JPH02146362A - Lubricating structure for planetary gears of automatic transmission - Google Patents

Abstract

PURPOSE:To perform sure lubrication by constituting a lubricating structure jetting lubricating oil from a fixed member adjacent to planetary gears and receiving this lubricating oil by a receiving member. CONSTITUTION:A shaft 113, supporting a pinion of planetary gears arranged adjacent to a central supporting member 310, has an oil path 113a in the axial direction opened to a side of the member 310 and an oil path 113b in the radial direction opened to a bearing part of the pinion 112, and an annular receiving member 117a for receiving lubricating oil, supplied through the member 310, is mounted to an opening part of the oil path in the axial direction. That is, the lubricating oil, injected through the oil path of the central supporting member 310, is received by the receiving member 117a and introduced into the oil path 113a of the shaft 113 supporting the pinion 112, lubricating its bearing part through the oil path 113b provided in the radial direction. The lubricating oil lubricates a tooth surface of the pinion 112 and its meshed sun gear 111 and a tooth surface of a ring gear 115.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an automatic transmission equipped with a starting device and a planetary gear device.

[Prior Art] In an automatic transmission equipped with a starting device and a planetary gear device,
By arranging multiple rows of planetary gears and the frictional engagement elements that control them within the transmission case, multi-speed shifting can be achieved without increasing the axial dimension. Are known. At this time, the frictional engagement element and the multiple rows of planetary gear devices are connected by a shaft member, but by arranging the multiple rows of planetary gear devices together, the connecting shafts are overlapped concentrically. It is necessary to The plurality of rows of planetary gears are disposed on the outer periphery of the overlapping shafts on the concentric shafts, but it is necessary to provide oil passages for supplying lubricating oil to the planetary gears.

[Problems to be Solved by the Invention] An automatic transmission embodying the present invention has three rows of single-brane gear sets arranged together, and an intermediate shaft with a triple structure that functions as a friction engagement element. By connecting, there are 5 forward speeds and 1 reverse speed.
A multi-speed transmission with multiple speeds has been achieved with a compact axial dimension.

The 3-row simple planetary gear set is arranged on the outer periphery of the connection between the triple intermediate shaft and the output shaft that supports the rear end of the intermediate shaft. Forcible lubrication is provided by providing a radial oil passage that communicates with the oil passage provided at the shaft center. However, since the first row of simple planetary gear sets is arranged around the outer periphery of the triple-structured shaft, it is difficult to arrange an oil passage from the shaft center. Since overdrive is achieved at the highest speed, sufficient lubrication is required.

Therefore, the present invention provides an arrangement structure for a lubricating oil supply oil passage suitable for a planetary gear device having the above structure.

[Means for Solving the Problems] In order to solve the problems described above, the present invention provides a central support member (310) attached to the center interior of a transmission case (300), and a central support member (310). a plurality of frictional engagement elements disposed closer to the starting device, a plurality of rows of planetary gears disposed on a side farther from the starting device than the central support member, a plurality of frictional engagement elements and a plurality of rows of planetary gears. A central support member (310
) The shaft (113) that supports the pinion of the planetary gear set (110) is arranged adjacent to the central support member (310).
An axial oil passage (113a) opening on the side and a pinion (
A radial oil passage (113b) opens to the bearing part of the
), and the opening of the oil passage in the axial direction has an annular receiving member (1) for receiving lubricating oil supplied via the central support member.
17a) to make a profit.

[Function] With the above configuration, the oil passage (11) of the shaft (113) that supports the pinion (112) is received by the receiving member (117a) of the lubricating oil injected through the oil passage of the central support member (310).
3a).

Note that the above-mentioned symbols in parentheses are in contrast to the drawings, but do not limit the configuration in any way.

[Embodiment] FIG. 2 shows a skeleton of an automatic transmission embodying the present invention, and the automatic transmission, which is designated as a whole by reference numeral 1, is equipped with a starting device 2 and a transmission 3.

Launch gear! Reference numeral 2 denotes a fluid transmission device, and a rear cover 204 . A turbine runner 208, which has a pump impeller 20B formed on the inner peripheral wall surface of the rear cover 204 and is disposed opposite to the pump impeller 206, is held by a turbine shell 210, and is
0 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3.

A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the outer race of the one-way clutch 216, and the inner race of the one-way clutch 216 is a fixed member. It is attached to the outer periphery of the support shaft 230. A lock-up clutch 220 that directly connects the front cover 202 and the turbine shell 210 is disposed between the front cover 202 and the turbine shell 210.

The input shaft 240 of the transmission 3 is connected to a clutch drum, generally designated by the reference numeral 400, and three clutches are disposed inside the clutch drum. In this embodiment, three clutches are connected from the front side of the transmission (hereinafter, the engine side will be referred to as the front, and the side far from the engine will be referred to as the rear), and a fifth clutch 15, which is a coast clutch. The first clutch 11 is a forward clutch. The second clutch 12, which is a direct clutch, is arranged in this order. Another drum 470 is arranged at the rear of the clutch drum 400, and the clutch drum 4
A third clutch 13, which is a reverse clutch, is disposed between the hub 445 that connects the drum 400 and the third clutch 13. A band-type second brake 22 for controlling the forward gear is provided on the outer periphery of the drum 470.

The hub of the fifth clutch 15 is connected to the front end of a first intermediate shaft 500 disposed at the axial center of the transmission 3, and the hub of the first clutch 11 is connected via the first one-way clutch 31. It is connected to the first intermediate shaft 500 . The front end of the first intermediate shaft 500 is supported by the rear end of the input shaft 240, and the rear end of the first intermediate shaft 500 is supported by the front end of an output shaft 700, which will be described later. The outer periphery of the first intermediate shaft 500 supports the inner periphery of a coaxially arranged second intermediate shaft 550 at two supporting points, and the outer periphery of the second intermediate shaft 550 is coaxially arranged. The inner peripheral portion of the third intermediate shaft 600 is supported by two fulcrums. Therefore, the intermediate shaft has a triple shaft structure.

The hub of the second clutch 12 is connected to the front end of the second intermediate shaft 550, and the hub of the second clutch 12 is connected to the front end of the second intermediate shaft 550.
The second drum 470 is connected to the third drum through an inner cylinder 480.
is connected to the front end of the intermediate shaft 600 of.

A planetary gear device is disposed on the outer periphery of the connecting portion between the intermediate shaft and the output shaft. The planetary gear device has a simple planetary gear set with three rows, and from the front side of the transmission 3, the first row, second row,
The sun gear 111 of the 6 first row simple planetary gear sets 110 arranged in the order of the third row is connected to the third intermediate shaft 60.
One end portion of the carrier shaft 113 that is connected to the carrier shaft 113 and meshes with the pinion 112 and supports the pinion 112 is connected to the rear end portion of the second intermediate shaft 550 via the carrier connecting member 114. The other end of the carrier shaft 113 is connected to the ring gear 125 of the second row simple planetary gear set 120 via a first connection member 150, and further connected to the second one-way clutch 32 via a second connection member 160. The outer race of the fourth clutch 14 is connected to the hub of the fourth clutch 14. A multi-plate third brake 23 is disposed on the outer periphery of the connecting member 150.

The rear end of the first intermediate shaft 500 is connected to a sun gear 121 of a second row of simple planetary gear sets, and this second row sun gear 121 has a larger outer diameter than the first row sun gear 111. The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 and ring gear 125 of the second row is connected to the ring gear 115 of the first row via the carrier connecting member 116, and the rear end of the shaft 123 is connected to the ring gear 115 of the first row. It is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

Inner cylinder 800 integrated with third row sun gear 131
is connected to the inner race of the second one-way clutch 32 and the third one-way clutch 33, and is also connected to the clutch drum 830 of the fourth clutch 14. This clutch drum 830 also serves as a brake drum for the band-type first brake 21.

A carrier shaft 133 supporting the third row of pinions 132
is coupled to the output shaft 700 via the carrier coupling portion 136.

FIG. 1 is a sectional view showing a specific structure of the automatic transmission having the skeleton explained in FIG.

The starting device 2 that constitutes the automatic transmission 1 is a fluid transmission device, and includes a housing 200 that opens on the engine side (front side).
is housed inside. A carrier cover 204 is integrally attached to the rear of the front cover 202, which rotates in response to the beating of the engine.

A pump impeller 206 is mounted on the inner peripheral wall of the rear cover 204.
A turbine runner 208 is formed and disposed opposite the pump impeller 206 and is held in a turbine shell 210. The turbine shell 210 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3 via a connecting member 211 .

A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the outer race 215 of the one-way clutch 216, and the inner race 2 of the one-way clutch 216.
Reference numeral 17 is attached to the front end outer peripheral part of the support tube 230.

A lock-up clutch 220 having a lock-up piston 222 is disposed between the front cover 202 and the turbine shell 210.

A cylindrical case 300 that houses the components of the transmission 3 is connected to the rear of the housing 200, and an oil pump cover 250 and a partition plate 270 are connected to the joint between the housing 200 and the transmission case 300. Attach the oil pump housing 260. An internal gear pump consisting of an external gear 262 and an internal gear 264 is accommodated within the oil pump housing 260, and the inner peripheral portion of the external gear 262 is connected to a shaft 266 that is integral with the carrier cover 204. The center portion of the oil pump cover 250 forms a cylindrical support portion 252 that protrudes rearward, and the rear outer circumference of the support tube 230 is press-fitted and fixed into the inner circumference of the support portion 252.

Support cylinder 230 (supports the input shaft at two fulcrums on the other inner circumference, and the rear end of the input shaft forms a radially expanding flange. The outer circumference of the flange is connected to the first clutch drum 4
00 is connected to the rear end inner circumferential portion of an inner cylinder 410 that is integrated with the inner cylinder 410. The first clutch 11 and the fifth clutch 15 are housed inside the first clutch drum 400, and a piston 420 for operating the first clutch 11 and a piston 430 for operating the fifth clutch 15 are arranged as a double piston. placed in the structure.

The rear end of the first clutch drum 400 opens rearward, and the second clutch drum 440 is connected via a spline formed on the inner circumference of this opening. Inside the second clutch drum 440, the second clutch 12 and the second clutch 12 are disposed.
A piston 450 for operating the clutch 12 is provided.

The inner circumference of the rear end of the input shaft 240 is connected to the first
supports the outer periphery of the distal end of the intermediate shaft 500.

A radially expanding flange portion 510 is formed at the front portion of the first intermediate shaft 500, and constitutes an inner race of the one-way clutch. This flange portion 510 and the first clutch 11
A first one-sided clutch 31 is disposed between the hub 520 and the hub 520. The front end of this flange portion 510 has a fifth
The hub 435 of the clutch 15 is fixed.

A hub 455 of the second clutch 12 housed within the second clutch drum 440 is connected to the front end of the second intermediate shaft 550. The second intermediate shaft 550 has a cylindrical shape, and the outer peripheral portion of the first intermediate shaft 500 supports two fulcrums at the front and rear of its inner peripheral portion. A clutch hub 445 is provided at the rear of the second clutch drum 440, and the third clutch 13 is provided between the third clutch drum 470 and the inner cylinder of the drum 470. A piston 490 is housed between the piston 480 and the piston 480 . The drum 470 also serves as a brake drum for the band-type second brake 22. A front end portion of the inner cylinder 480 is connected to the third intermediate shaft 600 via a connecting member 610.

The third intermediate shaft 600 has a cylindrical shape, and two supporting points at the front and rear of its inner circumference are supported by the outer circumference of the second intermediate shaft 550.

A central support member 3 is installed in the center of the transmission case 300.
Get 10. The central support member 310 has an outer circumferential portion joined to an inner circumferential portion of the transmission case, and a central portion formed into a cylindrical portion that protrudes forward. The ring member 310 is press-fitted into the outer peripheral part of the cylindrical part that protrudes forward, and the ring member 31
The inner circumferential portion of the inner cylinder 480 of the third clutch drum 470 is rotatably supported by the outer circumferential portion of the third clutch drum 470 .

The intermediate shaft having a triple structure extends rearward through the inner circumference of the central support member 310, and the outer circumference of the rear end of the first intermediate shaft 500 is supported by the inner circumference of the tip of the output shaft 700. At the rear of the transmission case 300, the rear 4? &a a o, and the rear support member 350 is fixed to the inner peripheral portion of the rear wall 330. This rear support member 350 is connected to the case 3 of the transmission.
00 has a cylindrical portion that protrudes toward the front, and the outer diameter of the cylindrical portion is formed into a plurality of stepped portions whose outer diameters are sequentially tapered toward the front. The inner circumferential portion of the front end of the cylindrical portion of the support member 350 supports the outer circumferential portion of the front portion of the output shaft 700 .

A spigot engagement portion 360 is provided at the rear end of the transmission case 300.
The inner periphery of the rear end of the rear case 370, which is concentrically fitted through the rear case 370, supports the rear outer periphery of the output shaft 700 via a bearing. therefore.

The output shaft 700 is reliably supported by two supporting points, and the first intermediate shaft 500 has its front and rear ends connected to the input shaft 240 and the output shaft 7.
00 is definitely supported.

As explained in the skeleton of FIG. 2, three rows of simple planetary gear sets are arranged on the outer periphery of the connecting portion between the triple-structured intermediate shafts 500, 550, 600 and the output shaft 700. A first row of sun gear 111 is formed at the rear end of the third intermediate shaft 600 supported on the outermost side, and a pinion 112
The shaft 11 of the carrier supporting the pinion 112 meshing with the
The inner circumferential portion of the carrier connecting member 114 supporting one end of the second intermediate shaft 550 is attached to the outer circumferential portion of the rear end of the second intermediate shaft 550 via a spline. The carrier connecting member 117 that supports the other end of the carrier shaft 113 is a first connecting member 150.
It is connected to the second row ring gear 125 via. Second
The row ring gear 125 is further connected to the outer race 810 of the second one-way clutch 32 via a second connection member 160. A multi-plate third brake 23 is disposed on the outer periphery of the first connecting member 150, and a piston 650 for operating the brake 23 is disposed on the rear wall of the central support member 310.

A second row of sun gears 121 is connected to the rear outer peripheral portion of the first intermediate shaft 500 . This second row of sun gear 121 is
The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 of the second row and the ring gear 125, which has a larger outer diameter than the sun gear 111 of the row, is connected to the sun gear 111 of the first row through the connecting member 116 of the carrier. ring gear 115
The rear end of the shaft 123 is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

The third row sun gear 131 has its rear end connected to the inner race 870 of the second one-way clutch and also connected to the inner race 820 of the third one-way clutch 33 via the inner cylinder 800 .

A drum 830 formed opposite to the inner cylinder 800
The fourth clutch 14 and a piston 880 for operating the fourth clutch 14 are housed inside, and the clutch hub 815 is connected to the outer race 810 of the second one-way clutch 32 . A band-type first brake 21 is disposed on the outer periphery of the clutch drum 830, and the clutch drum 830 is connected to the brake 21.
Also serves as the brake drum. Third one-way clutch 33
The outer periphery of the outer race 840 is the transmission case 300.
is fixed to the inner wall of the

A carrier shaft 133 supporting the third row of pinions 132
is supported by a connecting portion 136 formed at the front end of the output shaft 700. A parking gear 710 and a speedometer drive gear 730 are attached to the outer periphery of the output shaft 700 inside the rear case 370, and a claw 720 that connects to the gear 710 is provided on the outside of the parking gear 710. . A connecting member 750 is attached to the rear end of the output shaft using a nut 7.
Fixed at 55.

Rotation sensors 305 and 3 for detecting the rotation speed of rotating members are installed in the main parts inside the transmission case 300 and rear case 370.
06, 307 to obtain information for controlling the frictional engagement elements.

A hydraulic control device (not shown) is attached to the bottom of the transmission case 300 and covered with a cover 309 that also serves as an oil pan.

As described above, this automatic transmission is equipped with a 3-row simple planetary gear set as a planetary gear device, and uses 5 clutches, 3 brakes, and 3 one-way clutches to achieve 5 forward speeds and 1 reverse speed. The operation of each friction engagement element is shown below.

In the above table, the ○ mark indicates that the frictional engagement element engages, and the (0) mark indicates that it engages during engine braking.6 The present invention has the above configuration. This is an oil passage structure of a planetary gear implemented in an automatic transmission, and FIG. 3 shows a cross-sectional structure of the main part thereof.

As explained in Figs. 1 and 2, case 3 of the transmission
Inside the 00, three intermediate shafts 500°, 550, and 600 are arranged in a triple structure, and the first intermediate shaft 50 is arranged in the center.
The rear end outer circumferential portion of the output shaft 700 is supported by the tip inner circumferential portion of the output shaft 700. The rear end of the first intermediate shaft 500 is connected to the sun gear 121 of the second row of simple planetary gear sets, and the rear end of the second intermediate shaft 550, which is disposed concentrically around the outer periphery of the first intermediate shaft, is connected to the sun gear 121 of the second row of simple planetary gear sets. The pinion 112 is connected to the pinion 112 via a connecting member 114 that constitutes a carrier of a single-row simple planetary gear set.
It is connected to a shaft 113 that supports the. Second intermediate shaft 550
A sun gear 111 of the first row of simple planetary gear sets is integrally formed at the rear end of the third intermediate shaft 600, which is disposed concentrically on the outer periphery of the third intermediate shaft 600. A shaft 133 supporting a pinion 132 constituting a carrier of the third row of simple planetary gear sets is connected to an output shaft 700 via a connecting portion 136. The shaft 113 of the first row of carriers is connected to the second row of ring gears 125 via the shaft end side connecting member 117 and the first connecting member 150, and further via the second connecting member 160 to the third ring gear 125. connected to the sun gear of the column.

Further, the ring gear 115 in the first row is connected to the pinion 1 in the second row.
The connecting member 1 is connected to a shaft 123 supporting the connecting member 1
26 to the third row ring gear 135.

By combining these three rows of simple planetary gear sets, five forward speeds and one reverse speed are achieved.

A central support member 310 that supports the frictional engagement element is installed inside the center of the transmission case 300.

The center shaft side of the central support member 310 is formed into a cylindrical portion 312 that protrudes toward the front of the transmission, and a clutch drum that accommodates the third clutch 13, which is a reverse clutch, is formed on the outer periphery of the cylindrical portion 312 via a ring member 320. 470 inner drums 480 are supported. Moreover, this central support member 31
A piston 650 for operating a multi-plate third brake 23 is disposed on the rear wall of the vehicle.

In the automatic transmission of the present invention, a frictional engagement element is arranged in the front part of the transmission case, and a three-row simple planetary gear set is arranged in the rear part, and a triple-structured intermediate shaft is connected between the two. Although it is possible to shorten the axial dimension by connecting the gears, consideration must be given to the lubrication structure of the planetary gear set.

The lubrication of the simple planetary gear set with two rows of gruel is as follows:
An oil passage 500b is provided in the radial direction from a lubricating oil passage 505 provided at the center of the intermediate shaft 500 of the carrier.
Lubricating oil can be sent to the oil passage of the shaft 123 through the oil passage 126b formed in the shaft 123 to forcibly lubricate the second row simple planetary gear set. Similarly, in the case of the third row simple planetary gear set, the oil passage 50 in the radial direction
0d and the oil passage 136a of the connecting portion 136 are communicated, and the shaft 133
Forced lubrication is possible through the oil passage.

On the other hand, in the case of the first row of simple planetary gear sets, the third intermediate shaft 6, which is the outermost shaft of the triple structure,
Because it is arranged on the outer periphery of 00.

It is difficult to arrange a lubricating oil passage from the oil passage 505 of the axial center of the first intermediate shaft 500.

Therefore, in the present invention, a lubricating oil passage is provided using a central support member 310 fixed within the transmission case 300. The central support member 310 is a support member for a clutch drum, etc., and is also a member for arranging a plurality of oil passages for supplying hydraulic pressure to pistons that operate clutches and brakes.

The radial oil passage 310a is an oil passage for lubrication, and communicates with a lubricating oil supply source (not shown). Radial oil passage 31
The inner radial end of Oa communicates with an oil passage 310b provided in the axial direction. This axial oil passage 310b has a nozzle 310d that opens toward the first row of simple planetary gear sets, and spouts lubricating oil toward the carrier connecting member 117.

A lubricating oil receiving member 117a made of a ring-shaped plate is attached to the connecting member 117.
'lIJ lubricating oil is received in the gap formed between a and the connecting member 117. On the other hand, the carrier shaft 113 has an axial oil passage 11.
3a is provided, and the lubricating oil received by the receiving member 117a is transferred to the oil path 1.
13a, and lubricates the bearing portion of the pinion 112 via an oil passage 113b provided in the radial direction. The lubricating oil lubricates the tooth surface of the pinion 112, the tooth surface of the sun gear 111 that meshes with the pinion 112, and the tooth surface of the ring gear 115.

The second intermediate shaft, which is integrated with the carrier of the simple planetary gear set in the first row, has three
The input rotation is transmitted in 1st, 4th, and 5th speeds. Due to this rotation, the shaft 113 of the carrier is subjected to centrifugal force, and negative pressure is generated in the oil passage 113b formed on the outside in the radial direction, so that the lubricating oil in the oil passage 113a is jetted out to the bearing portion. Therefore, forced lubrication is achieved in the third to fifth gears where the first row of simple planetary gear sets participates in power transmission. In particular, in the fifth speed, the pinion 112 rotates relatively, and even at this time, sufficient lubricating oil is supplied to the meshing tooth surfaces.

[Effects of the Invention] Since the present invention is configured as described above, an automatic transmission is provided that can achieve multiple stages by using multiple rows of tim gear devices and can make the axial dimension compact by using a multiplex structure for power transmission shafts. In this machine, as a lubrication structure for a planetary gear set disposed on the outer periphery of a shaft member having a multiplex structure, lubricating oil is injected from a fixed member adjacent to the planetary gear set, and this lubricating oil is received by a receiving member. Therefore, reliable lubrication can be achieved.

Additionally, negative pressure can be generated by utilizing the centrifugal force generated by the rotation of the planetary gear device to achieve incidental lubrication.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of an automatic transmission embodying the invention, FIG. 2 is an explanatory diagram showing a skeleton, and FIG. 3 is a sectional view of essential parts showing an embodiment of the invention. 1... automatic transmission, 2... starting device, 3... transmission. 111... Sun gear of the first row of simple planetary gear sets, 112... Pinion of the first row of simple planetary gear sets, 113... Carrier of the first row of simple planetary gear sets. shaft, 117... First row simple planetary gear set carrier connection member, 117a... Lubricating oil receiving member, 310...
...Central support member.

Claims (1)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear device, a central support member installed inside the center of a case of the transmission, and a plurality of frictional engagement elements arranged closer to the starting device than the central support member. , comprising a plurality of rows of planetary gear devices disposed on the side farther from the starting device than the center support member, and a shaft member with a multilayer structure that connects the plurality of frictional engagement elements and the plurality of rows of planetary gear devices; The shaft that supports the pinion of the planetary gear set adjacent to the member has an axial oil passage that opens toward the central support member and a radial oil passage that opens to the pinion bearing. A lubrication structure for a planetary gear device of an automatic transmission, characterized in that an annular receiving member for receiving lubricating oil supplied via a central support member is attached to the opening of the oil passage.