JP2010071400A - Lubricant structure of automatic transmission for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To certainly supply lubricating oil into a pinion shaft of a planetary carrier when the planetary carrier of the planetary gear mechanism of an automatic transmission for a vehicle is stopped. <P>SOLUTION: When the planetary carrier 19 of the planetary gear mechanism 16 of the automatic transmission for the vehicle is rotated, the lubricating oil flowing from the radial inside of the planetary carrier 19 to the radial outside thereof by centrifugal force is led to the oil gallery 44a of the pinion shaft 44 by the inside guide 53a of a guide member 51, thereby lubricating a sliding surface between a pinion 22 and the pinion shaft. When the planetary carrier 19 is stopped, the lubricating oil flowing on the upper side of the planetary carrier 19 from the radial outside of the planetary carrier to the radial inside thereof by gravity is led to the oil gallery 44a of the pinion shaft 44 by the outside guide 53b of the guide member 51, thereby lubricating the sliding surface between the pinion 22 and the pinion shaft. Accordingly, it is possible to certainly lubricate the sliding surface between the pinion shaft 44 and the pinion 22 while eliminating both formation of an oil passage for lubrication provided to the planetary carrier 19 itself and supply of the pressurized lubricating oil to the oil passage. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention includes a planetary gear mechanism in which a sun gear, a planetary carrier, and a ring gear are coaxially arranged around a rotation shaft, and a pinion supported on the planetary carrier via a pinion shaft is engaged with the sun gear and the ring gear. The present invention relates to a lubricating structure of an automatic transmission for lubricating a sliding surface between the pinion shaft and the pinion with lubricating oil supplied to an oil hole formed inside the shaft.

  When lubricating a needle bearing disposed between a pinion shaft and a pinion through an oil passage formed in a pinion shaft of a planetary carrier of a planetary gear mechanism of an automatic transmission for a vehicle, the planetary carrier is rotating. Sometimes, lubricating oil can be supplied to the pinion shaft by centrifugal force from an oil passage inside the rotating shaft that supports the planetary carrier. However, when the planetary carrier stops rotating at a specific gear stage of the automatic transmission, it becomes difficult to supply the lubricating oil by the centrifugal force described above. It is necessary to enlarge the diameter of the oil passage of the planetary carrier.

Therefore, what is described in Patent Document 1 below forms an oil passage 280b extending radially in the output shaft 280 that rotates in the vicinity of the planetary carrier C201 when the planetary carrier C201 is stopped. Lubricating oil is supplied to the inside of the pinion shaft of the planetary carrier C201 by having the end face the radially inner end of the lubricating oil passage C201a formed in the planetary carrier C201 in the radial direction.
JP-A-7-208586

  However, in the above-mentioned conventional one, it is necessary to form a lubricating oil passage C201a that extends from the radially inner end side to the pinion shaft inside the planetary carrier C201, which increases the size of the planetary carrier C201 and increases the weight. In addition, there is a problem that causes an increase in cost due to an increase in the number of processing steps for forming the lubricating oil passage C201a and an increase in the number of parts due to the plug closing the downstream end of the lubricating oil passage C201a.

  The present invention has been made in view of the above-described circumstances, and makes it possible to reliably supply lubricating oil to the inside of a pinion shaft when the planetary carrier of the planetary gear mechanism of the automatic transmission for a vehicle is stopped. For the purpose.

  In order to achieve the above object, according to the first aspect of the present invention, a sun gear, a planetary carrier and a ring gear are arranged coaxially around a rotation axis, and the pinion supported by the planetary carrier via a pinion shaft is Lubricating a vehicle automatic transmission that includes a planetary gear mechanism that meshes with a sun gear and the ring gear, and that lubricates a sliding surface between the pinion shaft and the pinion with lubricating oil supplied to an oil hole formed inside the pinion shaft. In the structure, the planetary carrier includes an annular guide member, and the guide member is supplied from the radially outer side with an inner guide portion that guides the lubricating oil supplied from the radially inner side to the oil hole of the pinion shaft. An outer guide portion for guiding lubricating oil to the oil hole of the pinion shaft is provided. Lubrication structure for an automatic transmission is proposed.

  According to the second aspect of the present invention, in addition to the structure of the first aspect, a hydraulic engagement means for shifting is provided, and a part of the hydraulic oil that operates the hydraulic engagement means is used as the lubricating oil. A lubricating structure for an automatic transmission for a vehicle is proposed in which the guide member is supplied from the outside in the radial direction of the planetary carrier.

  According to the invention described in claim 3, in addition to the configuration of claim 2, part of the hydraulic oil that operates the hydraulic engagement means is provided via a check valve that opens with a hydraulic pressure equal to or higher than a predetermined value. Then, a lubricating structure for an automatic transmission for a vehicle is proposed, which is supplied to the guide member.

  According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, the check valve is provided in an oil passage connected to an upper portion of a working hydraulic chamber of the hydraulic engagement means. A lubricating structure for an automatic transmission for a vehicle is proposed.

  The input shaft 13 and the center shaft 36 of the embodiment correspond to the rotation shaft of the present invention, and the first planetary gear mechanism 16 of the embodiment corresponds to the planetary gear mechanism of the present invention, and the second planetary gear mechanism of the embodiment. The brake B2 corresponds to the hydraulic engagement means of the present invention.

  According to the configuration of the first aspect, when the planetary carrier of the planetary gear mechanism of the automatic transmission of the vehicle is rotating, lubricating oil that flows by centrifugal force from the radially inner side to the outer side of the rotating planetary carrier is guided inside the guide member. It is possible to lubricate the sliding surface between the pinion shaft and the pinion supported on the outer periphery of the pinion shaft. Further, when the planetary carrier stops rotating, the lubricating oil that flows by gravity from the radially outer side to the inner side of the upper part of the stopped planetary carrier is guided to the pinion hole of the pinion shaft by the outer guide part of the guide member, and the pinion shaft and its The sliding surface with the pinion supported on the outer periphery can be lubricated. This eliminates the need to form an oil passage for lubrication in the planetary carrier itself and supply pressurized oil to the oil passage, while the planetary carrier is rotating and stopped. Lubricating oil can be reliably supplied to the oil hole of the pinion shaft with a simple structure.

  According to the second aspect of the present invention, a part of the hydraulic oil that operates the hydraulic engagement means for shifting is supplied to the guide member from the outside in the radial direction of the planetary carrier as lubricating oil, so that the planetary carrier is stopped. Even if it exists, lubricating oil can be supplied reliably.

  According to the third aspect of the present invention, part of the hydraulic oil that operates the hydraulic engagement means is supplied to the guide member via the check valve that opens with a hydraulic pressure that is greater than or equal to a predetermined value. The surplus hydraulic fluid can be supplied to the guide member without any problem.

  According to the fourth aspect of the present invention, since the check valve is provided in the oil passage connected to the upper portion of the hydraulic pressure chamber of the hydraulic engagement means, the air remaining in the hydraulic pressure chamber is discharged via the check valve. Can do.

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

  1 to 4 show a first embodiment of the present invention. FIG. 1 is a skeleton diagram of an automatic transmission for a vehicle, FIG. 2 is a velocity diagram of the automatic transmission for a vehicle, and FIG. The principal part expanded sectional view of an automatic transmission, FIG. 4 is a perspective view of a guide member.

  As shown in FIG. 1, an automatic transmission T having eight forward speeds and one reverse speed for a front engine / rear drive vehicle has an input shaft 13 connected to a crankshaft 11 of an engine E via a torque converter 12, A center shaft 36 fitted to the outer periphery of the rear portion (left side in the figure) of the input shaft 13 so as to be relatively rotatable, an output shaft 14 disposed coaxially with the input shaft 13, and a counter shaft 15 disposed parallel to the input shaft 13. The first planetary gear mechanism 16 and the second planetary gear mechanism 17 are disposed on the outer periphery of the input shaft 13 and the center shaft 36.

  The first planetary gear mechanism 16 includes a sun gear 18 fixed to the center shaft 36, a planetary carrier 19 supported on the outer periphery of the center shaft 36 so as to be relatively rotatable, a ring gear 21 fixed to the ring gear carrier 20, A plurality of pinions 22 supported rotatably on the planetary carrier 19, and the pinions 22 mesh with both the sun gear 18 and the ring gear 21.

  The second planetary gear mechanism 17 rotates to the sun gear 23 fixed to the center shaft 36, the planetary carrier 24 fixed to the output shaft 14, the ring gear 26 fixed to the ring gear carrier 25, and the planetary carrier 24. A plurality of pinions 27 that are freely supported are provided, and the pinions 27 mesh with both the sun gear 23 and the ring gear 26.

  The ring gear carrier 20 of the first planetary gear mechanism 16 can be constrained to the casing 28 via the first brake B 1, and the ring gear carrier 25 of the second planetary gear mechanism 17 is connected via the second brake B 2 and the one-way clutch 29. The casing 28 can be restrained. The input shaft 13 can be coupled to the center shaft 36 via the first clutch C1, and the input shaft 13 can be coupled to the planetary carrier 19 of the first planetary gear mechanism 16 via the second clutch C2.

  A first gear 30 fixed to the input shaft 13 meshes with a second gear 31 that is freely supported by the counter shaft 15 via a third clutch C3. The third gear 32 that is detachably supported by the input shaft 13 via the fourth clutch C4 meshes with the fourth gear 33 that is fixed to the counter shaft 15. The fifth gear 34 fixed to the counter shaft 15 meshes with the sixth gear 35 fixed to the ring gear carrier 20 of the first planetary gear mechanism 16.

  Next, the establishment of each gear stage will be described with reference to the speed diagram of the automatic transmission T shown in FIG. 2 and the clutch and brake engagement table shown in Table 1.

  First, establishment of the first forward speed to the fifth forward speed will be described. When the first forward speed to the fifth forward speed are established, the input shaft 13 is coupled to the center shaft 36 by the engagement of the first clutch C1, and the center shaft 36 rotates at the same speed as the input shaft 13.

  When the second brake B2 is engaged and the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17 are non-rotatably constrained to the casing 28 in order to establish the first forward speed, the sun gear fixed to the center shaft 36 is secured. The rotation of the motor 23 is decelerated and transmitted to the planetary carrier 24, and the output shaft 14 integrated with the planetary carrier 24 rotates to establish the first forward speed.

  Further, in order to establish the forward second speed gear stage, when the first brake B1 is engaged and the ring gear carrier 20 and the ring gear 21 of the first planetary gear mechanism 16 are non-rotatably constrained to the casing 28, they are fixed to the center shaft 36. The rotation of the sun gear 18 is decelerated and transmitted from the planetary carrier 19 to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward second speed gear.

  When the fourth clutch C4 is engaged to establish the third forward speed, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, It is transmitted to the ring gear 21 via the ring gear carrier 20 of the sixth gear 35 and the first planetary gear mechanism 16. Then, the planetary carrier 19 is rotated by the differential rotation of the ring gear 21 and the sun gear 18 of the first planetary gear mechanism 16, and the rotation of the planetary carrier 19 is transmitted to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward third gear.

  When the third clutch C3 is engaged to establish the forward fourth speed, the rotation of the input shaft 13 causes the first gear 30, the second gear 31, the third clutch C3, the counter shaft 15, the fifth gear 34, It is transmitted to the ring gear 21 via the ring gear carrier 20 of the sixth gear 35 and the first planetary gear mechanism 16. Then, the planetary carrier 19 is rotated by the differential rotation of the ring gear 21 and the sun gear 18 of the first planetary gear mechanism 16, and the rotation of the planetary carrier 19 is transmitted to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward fourth speed gear.

  When the second clutch C2 is engaged to establish the forward fifth gear, the rotation of the input shaft 13 is directly performed through the second clutch C2 and the planetary carrier 19 of the first planetary gear mechanism 16 as it is. 17 ring gears 26. As a result, the sun gear 23 and the ring gear 26 of the second planetary gear mechanism 17 rotate at the same speed as the input shaft 13, so that the second planetary gear mechanism 17 is locked, and the planetary carrier 24 and the output shaft 14 are input. The fifth forward speed is established by rotating at the same speed as the shaft 13.

  Next, the establishment of the sixth forward speed to the eighth forward speed will be described. At the time of establishment of the sixth forward speed to the eighth forward speed, the second clutch C2 is engaged so that the rotation of the input shaft 13 is performed via the second clutch C2 and the planetary carrier 19 of the first planetary gear mechanism 16. The planetary carrier 19 of the first planetary gear mechanism 16 and the ring gear 26 of the second planetary gear mechanism 17 rotate at the same speed as the input shaft 13.

  When the third clutch C3 is engaged to establish the sixth forward speed, the rotation of the input shaft 13 causes the first gear 30, the second gear 31, the third clutch C3, the counter shaft 15, the fifth gear 34, 6 is transmitted to the ring gear 21 through the ring gear carrier 20 of the first planetary gear mechanism 16. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated, thereby establishing a forward sixth speed.

  When the fourth clutch C4 is engaged to establish the forward seventh speed, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, 6 is transmitted to the ring gear 21 through the ring gear carrier 20 of the first planetary gear mechanism 16. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward seventh speed gear stage.

  When the first brake B1 is engaged to establish the forward eighth speed, the ring gear carrier 20 and the ring gear 21 of the first planetary gear mechanism 16 are restrained to the casing 28 so as not to rotate. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward 8-speed gear stage.

  Next, the establishment of the reverse gear will be described.

  When the fourth clutch C4 is engaged to establish the reverse gear, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, and the sixth gear. 35 and the ring gear carrier 20 of the first planetary gear mechanism 16 is transmitted to the ring gear 21. At the same time, when the second brake B2 is engaged, the ring gear carrier 25 of the second planetary gear mechanism 17 and the planetary carrier 19 of the first planetary gear mechanism 16 are restrained by the casing 28 so as not to rotate. As a result, the sun gear 18 of the first planetary gear mechanism 16 rotates, and the sun gear 23 of the second planetary gear mechanism 17 integral with the sun gear 18 rotates, so that the second planetary gear is rotated by the differential rotation with the stopped ring gear 26. The planetary carrier 24 of the mechanism 17 rotates in the reverse direction, and the output shaft 14 integrated with the planetary carrier 24 rotates in the reverse direction, thereby establishing the reverse gear.

  Next, the structure of the first planetary gear mechanism 16 will be described in detail based on FIG. 3 and FIG.

  The sun gear 18 of the first planetary gear mechanism 16 is splined to the outer periphery of the center shaft 36 supported on the outer periphery of the input shaft 13 via the needle bearing 41. A clutch inner 43 of the second clutch C2 is supported on the outer periphery of the center shaft 36 via a needle bearing 42 so as to be relatively rotatable, and the planetary carrier 19 is spline-coupled to the clutch inner 43. Accordingly, the planetary carrier 19 can rotate relative to the center shaft 36. A pinion shaft 44 is fitted to the planetary carrier 19, and the pinion 22 is rotatably supported on the outer periphery of the pinion shaft 44 via needle bearings 45 and 45. A ring gear hub 47 is supported on the outer periphery of a portion where the planetary carrier 19 is splined to the clutch inner 43 via a needle bearing 46 so as to be relatively rotatable.

  The ring gear hub 47 includes a shaft hole 47a into which the needle bearing 46 is fitted at the center, a plurality of engagement holes 47d... On the outer peripheral side, and a large number of uneven portions 47e. The ring gear 21 meshing with the pinions 22 is provided with a plurality of engaging protrusions 21a projecting on one end side in the axial direction, and the engagement protrusions 21a are engaged with the engaging holes 47d so that the circlip is engaged. By fixing with 48, the ring gear 21 is coupled to the ring gear hub 47. The ring gear 21 is coupled to the ring gear carrier 20 by engaging the uneven portions 47 e formed on the outer peripheral surface of the ring gear hub 47 with the uneven portions 20 a formed on the end portion of the ring gear carrier 20. Further, by engaging a large number of concave and convex portions 19a protruding from the radial outer end of the planetary carrier 19 with a large number of concave and convex portions 25a formed on the inner peripheral surface of the ring gear carrier 25 of the second planetary gear mechanism 17, Planetary carrier 19 is coupled to ring gear carrier 25.

  A thrust bearing 55 is disposed between the ring gear hub 47 and the clutch inner 43, and a thrust bearing 56 is disposed between the planetary carrier 19 and the ring gear hub 47. A thrust bearing 57 is disposed between the two planetary carriers 19 and 24.

  One end of an oil hole 44a is opened on the end surface of the pinion shaft 44 on the side opposite to the ring gear hub 47, and a plurality (four in the embodiment) of oil holes 44b... Penetrate through the oil hole 44a in the radial direction. An oil hole 13b, 13c extending in the radial direction from an oil passage 13a formed in the axial direction inside the input shaft 13 penetrates to the outer peripheral surface, and a center shaft 36 fitted to the outer side in the radial direction via a needle bearing 41. The oil holes 36a and 36b extending in the radial direction pass through to the outer peripheral surface.

  An annular guide member 51 is fixed by a circlip 54 to the end surface of the planetary carrier 19 on the side opposite to the ring gear hub 47.

  As is clear from FIG. 4, the guide member 51 is configured by integrating a generally flat annular first member 52 and an annular second member 53 having a substantially V-shaped cross section. The second member 53 includes an inner guide portion 53a that extends radially inward of the guide member 51 and an outer guide portion 53b that extends radially outward, and is formed at each of the three guide portions 53a and 53b. It welds to the 1st member 52 in welding part 53c .... The first member 52 is formed with three openings 52a at positions facing the oil holes 44a of the three pinion shafts 44, and the inner guide portion 53a and the outer guide portion are formed in the openings 52a. The bent part where 53b continues is facing.

  Next, lubrication of the needle bearings 45 that support the pinions 22 on the pinion shafts 44 will be described.

  The lubricating oil supplied from the oil passage 13 a of the input shaft 13 through the oil hole 13 b lubricates the needle bearing 41, then lubricates the needle bearing 42 through the oil hole 36 a of the center shaft 36, and further oil holes of the clutch inner 43. The needle bearing 46 and the thrust bearings 55 and 56 are lubricated through 43a and the clearance between the planetary carrier 19 and the clutch inner 43. The lubricating oil supplied from the oil passage 13 a of the input shaft 13 through the oil hole 13 c lubricates the thrust bearing 57 through the oil hole 36 b of the center shaft 36 and the oil hole 18 a of the sun gear 18.

  If the planetary carrier 19 is rotating at this time, the lubricating oil that lubricates the thrust bearing 57 and adheres to the planetary carrier 19 is urged radially outward by the centrifugal force of the rotating planetary carrier 19, and the planetary carrier 19. Is captured by the inner guide portion 53a of the second member 53 of the guide member 51 provided in The lubricating oil is guided to the inner guide portion 53a and turned to the right in FIG. 3, and then supplied to the oil holes 44a of the three pinion shafts 44 from the three openings 52a of the first member 52. (See solid arrow). The lubricating oil supplied to the oil holes 44a passes through the oil holes 44b extending in the radial direction from the oil holes 44a, and can lubricate the needle bearings 45, 45 between the pinions 22 and the oil holes 44a.

  As described above, when the planetary carrier 19 is rotating, the lubricating oil adhering to the planetary carrier 19 is urged radially outward by the centrifugal force, so that the needle bearing is operated by the action of the inner guide portion 53a of the guide member 51. 45, 45 can be lubricated.

  By the way, since the planetary carrier 19 of the first planetary gear mechanism 16 stops rotating when the first forward speed and the reverse speed are established, the lubricating oil adhering to the planetary carrier 19 moves radially outward by centrifugal force. No lubrication by centrifugal force can be expected. However, at the time of establishing the first forward speed and the reverse speed where the planetary carrier 19 of the first planetary gear mechanism 16 stops rotating, the needle bearing is utilized using the lubricating oil that stays in the housing 28 and drops by gravity. 45 and 45 are lubricated.

  That is, the lubricating oil that adheres to the planetary carrier 19 that has stopped rotating and flows downward due to gravity is captured by the outer guide portion 53b of the second member 53 of the guide member 51 and guided to the outer guide portion 53b. Are changed from the three openings 52a of the first member 52 to the oil holes 44a of the three pinion shafts 44 (see broken line arrows). The lubricating oil supplied to the oil holes 44a passes through the oil holes 44b extending in the radial direction from the oil holes 44a, and can lubricate the needle bearings 45, 45 between the pinions 22 and the oil holes 44a.

  At this time, the lubricating oil cannot be supplied to the oil hole 44a of the pinion shaft 44 below the axis of the input shaft 13 because the outer guide portion 53b facing the oil hole 44a opens downward. An inner guide portion in which the lubricating oil supplied by gravity from the oil passage 13a of the input shaft 13 through the oil hole 13c is opened upward in the oil hole 44a of the pinion shaft 44 below the axis of the input shaft 13. Since the oil is guided and supplied by 53a, the lubricating oil can be supplied to the oil holes 44a of all the pinion shafts 44 even when the planetary carrier 19 is stopped.

  As described above, when the planetary carrier 19 is stopped and it is difficult to supply the lubricating oil to the oil holes 44a of the pinion shafts 44 by centrifugal force, the lubricating oil dripped by gravity is captured by the guide member 51. Since it is used for lubrication, a means for forming a special lubricating oil passage inside the planetary carrier 19 or supplying the lubricating oil at a high pressure becomes unnecessary, and the planetary carrier 19 is prevented from being enlarged and cost is reduced. Can contribute to down.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment, when the planetary carrier 19 stops rotating, the needle bearings 45, 45 are lubricated by using a part of the hydraulic oil that fastens the second brake B2.

  The second brake B2 includes a brake outer 61 formed integrally with the housing 28, and a plurality of friction engagement elements 62 that are spline-engaged with the ring gear carrier 25, and these friction engagement elements 62 are mutually connected. A brake piston 63 that is urged in a direction to engage with the cylinder part 28 is slidably fitted into a cylinder part 28 a formed in the housing 28. A working hydraulic chamber 64 that urges the brake piston 63 in the engaging direction is defined on the back surface of the brake piston 63, and this working hydraulic chamber 64 communicates with an oil pump (not shown) through an oil passage (not shown). . Therefore, when the hydraulic oil from the oil pump is supplied to the hydraulic pressure chamber 64, the brake piston 63 moves forward against the elastic force of the return spring 65, and the plurality of friction engagement elements 62 are engaged with each other. The second brake B2 is engaged.

  An oil passage 28b extending upward from the upper end of the working hydraulic chamber 64 to the inside of the housing 28 communicates with a check valve 68 having a ball 66 and a spring 67, and further, an oil passage 28c extending laterally from the check valve 68 to the inside of the housing 28. Opens at the top of the first planetary gear mechanism 16.

  The other configuration of the second embodiment is substantially the same as that of the first embodiment described above.

  Thus, when the planetary carrier 19 rotates, the lubricating oil urged radially outward by centrifugal force is applied to the pinion shaft by the inner guide portion 53a of the second member 53 of the guide member 51, as in the first embodiment. 44... Oil holes 44 a.

  On the other hand, when the first forward speed and the reverse speed where the planetary carrier 19 stops rotating are established, the second hydraulic brake B2 is engaged as is apparent from Table 1, so that the hydraulic pressure chamber 64 is pressurized. The hydraulic oil is supplied to urge the brake piston 63 in the engaging direction. At this time, when the hydraulic pressure in the working hydraulic chamber 64 exceeds a predetermined value, the check valve 68 is opened, and a part of the working oil in the working hydraulic chamber 64 passes through the oil passage 28b, the check valve 68, and the oil passage 28c as lubricating oil. And discharged to the upper part of the second planetary gear mechanism 16.

  This lubricating oil adheres to the planetary carrier 19 in which the rotation of the second planetary gear mechanism 16 is stopped and flows downward due to gravity, and as in the first embodiment, the outer guide portion of the second member 53 of the guide member 51. After being caught by 53b and guided by the outer guide portion 53b and turned in the right direction in FIG. 5, the three openings 52a of the first member 52 are changed to the oil holes 44a of the three pinion shafts 44. Supplied (see dashed arrows). The lubricating oil supplied to the oil holes 44a passes through the oil holes 44b extending in the radial direction from the oil holes 44a, and can lubricate the needle bearings 45, 45 between the pinions 22 and the oil holes 44a.

  According to the second embodiment, in addition to the function and effect of the first embodiment, a part of the hydraulic oil that operates the second brake B2 is used as the lubricating oil from the outside in the radial direction of the planetary carrier 19. Thus, the lubricating oil can be reliably supplied even when the planetary carrier 19 is stopped.

  Further, since a part of the hydraulic oil that operates the second brake B2 is supplied to the guide member 51 via the check valve 68 that opens with a hydraulic pressure equal to or higher than a predetermined value, the engagement of the second brake B2 is hindered. The surplus hydraulic oil can be supplied to the guide member 51.

  Moreover, since the check valve 68 is provided in the oil passages 28b and 28c connected to the upper part of the working hydraulic chamber 64 of the second brake B2, the air remaining in the working hydraulic chamber 64 can be discharged through the check valve 68. it can.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

  For example, the shape of the guide member 51 is not limited to the embodiment, and any shape may be used as long as it includes the inner guide portion 53a and the outer guide portion 53b.

Skeleton diagram of automatic transmission for vehicle according to first embodiment Speed diagram of automatic transmission for vehicles Expanded cross-sectional view of the main parts of an automatic transmission for vehicles Perspective view of guide member The figure corresponding to the said FIG. 3 based on 2nd Embodiment.

Explanation of symbols

13 Input shaft (rotating shaft)
16 First planetary gear mechanism (planetary gear mechanism)
18 Sun gear 19 Planetary carrier 21 Ring gear 22 Pinion 28b Oil passage 28c Oil passage 36 Center shaft (rotating shaft)
44 Pinion shaft 44a Oil hole 51 Guide member 53a Inner guide portion 53b Outer guide portion 64 Operating hydraulic chamber 68 Check valve B2 Second brake (hydraulic engagement means)

Claims (4)

A sun gear (18), a planetary carrier (19) and a ring gear (21) are arranged coaxially around the rotation shafts (13, 36), and are supported on the planetary carrier (19) via a pinion shaft (44). ) Is meshed with the sun gear (18) and the ring gear (21), and the pinion is supplied with lubricating oil supplied to an oil hole (44a) formed in the pinion shaft (44). In the lubricating structure of the automatic vehicle transmission that lubricates the sliding surface between the shaft (44) and the pinion (22),
The planetary carrier (19) includes an annular guide member (51), and the lubricating oil supplied from the radially inner side is guided to the oil hole (44a) of the pinion shaft (44). An automatic guide for a vehicle characterized in that an inner guide portion (53a) and an outer guide portion (53b) for guiding lubricating oil supplied from the radially outer side to the oil hole (44a) of the pinion shaft (44) are provided. Transmission lubrication structure.   The guide member (51) is provided with a hydraulic engagement means (B2) for shifting, and a part of the hydraulic oil that operates the hydraulic engagement means (B2) is used as lubricating oil from the outside in the radial direction of the planetary carrier (19). The lubricating structure of the automatic transmission for a vehicle according to claim 1, wherein   A part of the hydraulic oil that operates the hydraulic engagement means (B2) is supplied to the guide member (51) via a check valve (68) that opens with a hydraulic pressure equal to or higher than a predetermined value. The lubricating structure of the automatic transmission for vehicles according to claim 2.   The said check valve (68) is provided in the oil path (28b, 28c) connected to the upper part of the hydraulic_pressure | hydraulic chamber (64) of the said hydraulic engagement means (B2), It is characterized by the above-mentioned. Lubricating structure for automatic transmissions for vehicles.

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