JP5130814B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission mounted on, for example, a vehicle, and more particularly to an automatic transmission including two clutches that are overlapped in the axial direction and arranged at different positions in the radial direction.

  Recently, an automatic transmission mounted on a vehicle has been multi-staged, for example, forward 8 speed, and many components such as a clutch can be arranged compactly from the viewpoint of vehicle mounting. It has been demanded.

  Conventionally, two clutches with one input / output member in common and the other in the other are overlapped in the axial direction and arranged at different positions in the radial direction to achieve compactness, particularly in the axial direction. An automatic transmission has been proposed (see Patent Document 1). In the two clutches, a friction plate composed of multiple plates, a hydraulic servo that operates these friction plates, and a cancel oil chamber that cancels the centrifugal hydraulic pressure of the hydraulic chamber of the hydraulic servo are arranged to overlap each other in the axial direction. .

  The two hydraulic servos and the cancel oil chamber are arranged in a clutch drum integrated with the turbine shaft, and hydraulic pressure is supplied to the two hydraulic servos through oil holes formed in the clutch drum. Is done. In particular, the hydraulic servo on the outer diameter side is supplied with hydraulic pressure through an oil passage formed independently on the outer side of the clutch drum on the inner diameter side and an oil passage formed on the clutch drum on the inner diameter side.

  Of the two cancel oil chambers, the oil oil is directly supplied to the cancel oil chamber on the inner diameter side through an oil hole formed in the boss portion of the clutch drum, and the cancel oil chamber on the outer diameter side is supplied to the cancel oil chamber. The oil in the cancel oil chamber on the inner diameter side is supplied through an oil path provided in the piston of the inner diameter side clutch and an oil path formed in the inner diameter side clutch drum as the fixing member.

JP-A-7-269665

  The above two clutches are shortened in the axial direction by overlapping in the axial direction at different positions in the radial direction, but there are oil passages for supplying hydraulic pressure (or oil) to the hydraulic servo and the canceling oil chamber. It was getting complicated.

  In particular, in order to supply hydraulic pressure to the outer diameter side hydraulic servo, the inner diameter side clutch drum is used as a fixed member, and an independent oil path is formed on the outer side thereof, and the oil path formed on the inner diameter side clutch drum is The oil pressure must be supplied through the system, resulting in a complicated oil passage configuration.

  SUMMARY OF THE INVENTION An object of the present invention is to provide an automatic transmission that solves the above-described problems with a compact configuration, in particular, a compact configuration in the axial direction and a simple oil passage configuration.

The present invention includes two clutches (C3, C4) each having friction plates (21, 41) that are overlapped in the axial direction and arranged at different positions in the radial direction, and each of the two clutches includes a clutch drum. (22, 42), pistons (24, 44) constituting a hydraulic servo (20, 40) using a part of the clutch drum as a cylinder, and a plurality of friction plates (21, 41) engaged with the clutch drum And a cancel oil chamber (28, 48) disposed on the back side of the piston and canceling the centrifugal oil pressure acting on the hydraulic servo,
Of the two clutches, the hydraulic servo (20) and the cancel oil chamber (28) of one clutch (C3) located on the outer diameter side are the hydraulic pressures of the other clutch (C4) located on the inner diameter side. It is arranged on the outer diameter side with respect to the servo (40) and the cancel oil chamber (48),
The clutch drum (22) of the one clutch (C3) includes an inner peripheral side member (22 ₁ ) having a boss portion (22c) and a piston support portion (22e), a drum portion (22a), and a bottom portion (22b). An outer peripheral side member (22 ₂ ) having a single body,
The piston support portion (22e) includes a plurality of protrusions (72) protruding toward the clutch drum (42) of the other clutch (C4) and extending in the radial direction,
In the gap between the piston support portion (22e) of the inner peripheral side member (21 ₁ ) and the bottom portion (22b) of the outer peripheral side member (22 ₂ ) and the protrusion (72), the one clutch Form oil passages (B, b) for supplying and discharging hydraulic pressure to the hydraulic servo (20) of (C3) ,
Cancellation oil of the one clutch (C3) between the piston support portion (22e) including the circumferential portion of the plurality of protrusions (72) and the clutch drum (42) of the other clutch (C4) Forming a space (A ′) for supplying oil to the chamber (28);
The oil passage (b) in the protrusion (72) and the space (A ′) between the circumferential directions of the protrusion (72) are arranged so as to overlap in the axial direction.
It is in the automatic transmission characterized by this.

Hereinafter, each aspect of the present invention will be described. The clutch drum (22) of the one clutch (C3) is disposed so as to contain the clutch drum (42) of the other clutch (C4),
The oil passage (74, B) is formed between the bottom portion (22b) of the outer peripheral member (22 ₂ ) and the piston support portion (22e) of the inner peripheral member (22 ₁ ) .

Before provided with a groove (74) on the inner wall (73) which faces the inner circumference side member of the Kigaishu side member (22 ₂₎ (22 _1), grooves (74), formed by forming the oil passage.

With a gap (B) between the front Symbol inner circumference side member (22 ₁₎ and said outer peripheral member (22 _2), the gap (B) is formed by forming the oil passage.

The boss of the front Symbol inner circumference side member (22 ₁₎ (22c), the oil passage oil hole communicating with the (74, B) and (b), the one of the cancel oil chamber of the clutch (C3) (28 ) Is provided with an oil hole (a) for supplying oil with a phase shifted in the circumferential direction .

Before Symbol inner circumference side member (22 _1), comprising a plurality of projections ribbed for projecting toward the clutch drum (42) of the other clutch (C4) (72),
The oil hole (b) is built in the protrusion, and the opening (b ₂ ) of the oil hole (b) and the groove (74) are arranged to be aligned .

Before SL other clutch boss portion of the clutch drum (42) the inner circumference side member (22 ₁₎ of the (C4) (22c) the piston (44) and fitted the other hydraulic servo (C4) Configure
Oil holes (c) for supplying and discharging hydraulic pressure to the other hydraulic servo (40) are formed at a plurality of locations in the inner circumferential direction of the boss portion (22c) .

Input shaft Input rotation from driving dynamic source is input (7),
A first sun gear (S1) that is rotationally fixed to a fixing member (6) that is integral with the case, a first carrier (CR1) that is coupled to the input shaft, and a first sun gear that is rotationally fixed. (S1) and a first planetary gear (DP) comprising a first ring gear (R1) that outputs a reduced rotation by the first carrier (CR1) to which an input rotation is input,
A second sun gear (S2) that inputs a reduced rotation of the first ring gear (R1) by engagement of the first clutch (C1), and a first ring gear by engagement of the third clutch (C3). The decelerated rotation of (R1) is input, and the rotation of the input shaft via the first carrier (CR1) is input by the engagement of the fourth clutch (C4), and the first brake (B1) A third sun gear (S3) whose rotation is fixed by the locking of the first pin, a long pinion (P3) meshing with the third sun gear (S3), the long pinion (P3) and the second sun gear (S2) Has a short pinion (P4) that meshes with the second brake (B2), and the rotation is fixed by the engagement of the second brake (B2), and the rotation of the input shaft (7) is input by the engagement of the second clutch (C2). Second carrier ( And R2), while meshed with the long pinion (P3), with a second ring gear which is rotatably connected to the output member (8) (R2), a planetary gear set (PU) consisting of,
The one clutch is the third clutch (C3),
The other clutch is the fourth clutch (C4);
While engaging the first clutch (C1) and locking the second brake (B2), the first forward speed is achieved.
While engaging the first clutch (C1) and engaging the first brake (B1), the second forward speed is achieved.
By engaging the first clutch (C1) and the third clutch (C3), the third forward speed is achieved.
By engaging the first clutch (C1) and the fourth clutch (C4), the fourth forward speed is established.
By engaging the first clutch (C1) and the second clutch (C2), the fifth forward speed is established.
By engaging the second clutch (C2) and the fourth clutch (C4), the sixth forward speed is established.
By engaging the second clutch (C2) and the third clutch (C3), the seventh forward speed is achieved.
Engage the second clutch (C2) and lock the first brake (B1) to achieve the eighth forward speed,
The reverse gear is achieved by engaging the third clutch (C3) or the fourth clutch (C4) and engaging the second brake (B2) .

  In addition, although the code | symbol etc. in a parenthesis is for contrast with drawing, it does not have any influence on a claim by this.

  According to the first aspect of the present invention, the clutch unit and thus the automatic transmission can be compactly formed in the axial direction by arranging two clutches at positions that overlap in the axial direction and differ in the radial direction. While being possible, the hydraulic servo and cancellation oil chamber of one clutch located on the outer diameter side are arranged on the outer diameter side with respect to the hydraulic servo and cancellation oil chamber of the other clutch located on the inner diameter side, By supplying and discharging hydraulic pressure to the hydraulic servo of the one clutch through an oil passage formed between the inner peripheral member and the outer peripheral member of the clutch drum of the one clutch, an oil passage with a simple configuration can be obtained. The hydraulic pressure can be quickly supplied to the hydraulic servo of the one clutch, and the outer peripheral side member and the inner peripheral side member are integrally formed to form a clutch. It is also possible to achieve the axial further shortened.

Hereafter, the effect by each aspect of this invention is shown. The axial dimension of the automatic transmission is obtained by enclosing the clutch drum of one clutch in the other clutch drum and forming the oil passage between the bottom of the outer peripheral member and the piston support of the inner peripheral member. Can be made compact.

By an oil passage forming a groove on the inner peripheral side member facing the inner wall of the outer peripheral member, to supply and discharge the hydraulic pressure to the groove to the hydraulic servo of one clutch constituting the clutch drum of the hand of the clutch, The hydraulic pressure can be supplied and discharged to the hydraulic servo of one clutch located on the outer diameter side with a simple configuration. In addition, the clutch drum portion, which overlaps the hydraulic servo of the other clutch in the radial direction, is made thin, and it is not necessary to form an oil hole to the hydraulic servo of the one clutch. It is possible to shorten the length, and by providing a groove on the inner wall of the outer peripheral member facing the inner peripheral member, the oil passage cross-sectional area is expanded, and the hydraulic pressure can be supplied to and discharged from the hydraulic servo more quickly.

By configuring the oil passage comprises a gap, supplying and discharging hydraulic to the hydraulic servo of one clutch by the gap between the outer peripheral side member and the inner peripheral member of the hand of the clutch, planar throughout the circumferential direction The hydraulic pressure can be quickly supplied to and discharged from the hydraulic servo through the gap extending to Furthermore, by concurrent both the oil passage according to the oil path and the gap by the grooves, the sufficient flow rate and and a small oil passage resistance, quickly and accurately the hydraulic pressure supply and discharge to the hydraulic servo of one clutch It can be carried out.

The boss portion of the inner peripheral member of the clutch drum of the hand of the clutch, an oil hole for supplying oil to the hydraulic servo of the one of the clutch said, and the oil holes for supplying oil to the cancel oil chamber of the one clutch the By disposing the phases in the circumferential direction, the oil holes can be overlapped in the axial direction, and the hydraulic pressure or oil can be supplied accurately even if the axial direction of the clutch is shortened. .

Of the inner peripheral member and the outer member forming the clutch drum of the previous SL one clutch comprises a multiple projection you projecting toward the inner circumference side member in the clutch drum of the other clutch, the The oil hole for hydraulic servo supply of one clutch is built in the protrusion, and the oil hole is cut off by arranging so that the opening of the oil hole and the groove provided on the inner wall of the outer peripheral side member are aligned. The area can be increased, and the hydraulic pressure can be smoothly supplied to and discharged from the hydraulic servo of one clutch.

  Further, the space portion of the inner circumferential member and the groove of the outer circumferential member are arranged in different phases at different positions in the circumferential direction, and rib-shaped protrusions are disposed at positions facing the groove of the inner circumferential member. Therefore, one of the clutch drums can maintain high rigidity as a whole even if it is thin.

Fitted piston constitutes the other hydraulic servo and the boss portion of the inner peripheral member of the other side of the clutch drum and one clutch of the clutch, a plurality of locations on the inner circumferential direction of the boss portion, other hydraulic By forming the oil hole for supplying and discharging the hydraulic pressure to the servo, the hydraulic pressure can be easily filled in the entire hydraulic servo when the operation of the other clutch is started.

In an automatic transmission that achieves eight forward speeds and at least one reverse speed, it can be made compact, particularly in the axial direction.

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

The automatic transmission according to the present invention is an automatic transmission suitable for being mounted on a vehicle such as an FF (front engine / front drive) type vehicle, and the left and right directions in FIGS. 1, 3 and 4 are on the power transmission system. (forward drive source side and rear wheel side) longitudinal but corresponding to, the description for convenience, "front side" to the right side in the drawing is a drive source side such as an engine, the left in the drawing side " It is said to be “rear side”.

First, a schematic configuration of an automatic transmission 1 to which the present invention can be applied will be described with reference to FIG. As shown in FIG. 1, an automatic transmission 1 of the FF type includes a case 6 such as a housing and the transmission case, the front side of the case (specifically, the converter housing) 6, an engine (not shown) An input member (front cover and center piece) 10 as an automatic transmission 1 that can be connected is provided. The automatic transmission 1 includes a torque converter 2 having a lock-up clutch 2 a, and a transmission mechanism 3, a counter shaft portion 4, and a differential portion 5 are disposed in a case 6.

  The torque converter 2 is disposed on an axis centering on the input shaft 7 of the transmission mechanism 3 that is coaxial with the output shaft of an engine (not shown). Further, the counter shaft portion 4 is disposed on a counter shaft 12 that is on an axis parallel to the input shaft 7, and the differential portion 5 has left and right axles 15 and 15 on an axis parallel to the counter shaft 12. Arranged in a shape.

  The transmission mechanism 3 is provided with a planetary gear (deceleration planetary gear) DP on the input shaft 7, and a planetary gear unit (planetary gear set) PU on the rear side thereof.

  The planetary gear DP includes a first sun gear S1, a first carrier CR1, and a first ring gear R1, and the first carrier CR1 has a pinion P2 and a first pinion meshing with the first sun gear S1. This is a so-called double pinion planetary gear having pinions P1 meshing with the ring gear R1 so as to mesh with each other.

  On the other hand, the planetary gear unit PU has a second sun gear S2, a third sun gear S3, a second carrier CR2, and a second ring gear R2 as four rotational elements. This is a so-called Ravigneaux type planetary gear having a long pinion P3 meshing with the sun gear S3 and the second ring gear R2 and a short pinion P4 meshing with the second sun gear S2.

  The rotation of the first sun gear S1 of the planetary gear DP is fixed with respect to the case 6. The carrier CR1 is connected to the input shaft 7 so as to be the same rotation as the input shaft 7 (hereinafter referred to as “input rotation”), and is connected to the fourth clutch C4. Yes. Further, the first ring gear R1 is decelerated by the input rotation being decelerated by the fixed first sun gear S1 and the input first carrier CR1, and the first clutch C1 and the first clutch C1. 3 clutch C3.

  The third sun gear S3 of the planetary gear unit PU is connected to the first brake B1 and can be fixed to the case 6, and is connected to the fourth clutch C4 and the third clutch C3. Thus, the input rotation of the first carrier CR1 can be input via the fourth clutch C4, and the first reduction rotation of the ring gear R1 can be input via the third clutch C3. The second sun gear S2 is connected to the first clutch C1, and the reduced rotation of the first ring gear R1 can be input.

Further, the second carrier CR2 is connected to the second clutch C2 to which the rotation of the input shaft 7 is input, and the input rotation can be freely input via the second clutch C2. Connected to the one-way clutch F1 and the second brake B2, the rotation in one direction with respect to the case (specifically, the transmission case) 6 is restricted via the one-way clutch F1, and the second brake B2 The rotation can be freely fixed via the. The second ring gear R2 is connected to a counter gear 8 that is rotatably supported with respect to a center support member fixed to the case 6.

  The counter gear 8 meshes with a large-diameter gear 11 fixed on the counter shaft 12 of the counter shaft portion 4, and the counter shaft 12 has a small diameter formed on the outer peripheral surface. The gear 14 of the differential portion 5 is engaged with the gear 12a. The gear 14 is fixed to a differential gear 13 and is connected to the left and right axles 15 and 15 via the differential gear 13.

  Next, based on the above configuration, the operation of the speed change mechanism 3 will be described with reference to FIGS. 1 and 2.

  For example, in the D (drive) range and in the first forward speed (1st), as shown in FIG. 2, the first clutch C1 and the one-way clutch F1 are engaged. Then, the rotation of the first ring gear R1 that is decelerated by the fixed first sun gear S1 and the first carrier CR1 that is the input rotation is input to the second sun gear S2 via the first clutch C1. The Further, the rotation of the second carrier CR2 is restricted in one direction (forward rotation direction), that is, the reverse rotation of the second carrier CR2 is prevented and fixed. Then, the decelerated rotation input to the second sun gear S2 is output to the second ring gear R2 via the fixed second carrier CR2, and the forward rotation as the first forward speed is output from the counter gear 8. The

  During engine braking (coasting), the second brake B2 is locked and the second carrier CR2 is fixed, so that the forward rotation of the second carrier CR2 is prevented. Maintain the stage state. Further, at the first forward speed, the one-way clutch F1 prevents the second carrier CR2 from rotating in the reverse direction and enables forward rotation. For example, the first forward speed when the non-travel range is switched to the travel range. Can be smoothly achieved by the automatic engagement of the one-way clutch F1.

  At the second forward speed (2nd), the first clutch C1 is engaged, and the first brake B1 is locked. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the second sun gear S2 via the first clutch C1. . Further, the rotation of the third sun gear S3 is fixed by the locking of the first brake B1. Then, the second carrier CR2 is decelerated and rotated at a speed lower than that of the second sun gear S2, and the decelerated rotation input to the second sun gear S2 is transferred to the second ring gear R2 via the second carrier CR2. The forward rotation is output from the counter gear 8 as the second forward speed.

  At the third forward speed (3rd), the first clutch C1 and the third clutch C3 are engaged. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the second sun gear S2 via the first clutch C1. Further, the reduced rotation of the first ring gear R1 is input to the third sun gear S3 by the engagement of the third clutch C3. That is, since the reduced rotation of the first ring gear R1 is input to the third sun gear S3 and the second sun gear S2, the planetary gear unit PU is directly connected to the reduced rotation, and the reduced rotation is directly output to the second ring gear R2. Forward rotation as the third forward speed is output from the counter gear 8.

  In the fourth forward speed (4th), the first clutch C1 and the fourth clutch C4 are engaged. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the second sun gear S2 via the first clutch C1. . Further, the input rotation of the first carrier CR1 is input to the third sun gear S3 by the engagement of the fourth clutch C4. Then, the second carrier CR2 is decelerated and rotated at a speed higher than that of the second sun gear S2, and the decelerated rotation input to the second sun gear S2 is transmitted to the second ring gear R2 via the second carrier CR2. The counter gear 8 outputs the forward rotation as the forward four stages.

  In the fifth forward speed (5th), the first clutch C1 and the second clutch C2 are engaged. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the second sun gear S2 via the first clutch C1. . Further, the input rotation is input to the second carrier CR2 by the engagement of the second clutch C2. Then, the decelerated rotation input to the second sun gear S2 and the input rotation input to the second carrier CR2 result in a decelerated rotation higher than the above four forward speeds and output to the second ring gear R2, and the forward rotation Forward rotation as five stages is output from the counter gear 8.

  At the sixth forward speed (6th), the second clutch C2 and the fourth clutch C4 are engaged. Then, the input rotation of the first carrier CR1 is input to the third sun gear S3 by the engagement of the fourth clutch C4. Further, the input rotation is input to the second carrier CR2 by the engagement of the second clutch C2. That is, since the input rotation is input to the third sun gear S3 and the second carrier CR2, the planetary gear unit PU is directly connected to the input rotation, and the input rotation is output to the second ring gear R2 as it is, so that the sixth forward speed. Is output from the counter gear 8.

  At the seventh forward speed (7th), the second clutch C2 and the third clutch C3 are engaged. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the third sun gear S3 via the third clutch C3. . Further, the input rotation is input to the second carrier CR2 by the engagement of the second clutch C2. Then, due to the decelerated rotation input to the third sun gear S3 and the input rotation input to the second carrier CR2, the decelerated rotation is slightly higher than the input rotation and is output to the second ring gear R2 to advance The forward rotation as seven stages is output from the counter gear 8.

At the eighth forward speed (8th), the second clutch C2 is engaged, and the first brake B1 is locked. Then, the input rotation is input to the second carrier CR2 by the engagement of the second clutch C2. Further, the rotation of the third sun gear S3 is fixed by the locking of the first brake B1. Then, the input rotation of the second carrier CR2 is increased at a higher speed than the forward seventh stage by the fixed third sun gear S3 and is output to the second ring gear R2, and the forward rotation is countered as the eighth forward speed. Output from the gear 8.

  In the first reverse speed (Rev1), the third clutch C3 is engaged, and the second brake B2 is locked. Then, the rotation of the first ring gear R1 decelerated by the fixed first sun gear S1 and the first carrier CR1, which is the input rotation, is input to the third sun gear S3 via the third clutch C3. . The rotation of the second carrier CR2 is fixed by the locking of the second brake B2. Then, the decelerated rotation input to the third sun gear S3 is output to the second ring gear R2 via the fixed second carrier CR2, and the reverse rotation is output from the counter gear 8 as the first reverse speed. .

  In the second reverse speed (Rev2), the fourth clutch C4 is engaged, and the second brake B2 is locked. Then, the input rotation of the first carrier CR1 is input to the third sun gear S3 by the engagement of the fourth clutch C4. The rotation of the second carrier CR2 is fixed by the locking of the second brake B2. Then, the input rotation input to the third sun gear S3 is output to the second ring gear R2 via the fixed second carrier CR2, and the reverse rotation is output from the counter gear 8 as the second reverse speed. .

  For example, in the P (parking) range and the N (neutral) range, the first clutch C1, the second clutch C2, the third clutch C3, and the fourth clutch C4 are released. Then, between the first carrier CR1 and the third sun gear S3, between the first ring gear R1, the third sun gear S3 and the second sun gear S2, that is, between the planetary gear DP and the planetary gear unit PU. Is in a disconnected state. Further, the input shaft 7 and the second carrier CR2 are disconnected. Thereby, the power transmission between the input shaft 7 and the planetary gear unit PU is cut off, that is, the power transmission between the input shaft 7 and the counter gear 8 is cut off.

  Next, in the automatic transmission 1, the configuration of the third (one) clutch C3 and the fourth (the other) clutch C4 according to the first embodiment of the present invention will be described with reference to FIG. The fourth clutch C4 located on the inner diameter side is arranged in two stories so as to be enclosed in the third clutch C3. That is, the third clutch C3 is located on the outer diameter side of the fourth clutch C4, overlaps in the axial direction, and is disposed at a different position in the radial direction.

  The third clutch C3 includes a multi-plate friction plate 21 composed of a large number of outer friction plates 21a and inner friction plates 21b, a hydraulic servo 20 that connects and disconnects these friction plates 21, and a centrifugal acting on the hydraulic servo 20. And a cancel oil chamber 28 for canceling the hydraulic pressure. Similarly, the fourth clutch C4 positioned on the inner diameter side also includes a multi-plate friction plate 41 including a large number of outer friction plates 41a and inner friction plates 41b, and a hydraulic servo 40 that connects and disconnects these friction plates 41; And a cancel oil chamber 48 for canceling centrifugal hydraulic pressure acting on the hydraulic servo 40.

The hydraulic servo 20 of the third clutch C3 includes a clutch drum 22, a piston member 24, a cancel plate 25, and a return spring 26, thereby forming a hydraulic oil chamber 27 and on the back thereof. A cancel oil chamber 28 is configured. The clutch drum 22, an inner drum (inner circumference side member) 22 ₁ constituting the boss portion 22c and the piston support portion 22e, outer drum (outer circumference side member) that constitutes a drum portion 22a and a bottom 22b 22 ₂ and is, welding or the like The drum portion 22a extends to the rear side of the first clutch C1 (not shown), and the boss portion 22c is rotatable to the stator shaft (fixed member) 6a via the bush 55. It is supported. The boss 22c and the drum portion 22a are connected by a bottom portion 22b. Note that the converter housing and the transmission case that are integrally coupled are represented as the case 6, and the case itself and the one that is integrally fixed to the case are fixing members. Therefore, the fixing member is the case, the oil pump, or the like. A cover and a case, a stator shaft 6a and the like are included. Accordingly, the first sun gear S1 and the boss portion 22c of the drum 22 are not limited to the stator shaft 6a as long as they are fixed members, but are fixed to the case 6 or a fixed member integral therewith (sun gear S1) or rotatably supported. (Boss portion 22c).

A flange portion 22d is formed on the outer periphery of a piston support portion 22e extending from the boss portion 22c to the outer diameter side at an intermediate portion of the bottom portion 22b of the clutch drum 22, and the flange portion 22d includes the drum portion 22a and the boss portion 22c. It extends in the same direction and significantly shorter than the drum portion and the boss portion . Further, the flange portion 22d is oil-tightly connected to the outer peripheral surface via the piston member 24 and the O-ring 31, and on the inner peripheral surface thereof, the clutch drum 42 of the fourth clutch C4, which will be described later, is connected to the spline. (54) .

The piston member 24, while being the collar portion 22d axially movably fitted, the outer peripheral surface, and the inner peripheral surface of the clutch drum 22, via a seal member 56 connected to an oil-tight manner, said piston The member 24 and the inner peripheral surface of the clutch drum 22 forming the cylinder constitute the hydraulic oil chamber 27. The piston member 24 includes an extension portion 24a extending rearward, and the extension portion 24a presses the friction plate 21 so that the third clutch C3 is connected / disconnected.

  On the other hand, the clutch drum 42 of the fourth clutch C4 is restricted in the axial position by the snap ring 50 to the boss portion 22c of the third clutch C3 and is provided in an oil-tight manner via the O-ring 57. The clutch drum 42 includes a stepped portion 53 having a stepped cross section at the rear of the spline engaging portion 54 with the flange portion 22d of the third clutch C3.

Cancel plate 25 of the third clutch C3 is a stepped portion 53 provided on the clutch drum 4 2 of the fourth clutch C4 axial movement to contact with the rear is restricted, the seal member 58 at its outer periphery And the piston 24 is oil-tightly fitted to the clutch drum 42 of the fourth clutch via the seal member 85 in the inner peripheral portion. The cancellation oil chamber 28 that generates hydraulic pressure that balances with the centrifugal hydraulic pressure generated in the hydraulic oil chamber 27 of the third clutch is constituted by the outer peripheral surface of the cancel plate 25 and the inner peripheral surface of the piston 24. A return spring 26 is disposed between the cancel plate 25 and the piston 24, and always urges the piston 24 forward. The return spring 26 is a spring having a stronger urging force than a return spring 46 provided in a cancel oil chamber 48 of a fourth clutch C4 described later.

Above the hydraulic oil chamber 27 of the third clutch C3, via a piston support portion 22e of the inner drum 22 _1, and the bottom 22b of the outer drum 22 _2, a predetermined gap B provided between the oil hole b Supplied with oil. Since the gap B is provided so as to extend in a planar shape over the entire circumference, the gap B has a large oil passage cross-sectional area in a short (narrow) space in the axial direction as compared with the oil passage hole.

Moreover, the gap in the cancel oil chamber 28 of the third clutch C3, the clutch drum 42 of the fourth clutch C4, disposed between the piston support portion 22e back of the inner drum 22 ₁ of the third clutch C3 The lubricating oil from the oil hole a is supplied through A. Since the gap A is provided so as to extend in a planar shape over the entire circumference, the gap between the clutch drums 22 and 42 is kept narrow (thus reducing the axial dimension). The oil passage cross-sectional area is larger than that using oil holes. Note that a spline engaging portion 54 provided between the clutch drum 42 of the fourth clutch C4 and the flange portion 22e of the third clutch C3 is provided with a missing tooth, It is configured not to obstruct the flow of.

  On the other hand, the hydraulic servo 40 of the fourth clutch C4 has the above-described clutch drum 42, piston member 44, cancel plate 45, and return spring 46, and these constitute a hydraulic oil chamber 47. At the same time, a cancel oil chamber 48 is formed on the back surface thereof.

The piston 44 is provided in an oil-tight and axially movable manner via a boss portion 22c of the clutch drum 22 of the third clutch C3 and a seal member 59, and has an extension portion 44a that presses the friction plate 41. provided and an outer peripheral surface of the extension portion 44a, and the inner peripheral surface of the clutch drum 42, but is fitted in an oil-tight manner via an O-ring 51.

  The hydraulic oil chamber 47 of the fourth clutch C4 is constituted by the outer peripheral surface of the piston 44 and the inner peripheral surface of the clutch drum 42 forming the cylinder, and oil is supplied to the hydraulic oil chamber 47 through the oil hole c. It becomes the composition which is done.

The cancel plate 45 of the fourth clutch C4 is provided with its axial position regulated by the stepped portion 22f of the boss portion 22c of the third clutch drum 22 and the snap ring 30, and the cancel plate 45 It is fitted in an oil-tight manner via an inner circumferential surface and the seal member 60 of the piston 44.

  A cancel oil chamber 48 in which a hydraulic pressure that balances with the centrifugal hydraulic pressure generated in the hydraulic oil chamber 47 of the fourth clutch C4 is formed by the inner surface of the cancel plate 45 and the back surface of the piston 44. A return spring 46 is provided between the piston 44 and the cancel plate 45, and the piston 44 is always urged forward. The cancel oil chamber 48 is supplied with lubricating oil through an oil hole d.

  Next, with respect to the second embodiment in which the cross-sectional area of oil passage to the hydraulic oil chamber 27 and the cancel oil chamber 28 of the third clutch C3 is further increased, the configuration different from the first embodiment is mainly shown in FIG. ), (B), (c) and FIG.

As described above, the hydraulic oil chamber 27 of the third clutch C3 is supplied with oil from the oil hole b through the gap B, and the cancel oil chamber 28 is supplied with lubricating oil from the oil hole a through the gap A. Is configured to be supplied. The clearance B is provided with an outer surface 71 which is the surface facing the outer drum 22 ₂ of the inner drum 22 _1, a gap that extends in a planar manner between the inner wall 73 which is the inner surface of the outer drum 22 _2, the gap A is, inner a back 70 located at the back of the drum 22 ₁ of the outer surface 71, a gap that extends in a planar manner between the outer surface of the clutch drum 42 of the fourth clutch C4. The clutch drum 42 has an inner diameter side portion is formed obliquely rearward toward the inner diameter, coupled with that the up standing in a substantially vertical with the exception of the projections 72 the inner drum 22 ₁ of the clutch drum will be described later Thus, the gap A has a space portion A ′ that is wide on the center side (in the direction of the input shaft 7) in the axial direction, and is narrow on the outer diameter side.

_On the back surface 70 of the inner drum 221, rib-like protrusions 72 (protrusions) extending in the radial direction toward the fourth clutch C4 are projected at four locations on the circumference thereof. An oil hole b serving as a part of an oil passage for supplying oil to the hydraulic oil chamber 27 is formed inside. Oil holes b penetrates the inner drum 22 _1, and forms an opening _{b 2} in the outer surface 71. The above In the first embodiment, as shown in the lower half of FIG. 3, but the inner drum 22 ₁ is formed thicker, in the present embodiment, FIG. 4 (b as shown in), as a whole (non-protruding portions 72) the inner drum 22 ₁ becomes thinner, the space portion a 'is formed between the clutch drum 42 of the fourth clutch. That is, the space portion A 'is formed between the outer surface of the inner drum 22 ₁ of the rear 70 and the clutch drum 42 in the circumferential direction between parts of the protruding portions 72. Accordingly, the oil hole b formed in the protrusion 72 and the space portion A ′ are arranged so as to overlap in the axial direction when viewed from the circumferential direction. Further, the number of the protrusions 72 is not limited to four, but may be three or five, or other numbers.

As shown in FIG. 4 (a), the inner drum 22 _1, the boss portion 22c of the cylindrical shape are formed on the inner diameter side, the oil hole b and, oil holes for supplying lubricating oil to the cancel oil chamber 28 a and its discharge hole e are positioned out of phase in the circumferential direction (note that both holes a and e are shown together in FIG. 4 (b), but this is for convenience in drawing. This part shows a different cross section.) The oil holes b are arranged at four locations on the circumference of the boss portion 22c like the protrusions 72, and the oil holes a are sandwiched between the oil holes b on the left and right sides of the oil holes b. It is arranged. In addition, oil reservoirs a ₁ and b ₁ are formed in the supply oil holes a and b larger in the circumferential direction on the inner diameter side.

The outer drum 22 ₂ of the inner wall 73 facing the outer surface 71 of the inner drum 22 ₁ is provided with a groove 74 facing the opening portion _{b 2} of the oil holes b formed on the outer surface 71, groove 74 the inner wall The surface 73 extends radially in the outer diameter direction. Further, the groove 74 is formed as an elongated rectangular recess extending over the entire length of the gap B to the hydraulic oil chamber 27, and increases the oil passage cross-sectional area of the gap B without expanding in the axial direction. b and is filled quickly its circumferential oil supplied from the opening b ₂ of.

On the other hand, of the inner drum 22 ₁ of the rear 70, the surface being located on the surface protrusions 72 are not formed, i.e., oil holes a and the discharge holes e and the phase, the outer drum 22 ₂ side (Fr direction) It is formed to be recessed. The back surface 70 is formed with a gap A for supplying lubricating oil to the cancel oil chamber 28 together with the clutch drum 42 of the fourth clutch C4, and the back surface 70 is formed to be recessed in accordance with the oil hole a and the discharge hole e. By doing so, the oil passage cross-sectional area of the gap A is made large without expanding in the axial direction.

The clutch drum 22 of the third clutch C3 includes a protrusion 72 of the inner drum 22 _1, and arranged corresponding to the position of the same phase on the circumference a groove 74 of the outer drum 22 _2, inner drum 22 The concave portion of the back surface 70 of ₁ and the portion of the inner wall 73 other than the groove 74 are arranged corresponding to the position of the same phase on the circumference, so that the overall structure is thin and has high rigidity. ing.

  In the fourth clutch C4, the oil hole c for supplying oil to the hydraulic oil chamber 47 and the oil hole d for supplying lubricating oil to the cancel oil chamber 48 are arranged in the same or different phases in the circumferential direction. On the inner peripheral surface of the clutch drum 42 constituting the hydraulic oil chamber 47, grooves may be formed radially toward the outer diameter direction in the same manner as the third clutch C3.

  Next, the operation of the third clutch C3 and the fourth clutch C4 will be described below.

  The third clutch C3 connects and disconnects the third clutch C3 by moving the piston 24 in the axial direction by the hydraulic pressure generated in the hydraulic oil chamber 27 and pressing the friction plate 21. In the hydraulic oil chamber 27, hydraulic oil based on hydraulic pressure generated by an oil pump (not shown) is provided in a gap B and a groove 74 provided in a planar shape from the oil hole b formed in the clutch drum 22 over the entire circumference. Supplied through.

  Since the hydraulic oil pressure is applied to the hydraulic oil chamber 27, the lubricating oil is supplied to the cancel oil chamber 28 facing the piston 24 through the clearance A provided in a planar shape from the oil hole a to the entire circumference. The centrifugal oil pressure is generated in the cancel oil chamber 28 and balanced with the centrifugal oil pressure generated in the hydraulic oil chamber 27.

  Similarly, the fourth clutch C4 supplies hydraulic oil to the hydraulic oil chamber 47 from the oil hole c based on an oil pump (not shown), moves the piston 44 in the axial direction, and presses the friction plate 41. The fourth clutch C4 is disconnected and connected, and lubricating oil is supplied to the cancel oil chamber 48 from the oil hole d, and centrifugal oil pressure is generated in the cancel oil chamber 48, and the centrifugal oil pressure generated in the hydraulic oil chamber 47 is generated. Equilibrate with.

  Accordingly, when the third clutch C3 is disengaged, the pressure oil in the hydraulic oil chamber 27 is drained through the gap B, the groove 74, and the oil hole b. However, since the clutch drum 22 is rotating, the hydraulic oil Centrifugal oil pressure is generated in the chamber 27. At this time, a centrifugal oil pressure acting on the urging force of the return spring 26 and the oil in the cancel oil chamber 48 acts on the back surface of the piston member 24, and the piston member 24 is resisted against the centrifugal oil pressure in the hydraulic oil chamber 27. As a result, the capacity of the cancel oil chamber 28 increases rapidly, but the oil is quickly replenished through the gap A between the clutch drums 22 and 42, and the third clutch C3 There is no delay in operation.

  As described above, according to the automatic transmission 1 according to the present invention, the third clutch C3 is on the outer diameter side of the fourth clutch C4, overlaps in the axial direction, and is in a position different in the radial direction. By disposing, the clutch unit and the automatic transmission can be configured compactly in the axial direction, and an oil passage b is provided on the inner diameter side of the clutch drum 22 of the third clutch C3. By having a gap B that expands in a planar shape between the clutch drum 22 and the piston support portion 22e, it is possible to quickly supply and discharge hydraulic pressure to and from the hydraulic servo 20 of the third clutch C3. Further, by forming the groove 74 in the gap B, the hydraulic pressure can be supplied to and discharged from the hydraulic servo 20 of the third clutch C3 more quickly.

Further, a gap A provided between the clutch drum 22 of the third clutch C3 and the clutch drum 42 of the fourth clutch C4 is configured as an oil supply path to the cancel oil chamber 28 of the third clutch C3. Since the gap B is used as an oil passage to the hydraulic oil chamber 27 and the clutch drum 22 is made thin, the axial direction can be shortened. In this case, and a groove 74 in the third clutch C3, be formed by Hekomashi the back 70 of the inner drum 22 _1, to form a recess of the groove 74 and the outer surface 70 by shifting the circumferential direction of the phase, The clutch drum 22 of the third clutch C3 can maintain high rigidity as a whole.

The skeleton figure which shows this automatic transmission typically. The engagement table of this automatic transmission. FIG. 3 is an enlarged cross-sectional view showing a part of the automatic transmission according to the first embodiment. (A) The top view of the inner drum which concerns on 2nd Embodiment seen from Rr direction. (B) The expanded sectional view which shows a part of automatic transmission which concerns on 2nd Embodiment. (C) The top view of the inner drum which concerns on 2nd Embodiment seen from Fr direction. The top view of the outer drum which concerns on 2nd Embodiment seen from the Rr direction.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Automatic transmission 6a Fixed member 7 Input shaft 20 Hydraulic servo 21 Friction plate 22 Clutch drum 22 ₁ Inner peripheral member (outer drum)
22 ₂ Outer peripheral member (inner drum)
22a drum portion 22b bottom portion 22c boss portion 22d flange 24 piston 25 cancel plate 26 return spring 28 cancel oil chamber 30 snap ring 40 hydraulic servo 41 friction plate 42 clutch drum 44 piston 46 return spring 48 cancel oil chamber 54 spline engagement (spline) Engagement part)
72 Protrusions (protrusions)
74 Groove (oil passage)
A Gap A 'Space B B Gap (oil passage)
a oil hole b oil hole b ₂ opening c oil hole C1 first clutch C2 second clutch C3 one clutch (third clutch)
C4 The other clutch (fourth clutch)
PU planetary gear set DP reduction planetary gear S1 first sun gear S2 second sun gear S3 rotating element (third sun gear)
CR1 1st carrier R1 1st ring gear R2 2nd ring gear B1 1st brake B2 2nd brake P3 Long pinion P4 Short pinion

Claims (7)

Two clutches each having a friction plate that is overlapped in the axial direction and disposed at different positions in the radial direction, and each of the two clutches has a clutch drum and a hydraulic servo using a part of the clutch drum as a cylinder. a piston configuration, has said friction plate engaging said clutch drum, and a cancel oil chamber that cancels the centrifugal hydraulic pressure applied to the hydraulic servo is disposed on the rear side of the piston, the automatic transmission In the machine
Of the two clutches, the hydraulic servo and the cancel oil chamber of one clutch located on the outer diameter side are respectively on the outer diameter side with respect to the hydraulic servo and the cancel oil chamber of the other clutch located on the inner diameter side. Placed in
The clutch drum of the one clutch is formed integrally with an inner peripheral side member having a boss portion and a piston support portion, and an outer peripheral side member having a drum portion and a bottom portion,
The piston support portion includes a plurality of protrusions protruding toward the clutch drum of the other clutch and extending in the radial direction,
An oil passage for supplying and discharging hydraulic pressure to a hydraulic servo of the one clutch is formed in the gap between the piston support portion of the inner peripheral member and the bottom portion of the outer peripheral member and the protrusion ,
A space for supplying oil to the cancellation oil chamber of the one clutch is formed between the piston support portion including the circumferential portion of the plurality of protrusions and the clutch drum of the other clutch,
The oil passage in the projection and the space between the circumferential portions of the projection are arranged so as to overlap in the axial direction.
An automatic transmission characterized by that. The clutch drum of the one clutch is arranged so as to contain the clutch drum of the other clutch .
The automatic transmission according to claim 1. The inner wall of the outer peripheral member facing the inner peripheral member is provided with a groove, and the groove constitutes the oil passage.
The automatic transmission according to claim 1 or 2. An oil hole that communicates with the oil passage and an oil hole that supplies oil to the cancel oil chamber of the one clutch are disposed in the boss portion of the inner peripheral member with a phase shifted in the circumferential direction. ,
The automatic transmission according to claim 1 . Before Symbol the projections, with a built-in oil holes constituting the oil passage formed by arranging so as to align the said groove and opening of the oil hole,
The automatic transmission according to claim 3 . The other hydraulic servo is configured by fitting the piston to the clutch drum of the other clutch and the boss portion of the inner peripheral side member,
An oil hole for supplying and discharging hydraulic pressure to the other hydraulic servo is formed at a plurality of locations in the inner circumferential direction of the boss portion.
The automatic transmission according to any one of claims 1 to 5 . An input shaft to which input rotation from a drive source is input;
A first sun gear that is rotationally fixed to a case or a fixing member that is integral with the case, a first carrier that is coupled to the input shaft, the first sun gear that is rotationally fixed, and an input rotation are input. A reduction planetary gear comprising: a first ring gear that outputs reduced rotation by the first carrier;
A second sun gear that inputs a reduced rotation of the first ring gear by engagement of the first clutch; a reduced rotation of the first ring gear that is input by engagement of a third clutch; and a fourth clutch. A third sun gear that inputs rotation of the input shaft via the first carrier by engagement of the first carrier and is fixed by rotation of the first brake, and a long that meshes with the third sun gear. A pinion and a short pinion that meshes with the long pinion and the second sun gear, the rotation is fixed by the locking of the second brake, and the rotation of the input shaft is input by the engagement of the second clutch A planetary gear set comprising: a second carrier; and a second ring gear that meshes with the long pinion and is rotationally connected to the output member,
The one clutch is the third clutch;
The other clutch is the fourth clutch;
Engage the first clutch and lock the second brake to change the first forward speed,
Engage the first clutch and lock the first brake to change the second forward speed,
By engaging the first clutch and the third clutch, the third forward speed is established.
By engaging the first clutch and the fourth clutch, the fourth forward speed is established.
By engaging the first clutch and the second clutch, the fifth forward speed is established.
By engaging the second clutch and the fourth clutch, the sixth forward speed is established.
By engaging the second clutch and the third clutch, the seventh forward speed is established.
Engage the second clutch and lock the first brake to change the eighth forward speed,
The reverse gear is achieved by engaging the third clutch or the fourth clutch and locking the second brake, respectively.
The automatic transmission according to any one of claims 1 to 6 .

Images