear device 40 will be described with reference to FIGS. A lubricating oil passage 34 having one end opened in the recess 33 is formed in the shaft center portion of the input shaft 3. Lubricating oil of a predetermined pressure is supplied to the lubricating oil passage 34 from the lubricating oil supply passage 35 of the pump cover 8 through the radial hole 36. A shaft center oil passage 70 is formed in the shaft center portion of the shaft portion 45 of the carrier 44 so as to face the lubricant oil passage 34 of the input shaft 3, and the shaft center oil passage 70 and the lubricant oil passage 34 communicate with each other. ing. The carrier 44 is formed with a radial internal oil passage 71 that communicates with the axial oil passage 70 in the orthogonal direction.

The lubricating oil supplied to the recess 33 through the lubricating oil passage 34 of the input shaft 3 is guided to the axial oil passage 70 of the carrier 44 and further supplied to the oil hole 47a of the pinion shaft 46 through the internal oil passage 71. Is done. Further, a part of the lubricating oil supplied to the recess 33 is supplied to the ball bearing 57 through the joint portion 58a of the seal ring 58 as shown in FIG. By defining the size of the joint portion 58a and restricting the amount of lubricating oil to the ball bearing 57, the amount of lubricating oil guided to the pinion shaft 46 can be secured. An orifice hole 72 is formed at the terminal end of the axial oil passage 70 of the carrier 44, and a part of the lubricating oil is formed through the orifice hole 72 at a hollow portion formed at the shaft end of the drive shaft 10. 73, flows radially outward due to centrifugal force, thrust bearing 74 disposed between carrier 44 and ring gear 42, spline fitting portion 75 between ring gear 42 and drive shaft 10, and drive shaft 10 are connected to case 5 It is possible to lubricate the ball bearings 76 and the like that are supported.

As described above, the lubricating oil supplied to the oil hole 47 a of the pinion shaft 47 forcibly lubricates the needle bearing 48 and further forcibly lubricates the pinion gear 43. Then, after the pinion gear 43 is lubricated, the pinion gear 43 flows radially outward by centrifugal force and is stored inside the ring gear 42. Since the ring gear 42 has a bag structure, almost all of the lubricating oil sent through the internal oil passage 71 is accumulated inside the ring gear 42, discharged from the open end thereof, and supplied to the reverse brake 50. Therefore, seizure of the brake 50 can be reliably prevented. In addition, not only the lubricating oil supplied via the internal oil passage 71 but also the lubricating oil that has flowed through the orifice hole 72 is collected at the inner peripheral portion of the ring gear 42, and these lubricating oils are gathered to collect the ring gear 42. The reverse brake 50 can be lubricated.

A part of the lubricating oil supplied to the lubricating oil passage 34 of the input shaft 4 is supplied to the inner diameter side of the direct coupling clutch 60 and the thrust bearing 65 through a small hole 37 formed in the radial direction of the input shaft 4, and centrifugal force Is used to lubricate the direct coupling clutch 60 and the thrust bearing 65. Therefore, the lubricating oil supplied to the lubricating oil passage 34 can lubricate all the parts constituting the forward / reverse switching mechanism 4.

FIG. 6 shows a second embodiment of the present invention. In the first embodiment, lubricating oil is supplied to the ball bearing 58 through the joint portion 58a of the seal ring 58. However, the joint portion 58a of the seal ring 58 is set to be narrow, and the shaft portion 45 has a radial direction. Lubricating oil may be supplied to the ball bearing 58 through the orifice hole 45d by forming the orifice hole 45d.

In the planetary gear device of the above-described embodiment, an example in which a ring gear is used as an output element has been described. However, a carrier may be used as an output element.
Although the example of the stepped structure in which the shaft portion 45 of the carrier 44 has the large-diameter portion 45a and the small-diameter portion 45b has been shown, the shaft portion having a certain diameter that can be fitted into the small-diameter portion 33b of the recess 33 is also shown. Good. In this case, the radial dimension of the ball bearing 57 can be further reduced.
The present invention is not limited to the above embodiments. It goes without saying that the planetary gear device of the present invention can be applied not only to a continuously variable transmission but also to a general automatic transmission.
Although the single pinion type planetary gear device has been described in the above embodiment, a double pinion type planetary gear device may be used.

1 is a skeleton diagram of an example of a continuously variable transmission to which a planetary gear device according to the present invention is applied. FIG. 2 is a detailed sectional view of a forward / reverse switching mechanism of the continuously variable transmission shown in FIG. 1. FIG. 3 is a cross-sectional view of a main part showing a lubrication structure of the planetary gear device shown in FIG. 2. FIG. 4 is an exploded view of main parts of the planetary gear device shown in FIG. 3. It is a perspective view of a seal ring. It is sectional drawing of the other Example which shows the lubrication structure to a ball bearing. It is sectional drawing of the conventional planetary gear apparatus.

Explanation of symbols

3 Input shaft 4 Forward / reverse switching mechanism 10 Drive shaft 33 Recess 33a Large diameter portion 33b Small diameter portion 34 Lubricating oil passage 40 Planetary gear device 41 Sun gear 42 Ring gear 43 Pinion gear 44 Carrier 45 Shaft portion 46 Carrier plate 50 Reverse brake 57 Ball bearing (radial bearing)
58 Seal ring 58a Joint portion 60 Direct coupling clutch 70 Shaft center oil passage 71 Internal oil passage

Claims (3)

In a planetary gear device having a sun gear as an input element and a ring gear or carrier as an output element,
The sun gear is integrally formed with the input shaft, and a stepped recess having a large diameter portion and a small diameter portion is formed at the shaft end of the input shaft,
A shaft portion that is fitted into the concave portion of the input shaft is formed in the shaft center portion of the carrier,
A radial bearing is disposed between the large diameter portion of the recess and the shaft portion,
A seal ring is disposed between the small diameter portion of the recess and the shaft portion,
A lubricating oil passage having one end opened in the recess is formed in the axial center of the input shaft,
A shaft center oil passage communicating with the lubricating oil passage of the input shaft is formed in the shaft center portion of the shaft portion of the carrier, and a radial internal oil passage communicating with the shaft center oil passage is formed in the carrier. ,
A lubricating structure for a planetary gear device, wherein the lubricating oil supplied through the lubricating oil passage is supplied to a pinion gear supported by the carrier through an axial oil passage and an internal oil passage of the carrier. . 2. The planetary gear unit lubrication structure according to claim 1, wherein a part of the lubricating oil supplied via the lubricating oil passage is supplied to the radial bearing via a joint portion of the seal ring. . 3. The lubricating structure for a planetary gear device according to claim 1, wherein the sun gear is formed at an end portion of the input shaft, and the radial bearing is disposed radially inward of the sun gear.

Images