JP2757605B2 - Automatic transmission gear lubrication mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear lubrication mechanism capable of effectively lubricating gears constituting a planetary gear set of an automatic transmission.

[0002]

2. Description of the Related Art In an automatic transmission having a plurality of planetary gear sets, when lubricating the gears constituting each of the planetary gear sets, a method of providing a component (oil catch) for forming an oil reservoir and a method of not providing the component. There is. Here, if a method without an oil catch is adopted, lubricating oil is supplied from the inner peripheral side of the gear through an oil passage in the shaft where the planetary gear set is arranged. Since it is difficult to secure the oil amount, the lubrication efficiency is reduced, and the durability of the bearing part is reduced. For this reason, it is common to provide an oil catch as shown in FIG. FIG. 4 corresponds to FIG. 1 of Japanese Utility Model Application Laid-Open No. 61-6065, in which only one set of planetary gears 81 is shown on a shaft 80, and the planetary gear set adjacent to the left is shown. Omitted. In this conventional example, the planetary gear set 8
The member 82 connected to the first ring gear 81 _R and the carrier 8
1 oil catch 83 is fixed to one end in a space formed between the _{C, the} oil path 80a, oil catch 83 through 80b and the bearing 84 of the lubricating oil shaft 80 which is the axis fueling siege led to the space 85 to be guided into the gear through a further pinion 81 _P axial bore 86 provided in the center of.

[0003]

In the above-mentioned prior art, the space formed between the planetary gear set 81 and the planetary gear set (not shown) adjacent thereto is further divided into a space 85 further partitioned by an oil catch 83 as a dedicated component. due to the planetary gear set 81 oil reservoir for lubricating the interval the oil catch between carrier 81 _C and the member 82 in order to perform an efficient lubrication to ensure the amount of oil in the oil reservoir (volume) required amount or more Can not be packed to the same extent as without
As compared with the case where no oil catch is provided, the axial size of the automatic transmission increases. In particular, when a similar oil catch mechanism is provided also on the planetary gear set (not shown), the axial dimension increases more remarkably (almost twice).

An object of the present invention is to solve the above-mentioned problem by providing a member that blocks between adjacent planetary gear sets to form an oil reservoir common to both planetary gear sets.

[0005]

SUMMARY OF THE INVENTION To this end, a gear lubrication mechanism for an automatic transmission according to the present invention, in an automatic transmission having a plurality of planetary gear sets, is located closer to the outer periphery than a pinion shaft of an adjacent planetary gear set. A member having an axial cross-section that closes a portion between the adjacent planetary gear sets is connected to one of the adjacent planetary gear sets, and a common lubricating oil path communicating with the inside of each pinion shaft of the adjacent planetary gear sets. An oil reservoir is formed.

[0006]

According to the present invention, a member having an axial cross section that closes a portion closer to the outer periphery than the pinion shaft of an adjacent planetary gear set of an automatic transmission is connected to one of the adjacent planetary gear sets. Then, a common oil sump communicating with the lubricating oil passage communicating with the inside of each pinion shaft of each of the adjacent planetary gear sets is formed. An oil sump that can secure a sufficient amount of oil for lubricating the two planetary gear sets can be formed even if the size is reduced to the same size as the case where the member for forming is not provided. Therefore, a lubricating mechanism that simultaneously and efficiently supplies the lubricating oil to the adjacent planetary gear set can be made compact, and the durability of the planetary gear set improves.

[0007]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a partial sectional view showing a first embodiment of a gear lubrication mechanism of an automatic transmission according to the present invention, FIG. 2 is a skeleton diagram of a gear transmission mechanism of the automatic transmission using the same, and FIG. FIG. 1 is a diagram showing an entire configuration of an automatic transmission that has been used. First, FIG.
To explain the entire automatic transmission of this embodiment, the input shaft 1, the output shaft 2 and the intermediate shaft 3 located therebetween are provided in a coaxial butting relationship, and the planetary gear transmission mechanism is concentrically arranged between these input and output shafts. Deploy. The planetary gear transmission mechanism is the first
It comprises a planetary gear set 4, a second planetary gear set 5, and a third planetary gear set 6, and the first planetary gear set 4 includes a first sun gear 4
And _S, and the first ring gear 4 _R, a pinion 4 _P to mesh with the sun gear and the ring gear, a simple planetary gear set comprising more first carrier 4 _C rotatably supporting the pinion 4 _P, likewise the second And the third planetary gear set 5, 6
Are respectively second and third sun gears 5 _S and 6 _S , second and third ring gears 5 _R and 6 _R , pinions 5 _P and 6 _P meshing with these sun gears and ring gears, and these pinions are rotatable. This is a simple planetary gear set including second and third carriers 5 _C and 6 _C to be supported.

[0008] as well as connected to the input shaft 1 to the sun gear 4 _S, the input shaft sun gear 5 _S, 6 _S by the clutch C ₁ 1
Allowing binding to further the carrier 5 _C to allow binding to the input shaft 1 by a clutch C _2. Thereby fixable and by the ring gear 4 _R the first brake (band brake) B _1, the carrier 4 _C and the ring gear 5 _R to be fixed by the second brake B _2, further carrier 5
_C and the ring gear 6 _R can be fixed by the third brake B ₃ , and the carrier 6 _C is connected to the output shaft 2.

In this gear transmission mechanism, the clutches, brakes, and the like are selectively operated by the combinations shown in the following table (the operation states are indicated by circles) to make the first to fifth forward speeds.
Speed and reverse (R) speeds can be obtained (in this case, each shift can be dealt with only by changing one component without the need for double changing of components).

[0010]

Next, the overall structure of the automatic transmission according to this embodiment will be described with reference to FIG. In FIG. 3, reference numerals 1, 2, and 3 denote an input shaft, an output shaft, and an intermediate shaft, respectively. These shafts pass through the central portion of the transmission in the axial direction. A torque converter 7 (only part of which is shown in FIG. 3) is disposed on the left side of the input shaft 1 in the drawing, and an oil pump 8
Is arranged. Also in the right end portion vicinity of the input shaft 1, which corresponds to the clutch C _1, C ₂ in FIG. 2, the clutch 10,1
1 and a first brake (band brake) B _{1 and the} like are arranged, and the right end of the input shaft 1 rotatably supports the intermediate shaft 3. A first planetary gear set 4, a second planetary gear set 5, and a third planetary gear set 6 are arranged in this order over the entire intermediate shaft 3 from the left side in the figure, and a second planetary gear set is arranged on the outer circumference of the planetary gear set. And the third brakes B ₂ and B ₃
Etc. are arranged. On the right side of the intermediate shaft 3, the output shaft 2
, And the left end of the output shaft 2 rotatably supports the intermediate shaft 3. Another is the output shaft 2 of the piston unit and the support wall or the like of the brake B ₃ are arranged, the transmission case 9 is provided on its outermost periphery. This automatic transmission has
Supplying oil control valve 12 is disposed in the first outer circumference of the brake B ₁ in each of the oil passages shown.

Next, each component of the automatic transmission including the gear lubrication mechanism of the present embodiment will be described in more detail with reference to FIG. ₁ , a clutch 1 corresponding to the clutch C1 in FIG.
Reference numeral 0 denotes a clutch drum 13 that is spline-fitted to the input shaft 1, a plurality of clutch plates 14 connected to the clutch drum 13, and a plurality of clutch plates 14 arranged corresponding to the clutch plates and connected to the rotating member 15. The clutch plate 16, a piston 17 which presses these clutch plates to the right in the drawing during hydraulic operation to engage the clutch, a spring 18 for urging the piston 17 in a release direction (leftward in the drawing), and supports the spring 18 And a retainer 19. The clutch 11 which corresponds to the clutch C ₂ in FIG. 2, the clutch drum 20 that is spline-fitted to the inner periphery of the clutch drum 13
A plurality of clutch plates 21 connected to the clutch drum 20; a plurality of clutch plates 23 arranged between the clutch plates and connected to the rotating member 22; And a spring 26 for urging the piston 24 in a release direction (rightward in the drawing), a member 26 for supporting the spring 25 and defining a chamber for generating centrifugal hydraulic pressure. Consisting of: Further, the first brake (band brake) B ₁ has a brake drum 29 supported at one end by an input shaft support wall 27 via a bearing 28, and a maximum diameter portion of the brake drum 29 located closer to the outer periphery than the piston 24. , And the other end of the brake drum 29 is supported by bearings 31 and 32. Note that the clutches 10, 1
1, was placed together on the input shaft 1 of the brake B ₁ or the like, the majority (in this example of the friction element of the planetary gear speed change mechanism 5
(3 of them) are concentrated on this portion, thereby reducing the number of friction elements to be arranged on the intermediate shaft 3 as shown below, and connecting the three planetary gear sets 4, 5, 6 to the intermediate shaft 3. 3 to facilitate layout.

The intermediate shaft 3 is rotatably supported at both ends by an input shaft 1 and an output shaft 2 via bearings 40 and 41, respectively.
The right end of the rotating member 15 is spline-fitted near the left end. In the axial direction, the left side of the intermediate shaft 3 is connected to the clutch drum 13 on the input shaft 1 via the rotating member 15 and the bearing 42, and the right side is connected to the carrier 6 on the output shaft 2 via the sun gear 6 _S and the bearing 43. Supported by _C respectively. The rotary member 22 where the carrier 5 _C splined to the intermediate shaft is rotatably supported through a bearing 44 and 45, the sun gear 5 _S, 6 member with integrated _S sun gear 6 _S
Is spline-fitted to the intermediate shaft 3. In the first to third planetary gear sets 4 to 6 arranged on the intermediate shaft 3 as described above, the sun gear 4 _S of the first planetary gear set 4 has a hole 46 a of a member 46 connected to the right end of the piston 24. , The ring gear 4 _R is interdigitated with the right end of the brake drum 29, the carrier 4 _C is connected to the brake hub 48 of the brake B ₂ , and is also coupled to the ring gear 5 _R of the planetary gear set 5. Carrier 5 _C of second planetary gear set 5
The ring gear 6 of the third planetary gear set 6 has an end (right end) opposed to an end that is spline-fitted to the rotating member 22.
_R , and this ring gear 6 _R is connected to the third brake B ₃
Also serves as a brake hub. Note the output shaft 2 of the carrier 6 _C is splined is supported by the transmission case 9 via a bearing 50.

[0014] The first transmission case 9, on the outer periphery of the second planetary gear set 4, 5 brake drum 5 of the second brake B ₂
1 are fitted and fixed by a snap ring 52 and teeth 9 a provided at several places in the transmission case 9. A plurality of brake plates 53 are connected to the brake drum 51, and a plurality of brake plates 54 arranged corresponding to these brake plates are connected to the brake hub 48.
Further, a piston 55 is slidably supported by the brake drum 51 so as to move leftward against a spring force of a spring (not shown) when the brake is operated. A brake drum 56 is fitted on the outer periphery of the third planetary gear set 6 of the transmission case 9, and is fixed by a snap ring 57 and a detent 58. A plurality of brake plates 59 are connected to the brake drum 56, and the ring gear 6 also serves as a brake hub.
A plurality of brake plates 60 arranged between the brake plates are connected to _R. Incidentally, the piston of the brake B ₃ is arranged separately from the brake drum 56, a piston 61, 62 is slidably supported on the transmission case 9 is formed in the space on the left end of the output shaft 2 ing. These pistons have a double piston structure so as to move leftward against the spring force of the spring 63 when the brake is operated.

In this embodiment, an oil reservoir 70 is formed between the second planetary gear set 5 and the third planetary gear set 6 as shown in FIG. That is, the second planetary gear set 5
The exclusive parts oil catch 71 is coupled by welding or the like which is the portion of the cross-section extends parallel to the axis of the oil catch 71 of L-shaped cross-section for the oil reservoir formed on a side surface of the carrier 5 _C of the overlaps with 3 outer periphery of the carrier 6 _C of the planetary gear set 6. Oil catch 71
And seal 72 is interposed between the carrier 6 _C and the oil reservoir 70 is formed by the seal 72 on the inner peripheral side of the oil catch 71. Incidentally, the oil catch 71 as described above were overlapped to the carrier 6 _C is to absorb the tolerances of the bearing 73 between the planetary gear set 5 and 6.

In the lubrication mechanism of the present embodiment configured as described above, when lubricating oil is supplied from the control valve 12 to the oil passage in the intermediate shaft 3 via an oil passage (not shown), the lubrication mechanism shown in FIG. As shown, the lubricating oil passes through radial oil passages provided in the intermediate shaft 3 and the sun gears 5 _S , 6 _S , the sun gears 5 _S , 6 _S , the carriers 5 _C , 6 _C and the bearing 73.
, And a part thereof flows into the oil sump 70 via the bearing 73. At this time oil sump 7
0 oil catch 71, surrounded by a carrier 5 _C, 6 _C, and the bearing 73, since an independent space having a cross-sectional area illustrated, the oil amount of the oil reservoir (volume) of the planetary gear set 5, In this example in which the distance between the pinions 6 is equal to that without the oil catch, the pinion 5 _P of the planetary gear set 5 and the pinion 6 _P of the planetary gear set 6 are lubricated through axial holes provided at the center of each pinion shaft. Thus, the required amount of oil can be sufficiently satisfied, and an oil sump common to both planetary gear sets can be formed. Therefore, the adjacent planetary gear sets 5, 6 can be simultaneously and efficiently lubricated without increasing the axial dimension of the automatic transmission as compared with the case where the oil catch is not provided. Durability is improved. Incidentally, since the completely dammed between planetary gear set 5 and 6 by the oil catch 71 in this example, located on the outer periphery of the oil catch 71 can supply lubricating oil to the ring gear 6 _R of the planetary gear set 6 eliminated, but configured to supply the lubricating oil from the left space of the piston 61 of the brake B ₃ instead.

[0017]

Thus, as described above, the gear lubrication mechanism of the automatic transmission according to the present invention blocks the pinion shafts of both planetary gear sets by blocking the portion closer to the outer periphery than the pinion shafts of the adjacent planetary gear sets. Since a common oil sump communicating with the communicating lubricating oil passage is formed, the interval between the two planetary gear sets is reduced to the minimum necessary size, that is, the same size as that when the member forming the oil sump is not provided. Also, it is possible to form an oil sump that can secure a sufficient amount of oil for lubrication of both planetary gear sets.
Therefore, a lubricating mechanism that simultaneously and efficiently supplies the lubricating oil to the adjacent planetary gear set can be made compact, and the durability of the planetary gear set improves.

[Brief description of the drawings]

FIG. 1 is a partial sectional view showing a first embodiment of a gear lubrication mechanism for an automatic transmission according to the present invention.

FIG. 2 is a skeleton diagram of a gear transmission mechanism of the automatic transmission using the example.

FIG. 3 is a diagram showing an overall configuration of an automatic transmission using the same example.

FIG. 4 is a diagram for explaining a conventional technique.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 output shaft 3 intermediate shaft 4 first planetary gear set 5 second planetary gear set 6 third planetary gear set 70 oil sump 71 oil catch (member forming oil sump) 72 seal

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-5-33849 (JP, A) JP-A 61-6065 (JP, U) JP-A-3-1353 (JP, U) Field (Int.Cl. ⁶ , DB name) F16H 57/04 F16H 3/66 F16H 3/62

Claims (1)

(57) [Claims] 1. An automatic transmission having a plurality of planetary gear sets, wherein a member having an axial cross section that closes a portion closer to the outer periphery than a pinion shaft of an adjacent planetary gear set is connected to any one of the adjacent planetary gear sets. A lubricating mechanism for an automatic transmission, wherein the lubricating oil passage communicates with a lubricating oil passage communicating with the inside of each pinion shaft of the adjacent planetary gear set. .