JPH02120573A - Lubricating device in automatic transmission gear - Google Patents

Abstract

PURPOSE:To prevent the abrasion of a clutch plate and the like by interposing a sealing member between a flange member positioned at the farthest outer part of a wet multiple disc clutch and the inner peripheral surface of a drum member, thereby providing the multiple disc clutch with appropriate oil bath lubrication. CONSTITUTION:Oil scattered around a sun gear S1 on the basis of the rotation of an input shaft 5 at the driving time of an automatic transmission gear passes through an oil pore 20 and the like and is received at the inner peripheral side of a clutch drum 12. In this case, because the part between the inner peripheral surface of the clutch drum 12 and the outer peripheral surface of a flange member 9 is closed by means of a sealing member 11, the oil does not flow out in the axial direction but its appropriate quantity is collected in a first clutch C1 part. Accordingly, the first clutch C1 is effectively oil bathed and lubricated with the appropriate quantity of oil. A clutch plate 8 and the like are thus prevented from excessive abrasion owing to the appropriate oil-bath lubrication with the appropirate quantity of oil.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Industrial application field The present invention relates to automatic transmissions installed in automobiles, especially forward
The present invention relates to an automatic transmission having an automatic speed change mechanism, and more particularly to a lubricating device for lubricating a wet multi-disc clutch disposed on a rotating member.

(B) Prior Art Conventionally, the applicant has arranged a plurality of clutches each connected to a plurality of rotating elements and a hydraulic clutch for operating the clutches together at the rear end of an automatic transmission mechanism, and furthermore, these clutches have been arranged. A third clutch and a hydraulic actuator for its operation are arranged in the provided clutch section, and with a slight change,
An automatic transmission has been devised in which a three-speed automatic transmission mechanism can be changed to a four-speed automatic transmission mechanism without increasing costs (see Japanese Patent Application Laid-Open No. 141344/1983).

As shown in FIG. 5, the clutch section 47 of the automatic transmission includes a first clutch C consisting of a wet multi-disc clutch.
1 and a second clutch C2, and is located at the rear end of the automatic transmission mechanism and housed in the transaxle rear cover 17, and the rear end of the input shaft 5 is fitted with the central boss portion 17a of the cover 17. A sleeve portion 5a is provided for the purpose. A clutch drum 1 is attached to the sleeve portion 5a.
2 (flange portion) are integrally connected, and a movable member 7 is fitted to the clutch drum 12 so as to be slidable only in the axial direction by a spline, and a piston member 15 is fitted to the movable member 7 in the axial direction. They are fitted so that they can slide in one direction or another. Furthermore, the movable member 7 constitutes an oil chamber with a cylinder formed from the inner circumferential surface of the clutch drum 12 to constitute a hydraulic actuator 3 for the first clutch C1, and a piston member [5] is the inner circumferential surface of the movable member 7. An oil chamber is formed between the cylinder and the cylinder, and constitutes a hydraulic actuator 4 for the second clutch C2.

Further, the first clutch C1 includes a large number of separator plates 6, clutch plates 8, and a flange member 9 attached to the clutch drum 12 so as to be prevented from moving in the axial direction. It is interposed between a spline formed on the inner circumferential surface of the radial portion and a spline formed on the axially extending portion surface of ring gear R1. Similarly, the second clutch C2 is interposed between a spline formed on the inner peripheral surface of the outer diameter portion of the movable member 7 and a spline formed on the outer peripheral surface of the hub portion 50a fixed to the hollow shaft 50. There is.

(C) Problems to be Solved by the Invention However, in the conventional automatic transmission described above, for example, when the first clutch C1 is activated, centrifugal force is applied from the input shaft 5 to prevent clutch plate wear and heat generation. It is necessary to effectively lubricate the clutch C1 in an oil bath using the oil that is radially scattered by the clutch. Since a gap is formed between the clutch drum and the inner circumferential surface, the oil that is stopped at the inner circumferential surface of the clutch drum flows out in the axial direction from the gap, and an appropriate amount of oil is stored in the clutch 01 part. The clutch C
1 has become difficult to properly bath lubricate.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a lubricating device that solves the above-mentioned problems by closing the gap between the flange member and the inner circumferential surface of the clutch drum to maintain an oil-tight state.

(d) Means for Solving the Problems The present invention has been made in view of the above-mentioned circumstances. For example, as shown in FIG. A drum member (12
), and a wet multi-disc clutch (C1) and a hydraulic actuator (3) for engaging the multi-disc clutch (C1) are arranged on the inner circumferential side of the outer diameter part, and The wet multi-disc clutch (C) is activated by the operation of the hydraulic actuator (3).
1) as appropriate, and connect the input shaft (5) to another rotating element (
R8), the automatic transmission (A) is located at the outermost side of the wet multi-disc clutch (C1) and is mounted so as to be prevented from moving in the axial direction by the drum member (12). between the flange member (9) and the inner peripheral surface of the drum member,
It is characterized by the interposition of a sealing member (11).

and - by way of example, said input shaft (5) has a single planetary gear (13) and a dual planetary gear (14).
It has a planetary gear unit (18) that combines the two planetary gears (13) and (14), and the sun gears (Sl) and carriers (CRI) of these two planetary gears (13) and (14) are integrally connected, and the carrier (CRI ) is connected to the output member (19), and the wet multi-disc clutch is a first (forward) clutch (C1) that is connected from 1st gear to 3rd gear in a directly connected state and released in 4th gear; The input shaft (5) is connected to the ring gear (R1) of the single planetary gear (13) via the first clutch (C1).
Configure it to connect to.

Further, a predetermined number of oil holes (12a) are provided in the drum member (12).
), the oil is stored inside the drum member, and the oil is configured to flow outward in a predetermined amount from the oil hole (12a).

(f) Effect Based on the above configuration, when the automatic transmission (A) is driven, oil that is radially scattered from the input shaft (5) based on centrifugal force is received by the inner circumferential surface of the drum member (12). It will be done. Then, the oil is prevented from flowing out in the axial direction by the seal member (11) interposed between the flange member (9) and the inner circumferential surface of the drum member, so that an appropriate amount of oil is stored and the wet multi-disc clutch ( For example, even if the wet multi-plate clutch is the first clutch (C1) that is released when upshifting to the high-speed 4th gear, the clutch plates that rotate relative to each other at high speed are Proper oil bath lubrication prevents excessive wear.

In addition, since the oil stored for the oil bath lubrication flows out in a predetermined amount to the outside of the drum member from a predetermined number of oil holes (12a) formed in the drum member (12), the clutch (
The heat generated during the operation of C1) is successively dissipated.

Note that the symbols in parentheses are used for reference to contrast with each component in the drawings, and do not limit equivalent configurations.

(F) Embodiments Hereinafter, embodiments of the present invention will be described with reference to the drawings.

First, an outline of the automatic transmission A to which the present invention is applied will be explained with reference to FIG.
A torque converter 26 having a lock-up clutch 25 and a 4-speed forward automatic transmission mechanism 1 are supported on the input shaft 5, and a front axle shaft 23a and 23b are supported on the input shaft 5. An underdrive mechanism 27 is supported, and a front axle shaft 23a,
A front differential device 29 is supported on 23b.

The 4-speed automatic transmission mechanism 1 has a planetary gear unit 18 formed by combining a single planetary gear 13 and a dual planetary gear 14, and the planetary gear unit 18 has the sun gears S1 and carriers CR1 of both planetary gears integrally connected to each other. The pinion that meshes with the sun gear S1 is a long pinion P.
1. Then, the input shaft 5 and the ring gear R1 (small ring gear) of the single planetary gear 13
are connected via a first (forward) clutch C1, and input shaft 5 and sun gear S1 are further connected via a second (reverse) clutch C2. Also,
The sun gear S1 is directly connected and locked by the first brake B1, and its one-way rotation is locked by the second brake B2 via the first one-way clutch F1. Further, the ring gear R2 (large ring gear) of the dual planetary gear 14 is directly locked by the third brake B3, and its one-way rotation is locked by the second one-way clutch F2. And carrier C
RI is connected to a counter drive gear 19 supported by a case bulkhead, and this gear 19 serves as an output member of the four-speed automatic transmission mechanism 1.

The above-mentioned clutches CI, C2 and brakes Bl, B
2. One-way clutches Fl and F2 are the same as those in the 3-speed automatic transmission mechanism, but in this 4-speed automatic transmission mechanism 1,
In addition to the above configuration, a third clutch CO1 connects the input shaft 5 and the large ring gear R2, and a fourth clutch C3 and a third one-way clutch are interposed between the output side member of the clutch CO and the small ring gear R1. When the FO is attached, the underdrive mechanism 27 has one single planetary gear 32, and the carrier CR3 and sun gear S3 of the planetary gear are connected to a fifth (direct)
They are connected via clutch C4. In addition, the sun gear S3 is directly locked by the fourth (underdrive) brake B4, and the fourth one-way clutch F
3 locks the rotation in one direction. A ring gear R3 is connected to a counter driven gear 33 which meshes with the counter drive gear 19 and becomes an input member of the underdrive mechanism 27, and a carrier CR3.
is connected to the counter shaft 22. Further, a reduction gear 35 serving as an output member of the underdrive mechanism 27 is fixed to the counter shaft 22.

Also, front differential equipment! 29 has a differential carrier 36 and left and right side gears 37a, 37b, and a ring gear 39 is fixed to the differential carrier 36, which serves as a gear mount case. The ring gear 39 meshes with the reduction gear 35 to constitute a final reduction mechanism, and left and right side gears 37a and 37b are connected to left and right front axle shafts 23a and 23b, respectively.

Next, the operation of the 4-speed automatic transmission mechanism 1 in the automatic transmission A will be explained with reference to FIG. 4.

The rotation of the engine crankshaft 55 is controlled by the torque converter 26.
or via the lock-up clutch 25 to the input shaft 5. In the first speed state in the D range, the first clutch C1 is in the connected state. In this state, the rotation of the input shaft 5 is transmitted to the small ring gear R1 via the first clutch C1, and in this state, the rotation of the large ring gear R2 is prevented by the second one-way clutch F2. , the common carrier CRI is rotated at a significantly reduced speed in the forward direction while causing the sun gear S1 to idle in the reverse direction, and the rotation is taken out from the counter drive gear 19.

Furthermore, in 1) second gear in the range, the second brake B2 is activated in addition to the first clutch C1 being connected.

Then, rotation of the sun gear S1 is stopped by the operation of the first one-way clutch F1 based on the brake B2,
Therefore, the rotation of the small ring gear R1 from the input shaft 5 decelerates and rotates the carrier CRI in the positive direction while causing the large ring gear R2 to idle in the positive direction.
9, it is taken out as a 2nd speed. In addition, when shifting from 1 to 2, the second
The one-way clutch F2 is switched from the locked state to the overrun state, and shifts are performed smoothly without causing any shift problems due to clutch switching.

In the third speed state in the D range, the third clutch CO and the fourth clutch C3 are connected from the second speed state. Then, it is transmitted from the input shaft 5 to the small ring gear R1 via the first clutch C1 and to the large ring gear R2 via the third clutch CO, and the planetary gear unit 18 rotates integrally, and the direct rotation is caused by the counter rotation. The signal is transmitted to the drive gear 19. Note that during the 2->3 shift, the first one-way clutch F1 is switched from the locked state to the overrun state, and shifts from 1 to 1 are performed smoothly without causing a shift shock due to clutch change.

In addition, in the third speed state, the fourth clutch C3 is connected together with the third clutch Co, and the rotation of the input shaft 5 is controlled by the third clutch CO1, the fourth clutch C3, and the third one-way clutch FO. The small ring gear R is also
The rotation of the input shaft 5 is transmitted to the input shaft 1.

When upshifting from 3rd speed to 4th speed in the D range, first clutch C1 is released. In this state, rotation is exclusively transmitted to the small ring gear R1 through a path via the third clutch CO1, the fourth clutch C3, and the third one-way clutch FO, and in this state, the rotation is transmitted to the small ring gear R1 through the path exclusively via the third clutch CO1, the fourth clutch C3, and the third one-way clutch FO. is activated. Then, the Sangya Sl is stopped even against the reverse torque, and the rotation of the large ring gear R2 transmitted from the input shaft 5 via the third clutch Co overruns the one-way clutch FO and causes the small ring gear R1 to idle at high speed. While carrier CR
1 as an overdrive rotation. On this occasion,
Since the first clutch C1 is in a released state and the gears are changed under the action of the third one-way clutch FO, the shift is performed smoothly without causing a shift shock due to changing grips.

Furthermore, in the engine brake operating state such as 3rd range, 2nd range or lunge, the third brake B3 operates in 1st gear to stop the large ring gear R2 even against reverse torque, and also in 2nd gear. At the time, the first brake B1
is activated to stop sun gear S1 even against reverse torque.

In the reverse range, the second clutch C
2 is connected, and the third brake B3 is activated.

In this state, the rotation of the input shaft 5 is transmitted to the sun gear S1 via the second clutch C2, and in this state, the large ring gear R2 is fixed by the operation of the third brake B3. While the ring gear R1 is being reversed, the carrier CRI is also reversed, and the reverse rotation of the carrier is taken out by the counter drive gear 19.

On the other hand, the underdrive mechanism 27 is connected to the fourth brake B.
4 and/or when the sun gear S3 is stopped by the fourth one-way clutch F3, the rotation from the counter driven gear 33 is transferred from the ring gear R3 to the carrier CR3.
It is extracted as a deceleration (underdrive) rotation. Furthermore, when the fourth clutch B4 is released and the fifth clutch C4 is engaged, the carrier CR3 and the sun gear S
3 are integrated, and direct rotation is taken out to the counter shaft 22.

Then, the automatic transmission A has a forward speed 4 of the 4-speed automatic transmission mechanism 1.
The speed change and the deceleration and direct connection of the underdrive mechanism 27 are appropriately combined to obtain a predetermined speed, and the rotation is transmitted to the front differential device 29 via the reduction gear 35 and the ring gear 39, and further to the left and right flow chart axle shafts. It is transmitted to 23u and 23b.

Next, an embodiment of the automatic transmission A described above will be described with reference to FIG.

The automatic transmission A has an integrated case consisting of a 1-lance axle case 40, a transaxle housing 41, and a rear cover 17, and the case includes an input shaft 5, a counter shaft 22, and a front differential device 3i29.
A ring gear mount case 36 serving as a differential carrier is rotatably supported. A torque converter 26 having a lock-up clutch 25 is disposed on the input shaft 5.
and a four-speed automatic transmission mechanism 1 are disposed, and an underdrive mechanism 27 is disposed on the counter shaft 22. Further, a valve body 44 covered with a side cover 48 is disposed in the transaxle case 40.

The 4-speed automatic transmission mechanism 1 includes a brake section 43, an output section 45, a planetary gear unit 18, and a clutch section 47 arranged in this order in the axial direction rearward from the engine crankshaft 55, and further includes a brake section 43 and a torque converter. An oil pump 49 is disposed between the input shaft 26 and the input shaft 5, and a hollow shaft 5o is supported rotatably by being fitted onto the input shaft 5.

The planetary gear unit 18 includes a single planetary gear 13 and a dual planetary gear 14 (see FIG. 3), and the single planetary gear 13 includes a sun gear S1, a ring gear R1, and a binion P1 that mesh with these gears. The dual planetary gear 14 includes a sun gear S1, a ring gear R2, and a ring gear R2 formed on a hollow shaft 50.
and a carrier CRI that supports a first pinion P that meshes with sun gear S1 and a second pinion P2 that meshes with ring gear R2 so as to mesh with each other. In both of these planetary gears 13 and 14, the sun gear S1 is composed of a single gear having the same number of teeth formed on the hollow shaft 5o, and the carrier CR1 is integrally constructed, and the pinion P
1 is composed of an integrated long pinion.

Further, in the brake part 43, a one-way clutch F1, a first brake B1 consisting of a multi-disc brake, and a second brake B2 consisting of a multi-disc brake are disposed in order from the inner diameter side toward the outer diameter direction. ing. The first one-way clutch F1 has an inner race in which the tip of the hollow shaft 50 is engaged with a spline, and a second brake hub extending radially outward is fixed to the outer race. Further, a first brake hub is fixed to the front side (engine side) of the inner race of the one-way clutch F1. And the oil pump 49
On the rear side of the oil pump cover, a first brake hydraulic actuator 60 and a second brake hydraulic actuator 51 are formed in order from the inner diameter side in an annular manner.

On the other hand, the output section 45 has a counter drive gear 19 located approximately in the center of the 4-speed automatic transmission mechanism 1, and the counter drive gear 19 has a double Cheebird bearing 5
3, and its boss portion is connected to the carrier CRI of the planetary gear unit 18. Further, the outer race of the bearing 53 is splined and fitted to the inner peripheral surface of the case partition 40a, and a second one-way clutch F2 is attached to the outer peripheral surface of the race extension, and a ring gear R2 is attached to the outer race of the bearing 53. A third brake B3 is interposed between the outer periphery and the axle case 40.

As shown in detail in FIG. 1, the clutch section 47 is
It is provided with a first (forward) clutch C1 and a second (reverse) clutch C2, and is located at the rear end of the 4-speed automatic transmission mechanism and housed in the h-lance axle rear cover 17.

In addition, the central boss portion 1 of the rear end portion of the input shaft 5
7a, and a clutch drum 12 is integrally connected to the sleeve portion 5a. Further, a movable member 7 is fitted to the clutch drum 12 by a spline so as to be slidable only in the axial direction, and a piston member 15 is fitted to the movable member 7.

Further, the movable member 7 forms an oil chamber with a cylinder formed from the inner peripheral surface of the clutch drum 12, thereby forming a hydraulic actuator 3 for the first clutch C1.

Further, the piston member 15 forms an oil chamber between the piston member 15 and a cylinder formed from the inner circumferential surface of the movable member, thereby configuring the hydraulic actuator 4 for the second clutch C2. A spring 58 is compressed between the piston member 15 and a member 57 of the spring receiver fixed to the sleeve portion 5a with a snap ring, and the spring 58 is connected to the piston member of both hydraulic actuators 3. 7 and 15 constitute a common return spring. Further, the second clutch C2 is interposed between a spline formed on the inner peripheral surface of the outer diameter portion of the movable member 7 and a spline formed on the outer peripheral surface of the hub portion 50a fixed to the hollow shaft 50.

Furthermore, the first clutch C1 has a clutch drum 12.
A separator plate 6 fitted into a spline formed on the inner circumferential surface of the outer diameter portion of the ring gear R1... A clutch plate 8 fitted into a spline formed on the axially extending portion of the ring gear R1.
..., and a flange member 9 located at the outermost side of the separator plate 6, and the flange member 9 is prevented from being removed by a snap link 10.

On the other hand, the axially extending portion of the ring gear R1 has a predetermined number of oil holes 2 for supplying oil to the first clutch C1.
0... are formed in the outer diameter portion of the clutch drum 12, and a predetermined number of oil holes 12a... are formed in the vicinity of the first clutch C1, and the outer circumferential portion of the flange member 9 A sealing member 11 made of a rubber material is interposed between the clutch drum 12 and the inner circumferential surface of the clutch drum 12. Therefore, the oil scattered by the centrifugal force from the input shaft 5 is removed from the oil hole 20.
The bearing is temporarily stopped on the inner circumferential surface of the clutch drum 12 by passing through the clutch drum 12, and the space between the drum 12 and the flange member 9 is oil-tightly closed by the seal member 11, so that the shaft Instead of flowing out in the direction, an appropriate amount is stored in the first clutch C1 to lubricate the clutch C1 in an oil bath, and a predetermined amount is scattered to the outside of the clutch drum from the oil hole 12a to radiate heat. There is.

The present 4-speed automatic transmission mechanism 1 includes the following devices in addition to the parts common to the above-mentioned 3-speed automatic transmission mechanism.

That is, a sleeve member 75 is fitted into the annular boss portion 17b of the rear cover 17, and a flange member 76 is fixed to the sleeve member 75, forming a cylinder of the hydraulic actuator 54 for the third clutch C4. There is. Further, a groove 70b is formed in the other end portion of the drum member 70 provided on the outer diameter side of the flange member 76 of the hydraulic actuator 54, and a separator plate 92 constituting the fourth clutch C3 is formed in the groove 70b. engaged. and,
Parallel to the inner diameter side of the drum member 70, an annular tube 71 constituting a tension member is installed between the third clutch C3 separator plate and the fourth clutch C3 separator plate 92. . The outer race 100 of the third one-way clutch FO is positioned between the retaining snap ring 10 of the first clutch C1 and the snap link 91 for connecting the drum member through a thrust washer 97.99. is installed.

On the other hand, the underdrive mechanism 27 has one single planetary gear 32, as shown in FIG.

Further, a counter driven gear 33 is rotatably supported on the counter shaft 22 via a bearing 103.
Further, a reduction gear 35 is fixed on the shaft 22. The ring gear R3 of the planetary gear 32 is connected to the counter driven gear 33, and the carrier CR3 supporting the binion P3 is integrally formed with the counter shaft 22 bulging in the outer radial direction. Further, the sun gear S3 is formed on a hub 105 rotatably supported on the shaft 22, and a drum 106 fixed to the outer diameter of the hub has a fourth brake B4 made of a band brake on its outer circumferential surface. engaged. Further, a fifth clutch C4 is interposed between the inner peripheral surface of the drum 106 and a hub fixed to the carrier CR3, and a piston is fitted into the hub 105 adjacent to the clutch C4. This constitutes a hydraulic actuator 107 for clutch C4. Furthermore, a fourth one-way clutch F3 is interposed between the extension of the hub 105 and the case 40.

Further, the front differential device 29 has a ring gear mount case 36 that serves as a differential carrier, and the case 36 is rotatably supported by the housing 41 and the case 40 via bearings. Further, a large-diameter ring gear 39 that meshes with the reduction gear 35 is fixed on the mount case 36, and a pinion gear 111 is rotatably supported inside the ring gear 39 by a pinion shaft 110. Left and right side gears 37a and 37b meshing with the gear 111 are rotatably supported. And the side gear 37a.

Left and right front axle shafts 23a and 23b are fitted and connected to 37b, respectively.

Next, the operation of the above embodiment will be explained.

In the first forward speed state, hydraulic pressure is supplied to the hydraulic actuator 3 through an oil passage formed in the rear cover 17. Then, the movable member 7 uses the clutch drum 12 as a cylinder.
moves against the spring 58, and the first clutch C1
engage. In this state, the rotation of the input shaft 5 is
The rotation is transmitted to the small ring gear R1 via the clutch drum 12 and the first clutch C1, and together with the large ring gear R2 being locked by the second one-way clutch F2, the first speed rotation is taken out from the carrier CRI. Ru. In addition,
When the engine brake is activated, the third brake B3 is activated to directly lock the large ring gear R2. Then, as previously explained with reference to the schematic diagram in FIG. is transmitted to the front differential device 29, and then to the left and right front axle shafts 23a, 23b.

In addition, in the forward second speed state, the hydraulic actuator 5
1 to operate the second brake B2. Then, the first one-way Kura Sochi F1 and the hollow shaft 50
The sun gear S1 is stopped via the first clutch C1, and the rotation of the small ring gear R1 via the first clutch C1 is taken out as second speed rotation from the carrier CRI as described above. In addition, 2
If engine braking is required at high speeds,
Hydraulic pressure is supplied to hydraulic actuator 60 to directly fix sun gear S1.

In the third forward speed, in addition to supplying hydraulic pressure to the hydraulic actuator 3 for the first clutch C1, hydraulic pressure is supplied to the hydraulic actuator 54 through an oil passage formed in the annular boss portion 17b of the rear cover 17. and engages the third clutch CO. As a result, the rotation of the input shaft 5 is transmitted to the large ring gear R2, and together with the rotation of the small ring gear R1 via the first clutch C1, the direct rotation that rotates the gear unit 18 integrally is transmitted to the carrier CR1. taken from.

Furthermore, prior to upshifting to the fourth forward speed, the hydraulic actuator 3 is first drained and the first clutch C1 is released. In this state, the small ring gear R1 is
Power is transmitted exclusively through the third clutch CO, fourth clutch C4, and third one-way clutch FO. In this state, when hydraulic pressure is supplied to the hydraulic actuator 60 to operate the first brake B1 and stop the sun gear S1, the rotation of the input shaft 5 is transferred to the large ring gear via the third clutch CO and the drum member 70. R2
is transmitted to the carrier CRI, causing the small ring gear R1 to idle at high speed while overrunning the one-way clutch FO.
The overdrive rotation is taken from.

In addition, in the reverse range, hydraulic pressure is supplied to the hydraulic actuator 4 through an oil path formed in the rear cover 17, and the movable member 7 is used as a cylinder to move the piston member 15 against the spring 58. At the same time, the third brake B3 is engaged. In this state, the rotation of the input shaft 5 is controlled by the clutch drum 12.
, is transmitted to the sun gear S1 via the movable member 7, the second clutch C2, etc., and is reversely rotated or taken out from the carrier CRI by stopping the large ring gear R2 based on the third brake B3.

When the automatic transmission A is driven, oil scattered around the sun gear S1 based on the rotation of the input shaft 5 passes through oil holes 20 formed in the axially extending portion of the ring gear R1. Then, the receiver is stopped on the inner peripheral side of the clutch drum 12. In this case, the oil is kept in a chamber between the inner circumferential surface of the clutch drum and the outer circumferential surface of the flange member 9 by the seal member 11, so that the oil does not flow out in the axial direction and is properly distributed to the first clutch 01 portion. A large amount can be stored. Therefore, the first clutch C1 is effectively bath lubricated by the appropriate amount of oil. In particular, the clutch C1 is connected from 1st to 3rd gear and released at 4th gear, but even if the separator plate 6 and clutch plate 8 rotate relative to each other at high speed during 4th gear, Since the clutch plates 8 and the like are properly lubricated with the appropriate amount of oil mentioned above, excessive wear does not occur. Further, the oil is allowed to flow out of the clutch drum 12 in a predetermined amount from the oil hole 12a to the outside of the drum for heat radiation.

(G) As described in detail, according to the present invention, a seal is provided between the outermost flange member (9) and the inner peripheral surface of the drum member (12) of the wet multi-disc clutch (C1). Since the member (11) is interposed, an appropriate amount of oil can be stored in the wet multi-disc clutch (C1) without oil flowing out in the axial direction of the drum member (12) that rotates together with the input shaft (5). This makes it possible to properly lubricate the multi-plate clutch (C1) in an oil bath and prevent wear of the clutch plates (8) and the like.

Furthermore, if the wet multi-disc clutch is a first (forward) clutch (C1) that is connected from 1st gear to 3rd gear which is a direct connection state and is released at 4th gear, the clutch (C1) released at 4th gear. Even if the separator plate (6) and clutch plate (8) rotate relative to each other at high speed, excessive wear of the clutch plate (8...) can be prevented by proper oil bath lubrication. This can extend the life of the device.

Further, a predetermined number of oil holes (12a) are provided in the drum member (12).
), and the oil is stored inside the drum member and is configured to flow outward in a predetermined amount from the oil hole (12a), thereby reducing the heat generated during the operation of the wet multi-disc clutch (C1). , can be released sequentially through oil.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing the main parts of a lubricating device in an automatic transmission according to the present invention, FIG. 2 is a cross-sectional view showing the entire automatic transmission, FIG. 3 is a schematic diagram thereof, and FIG. FIG. 3 is a diagram showing the operation of the automatic transmission mechanism. FIG. 5 is a sectional view showing a clutch portion of an automatic transmission that the applicant has already devised. Pressure actuator) 5... Input shaft 9... Flange member 12... Drum member (clutch drum) 12a... Oil hole 11... Seal member
13...Single planetary gear 14...
Dual planetary gear, 18...planetary gear unit

Claims (1)

[Claims] 1. The input shaft has an inner peripheral end of a drum member formed by extending its outer diameter part in the axial direction, and a wet-type polypropylene member is attached to the inner peripheral side of the outer diameter part. An automatic transmission comprising: a plate clutch and a hydraulic actuator for engaging the multi-disc clutch; the wet multi-disc clutch is appropriately engaged by operation of the hydraulic actuator; and the input shaft is connected to another rotating element. A sealing member is interposed between the inner circumferential surface of the drum member and a flange member located at the outermost side of the wet type multi-disc clutch and attached to the drum member so as to be prevented from moving in the axial direction. A lubrication device for an automatic transmission, characterized by: 2. The input shaft has a planetary gear unit that is a combination of a single planetary gear and a dual planetary gear, and the sun gears and carriers of both planetary gears are integrally connected, and the carrier is connected to the output member, and The wet multi-disc clutch includes: 1
Claim 1, wherein the first clutch is connected from speed to third speed, which is a directly connected state, and is released at fourth speed, and the input shaft is connected to a ring gear of a single planetary gear via the first clutch. Lubricating device in the automatic transmission described. 3. Lubricating in an automatic transmission according to claim 1, wherein a predetermined number of oil holes are formed in the drum member, and oil is stored inside the drum member and flows outward in a predetermined amount from the oil holes. Device.