JP3831334B2 - Gear transmission for automatic transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention includes an input unit, three sets of planetary gears, three clutches, two brakes, and an output unit. The three clutches and two brakes, which are speed change elements, are appropriately engaged / The present invention relates to a technology for downsizing a transmission in an automatic transmission gear transmission that obtains at least six forward speeds and one reverse speed by releasing.
[0002]
[Prior art]
Today, automatic transmissions tend to be multi-staged with the aim of improving fuel efficiency and driving performance, and are gear transmissions for automatic transmissions that allow selection of six forward speeds and one reverse speed. As a gear transmission using a type compound planetary gear train (a compound planetary gear train in which sun gears are engaged with double pinions, respectively), for example, a configuration described in Patent Document 1 is disclosed. In the gear transmission for an automatic transmission having such a configuration, the clutches C1 and C2 for connecting and disconnecting the reduction force are arranged at the rear or upper part of the Ravigneaux type planetary gear train G, and the Ravigneaux type planetary gear train. A configuration in which a brake B1 (band type brake in the figure) is arranged on the outer periphery of G and a brake B2 is arranged in the same row is conventional.
[0003]
[Patent Document 1]
JP 2000-55152 A (FIG. 1).
[0004]
[Problems to be solved by the invention]
However, the technique described in Patent Document 1 has the following problems.
(1) The clutches and brakes are arranged so as to overlap in the axial direction, and the respective clutch members and brake members become longer in the axial direction, which is disadvantageous in terms of weight.
(2) In the FF vehicle, the vehicle side member (responsible for the rigidity of the vehicle body) is arranged on the side opposite to the side where the engine is assembled (the rear end portion of the AT), so the clearance with the automatic transmission is narrow. However, it is easy to cause deterioration in mountability due to the large trunk circumference at the rear end of the AT.
{Circle around (3)} Each member overlaps in the axial direction, and the flow of lubricating oil for clutches and brakes becomes complicated, making it difficult to ensure lubricity.
[0005]
The present invention has been made paying attention to the above problems, and includes a plurality of planetary gear sets including a compound planetary gear train, three clutches and two brakes, and a combination of engagement and release of these clutches and brakes. An object of the present invention is to provide a gear transmission for an automatic transmission capable of ensuring lubrication performance while reducing the size of the gear transmission and making it possible to select at least six forward speeds and one reverse speed. .
[0006]
[Means for Solving the Problems]
In order to solve the above problems, in the present invention, an input unit that inputs rotation from a drive source, an output unit that is coaxially disposed in the input unit and transmits output rotation of the gear transmission, and these input units And a plurality of planetary gear sets including a complex planetary gear train capable of providing a large number of conduction paths between the output section and the output section, and selecting one of the conduction paths by the plurality of planetary gear sets at a corresponding gear ratio. Three clutches and two brakes that are selectively connectable and disengaged so that the rotation from the parts can be changed and output to the output part, and at least by the combination of engagement and release of these clutches and brakes A gear transmission for an automatic transmission that allows selection of six forward speeds and one reverse speed is assumed.
[0007]
At this time, one planetary gear set among the plurality of planetary gear sets is used as a reduction planetary gear set that always decelerates and outputs the input rotation, and the remaining two planetary gear sets are combined. A pair of planetary gear sets, two sun gears, a common pinion that meshes with the two sun gears, a ring gear that meshes with the pinion, and a carrier that rotatably supports the pinion; A double sun gear planetary gear set comprising a center member that extends from between the two sun gears and rotates integrally with the carrier, and the other planetary gear set is connected to one sun gear and the sun gear. And a single pinion type planetary gear set comprising a ring gear meshing with the pinion and a carrier that rotatably supports the pinion. The input member of the reduced rotation to the case planetary gear train Of the single pinion type planetary gear set A member connected to the ring gear.
[0008]
Then, the reduction planetary gear set, the single pinion type planetary gear set, and the double sun gear type planetary gear set are arranged in this order from the power source, and two of the three clutches are output from the reduction planetary gear set. With decelerated rotation A member connected to the ring gear of the single pinion type planetary gear set and a sun gear of the single pinion type planetary gear set. The first and second clutches that selectively connect and disconnect the members are used, and the remaining one clutch is the rotation of the input unit. The center The third clutch selectively connects and disconnects the member.
[0009]
At this time, a multi-plate friction element of a second clutch, which is a jump transmission clutch including a reverse gear among two clutches that connect and disconnect the reduction rotation, is arranged radially outward of the reduction planetary gear set, The reduced rotation is radially outward of the pinion planetary gear set. And a member connected to the ring gear of the single pinion type planetary gear set; Connect and disconnect Low A multi-plate friction element of a first clutch that is a shift stage clutch is arranged, and an input portion and a double sun gear planetary gear are arranged at a position that overlaps in the axial direction on the rear end side of the transmission of the double sun gear planetary gear set. A multi-plate friction element of a third clutch, which is a high-speed transmission clutch that directly connects the pair, is arranged.
[0010]
Further, in the invention described in claim 2, the basic configuration is the same as that of the invention described in claim 1, and as an arrangement of different clutches, an input portion is provided radially outward of the double sun gear type planetary gear set. A multi-plate friction element of a third clutch, which is a high-speed transmission clutch that directly connects a double sun gear type planetary gear set, is arranged.
[0011]
[Action and effect of the invention]
That is, in the first invention, the first clutch is arranged on the outer periphery of the single pinion type planetary gear set, the second clutch is arranged radially outward of the reduction planetary gear set, and the double sun gear type planetary gear is arranged. Since the third clutch is arranged at the rear end side of the pair of transmissions and in the position overlapping in the axial direction, it is possible to reduce the size in the radial direction. It is possible to improve the mountability to FF vehicles that do not have any.
[0012]
In the second invention, the first clutch and the second clutch are arranged in the same manner as in the first invention, and the third clutch is arranged radially outward of the double sun gear type planetary gear set. Thus, it is possible to reduce the size in the axial direction, and in particular, it is possible to improve the mountability to an FF vehicle or the like having no room in the axial direction space.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, first to second embodiments for realizing a gear transmission for an automatic transmission according to the present invention will be described with reference to the accompanying drawings.
[0014]
(First embodiment)
The first embodiment is a gear transmission for an automatic transmission corresponding to the invention described in claims 1, 3, 4, 5, 6, 8, and 9. FIG. 1 is a gear for an automatic transmission according to the first embodiment. It is a skeleton figure which shows a transmission.
[0015]
In FIG. 1, G1 is a first planetary gear, G2 is a second planetary gear, G3 is a third planetary gear, M1 is a first connecting member, M2 is a second connecting member, C1 is a first clutch, and C2 is a second clutch. , C3 is a third clutch, B1 is a first brake, B2 is a second brake, Input is an input shaft (input unit), and Output is an output gear (output unit).
[0016]
In the gear transmission for an automatic transmission according to the first embodiment, a single pinion type first planetary gear G1 as a speed reducer is disposed at the right end of FIG. 1, and a single pinion type second planetary gear G2 is disposed at the center. This is an example in which a third sun gear G3 of a double sun gear type is arranged at the left end. The second planetary gear G2 and the third planetary gear G3 constitute a so-called isimal planetary gear train.
[0017]
The first planetary gear G1 has a first sun gear S1, a first ring gear R1, and a first carrier PC1 that supports a first pinion P1 that meshes with both gears S1 and R1, and is a single pinion planetary as a speed reducer. It is a gear.
[0018]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier PC2 supporting a second pinion P2 meshing with both the gears S2, R2.
[0019]
The third planetary gear G3 includes two third sun gears S3 and a fourth sun gear S4, a third pinion P3 that meshes with each of the third and fourth sun gears S3 and S4, and an axial direction that supports the third pinion P3. A third carrier PC3, a center member CM connected to the third carrier PC3 and disposed between the sun gears S3 and S4, and a third ring gear R3 meshing with the third pinion P3. It is a double sun gear type planetary gear. The center member CM is coupled to the third carrier PC3 at a spatial position with a plurality of third pinions P3 adjacent on the circumference of the third carrier PC3.
[0020]
The input shaft Input is connected to the first ring gear R1 and inputs a rotational driving force from an unillustrated engine as a drive source via a torque converter or the like.
[0021]
The output gear Output is connected to the second carrier PC2, and transmits the output rotational driving force to the drive wheels via a final gear or the like not shown.
[0022]
The first connecting member M1 is a member that integrally connects the second sun gear S2 and the third sun gear S3.
[0023]
The second connecting member M2 is a member that integrally connects the second carrier PC2 and the third ring gear R3.
[0024]
The first clutch C1 is a clutch that selectively connects and disconnects the first carrier PC1 and the second ring gear R2.
[0025]
The second clutch C2 is a clutch that selectively connects and disconnects the first carrier PC1 and the second sun gear S2.
[0026]
The third clutch C3 is a clutch that selectively connects and disconnects the input shaft Input and the center member CM.
[0027]
The first brake B1 is a brake that selectively stops the rotation of the third carrier PC3.
[0028]
The second brake B2 is a brake that selectively stops the rotation of the fourth sun gear S4.
[0029]
Each of the clutches C1, C2, C3 and the brakes B1, B2 has an engagement pressure (marked with a circle) and a release pressure (indicated by a circle) and a release pressure ( An unillustrated shift hydraulic control device that creates a blank is connected. Note that a hydraulic control type, an electronic control type, a hydraulic pressure + electronic control type, and the like are employed as the transmission hydraulic pressure control device.
[0030]
Next, the operation will be described.
[0031]
[Shifting action]
[0032]
FIG. 2 is a diagram showing a fastening operation table of 6-speed forward and reverse 1-speed in the gear transmission for an automatic transmission of the first embodiment, and FIG. 3 is 6-speed forward in the gear transmission for an automatic transmission of the first embodiment. FIG. 4 to FIG. 7 are diagrams showing the sixth forward speed and the reverse first speed of the gear transmission for an automatic transmission according to the first embodiment. It is a figure which shows the torque flow of. In FIG. 3, the bold line is a collinear diagram of the first planetary gear G1, and the middle line is a collinear diagram of the Ishimaru planetary gear train. 4 to 7, the torque transmission path of the clutch / brake member is indicated by a thick line, and the torque transmission path of the gear is indicated by hatching. Hereinafter, the shifting operation at each of the six forward speeds and the first reverse speed will be described.
[0033]
<First gear>
The first speed is obtained by engaging the first clutch C1 and the first brake B1, as shown in FIG.
[0034]
At the first speed, in the second planetary gear G2, the rotation decelerated by the first planetary gear G1 by the engagement of the first clutch C1 is input to the second ring gear R2.
[0035]
On the other hand, in the third planetary gear G3, since the third carrier PC3 is fixed to the case by the engagement of the first brake B1, the rotation of the third sun gear S3 is the rotation of the output rotation from the third ring gear R3. The direction is reduced and rotated in the reverse direction. The rotation of the third sun gear S3 is transmitted to the second sun gear S2 of the second planetary gear G2 via the first connecting member M1.
[0036]
Therefore, in the second planetary gear G2, the rotation that is decelerated in the forward direction is input from the second ring gear R2, and the decelerated rotation in the reverse direction is input from the second sun gear S2, and from the second ring gear R2, The rotation whose speed has been reduced is output from the second carrier PC2 to the output gear Output after passing through the second connecting member M2.
[0037]
That is, as shown in the collinear diagram of FIG. 3, the first speed includes the engagement point of the first clutch C1 in which the rotation decelerated by the first planetary gear G1 is the input rotation to the second ring gear R2, and the third carrier. It is defined by a line connecting the engagement point of the first brake B1 that stops the rotation of the PC3, and the rotation input from the input shaft Input is decelerated and output from the output gear Output.
[0038]
The torque flow at the first speed is as shown in FIG. 4 (a). The first clutch C1, the first brake B1, each member indicated by a thick line, the second planetary gear G2 and the third planetary gear indicated by hatching. Torque acts on G3 (excluding the fourth sun gear S4). That is, at the first speed, the second planetary gear G2 and the third planetary gear G3 constituting the isimal type planetary gear train are involved in torque transmission.
[0039]
<Second gear>
As shown in FIG. 2, the second speed is obtained by releasing the first brake B1 at the first speed and engaging the second brake B2, that is, engaging the first clutch C1 and the second brake B2.
[0040]
At the second speed, in the second planetary gear G2, the rotation decelerated by the first planetary gear G1 by the engagement of the first clutch C1 is input to the second ring gear R2.
[0041]
On the other hand, in the third planetary gear G3, the fourth sun gear S4 is fixed to the case by the engagement of the second brake B2, so that the third sun gear S3 connected via the third pinion P3 is fixed. The second sun gear S2, which is connected to the third sun gear S3 via the first connecting member M1, is fixed to the case.
[0042]
Therefore, in the second planetary gear G2, the rotation decelerated in the positive direction is input from the second ring gear R2, and the second sun gear S2 is fixed, and the decelerated rotation from the second ring gear R2 is the second rotation. The carrier PC2 passes through the second connecting member M2 and is output to the output gear Output.
[0043]
That is, as shown in the collinear diagram of FIG. 3, the second speed includes the engagement point of the first clutch C1 in which the rotation reduced by the first planetary gear G1 is the input rotation to the second ring gear R2, and the fourth sun gear. It is defined by a line connecting the engagement point of the second brake B2 that stops the rotation of S4, and the rotation input from the input shaft Input is decelerated (higher than the first speed) and output from the output gear Output.
[0044]
The torque flow at the second speed is as shown in FIG. 4 (b). Torque acts on the first clutch C1, the second brake B2, each member indicated by a thick line, and the second planetary gear G2 indicated by hatching. It will be. As for the third planetary gear G3, the unconstrained third pinion P3 only revolves around the fixed sun gears S3 and S4 with the output rotation of the third ring gear R3, and functions as a rotating member. It does not participate in torque transmission.
[0045]
<3rd speed>
As shown in FIG. 2, the third speed is obtained by releasing the second brake B2 at the second speed and engaging the second clutch C2, that is, engaging the first clutch C1 and the second clutch C2. It is done.
[0046]
In the third speed, the rotation from the input shaft Input is decelerated and output in the first planetary gear G1, and the first planetary gear G1 is engaged in the second planetary gear G2 by the engagement of the first clutch C1 and the second clutch C2. The rotation decelerated by this is simultaneously input to the second ring gear R2 and the second sun gear S2.
[0047]
Accordingly, the second planetary gear G2 rotates integrally, and the rotation decelerated by the first planetary gear G1 after passing through the second connecting member M2 from the second carrier PC2 is output to the output gear Output as a reduced rotation. .
[0048]
That is, as shown in the collinear diagram of FIG. 3, the third speed is the first clutch C1 engagement point where the rotation reduced by the first planetary gear G1 is the input rotation to the second ring gear R2, and the first planetary gear. It is defined by a line connecting the engagement point of the second clutch C2 that makes the decelerated rotation from the gear G1 the input rotation to the second sun gear S2, and decelerates the rotation input from the input shaft Input to the output gear Output. Output.
[0049]
The torque flow at the third speed is as shown in FIG. 5A, and the first and second planetary gears G1, G2 shown by hatching, the first clutch C1, the second clutch C2, and the members shown by bold lines. Torque acts on G2. That is, the third planetary gear G3 is not involved in torque transmission at all.
[0050]
<4th speed>
As shown in FIG. 2, the fourth speed is obtained by releasing the second clutch C2 at the third speed and engaging the third clutch C3, that is, engaging the first clutch C1 and the third clutch C3. .
[0051]
In the fourth speed, in the second planetary gear G2, the rotation decelerated by the first planetary gear G1 by the engagement of the first clutch C1 is input to the second ring gear R2.
[0052]
On the other hand, in the third planetary gear G3, the input rotation from the input shaft Input is input to the third carrier PC3 via the center member CM by the engagement of the third clutch C3. Therefore, the rotation of the third sun gear S3 is increased more than the output rotation of the third ring gear R3, and the increased rotation of the third sun gear S3 is transmitted to the second sun gear S2 via the first connecting member M1. .
[0053]
That is, as shown in the collinear diagram of FIG. 3, the fourth speed includes the engagement point of the first clutch C1 in which the rotation reduced by the first planetary gear G1 is the input rotation to the second ring gear R2, and the third carrier. Rotation input from the input shaft Input is decelerated slightly and output from the output gear Output.
[0054]
The torque flow at the fourth speed is as shown in FIG. 5 (b). The first clutch C1, the third clutch C3 and each member indicated by bold lines, the first planetary gear G1 and the second planetary gear indicated by hatching. Torque acts on G2 and the third planetary gear G3 (excluding the fourth sun gear S4).
[0055]
(5-speed)
In the fifth speed, as shown in FIG. 2, the first clutch C1 in the fourth speed is released and the second clutch C2 is engaged. That is, it is obtained by engaging the second clutch C2 and the third clutch C3.
[0056]
In the fifth speed, the input rotation from the input shaft Input is input to the third carrier PC3 via the center member CM by the engagement of the third clutch C3. At the same time, when the second clutch C2 is engaged, the rotation from the first carrier PC1 decelerated by the first planetary gear G1 is transferred to the third sun gear S3 and the fourth sun gear S4 via the second sun gear S2 and the first connecting member M1. Entered.
[0057]
Therefore, in the third planetary gear G3, the input rotation is input to the third carrier PC3, and the rotation decelerated by the first planetary gear G1 is input to the third sun gear S3. The third ring gear R3 passes through the second connecting member M2 and is output to the output gear Output.
[0058]
That is, in the fifth speed, as shown in the collinear diagram of FIG. 3, the engagement point of the third clutch C3, which uses the rotation of the third carrier PC3 as an input rotation, and the first carrier PC1 and the second sun gear S2 are integrated. The rotation input from the input shaft Input is accelerated and output from the output gear Output.
[0059]
The torque flow at the fifth speed is as shown in FIG. 6 (a). The second clutch C2, the third clutch C3, each member indicated by bold lines, the first planetary gear G1 and the third planetary gear indicated by hatching. Torque acts on G3 (excluding the fourth sun gear S4). As for the second planetary gear G2, the unconstrained second ring gear R2 only revolves around the second sun gear S2 along with the output rotation of the second pinion P2, and only functions as a rotating member. It is not involved in torque transmission.
[0060]
(6-speed)
As shown in FIG. 2, the sixth speed releases the second clutch C2 at the fifth speed and engages the second brake B2. That is, it is obtained by engaging the third clutch C3 and the second brake B2.
[0061]
In the sixth speed, the input rotation from the input shaft Input is input to the third carrier PC3 through the center member CM by the engagement of the third clutch C3. At the same time, the fourth sun gear S4 is fixed by engaging the second brake B2.
[0062]
Therefore, in the third planetary gear G3, the input rotation is input to the third carrier PC3 and the fourth sun gear S4 is fixed, and the rotation that is accelerated from the input rotation is transmitted from the third ring gear R3 to the second ring gear R3. After passing through the connecting member M2, it is output to the output gear Output.
[0063]
That is, in the sixth speed, as shown in the collinear diagram of FIG. 3, the input point is the engagement point of the second brake B2 for fixing the fourth sun gear S4 of the third planetary gear G3 and the rotation of the third carrier PC3. It is defined by a line connecting the engagement point of the third clutch C3, and the rotation input from the input shaft Input is increased and output from the output gear Output.
[0064]
The torque flow at the sixth speed is as shown in FIG. 6 (b). The third clutch C3, the second brake B2, each member indicated by the thick line, and the third planetary gear G3 indicated by the hatching (the third sun gear S3). Torque).
[0065]
(Reverse 1st speed)
As shown in FIG. 2, the first reverse speed is obtained by engaging the second clutch C2 and the first brake B1.
[0066]
At the first reverse speed, the reduced rotation from the first planetary gear G1 is input to the third sun gear S3 via the second sun gear S2 and the first connecting member M1 by the engagement of the second clutch C2. On the other hand, the third carrier PC3 is fixed to the case by the engagement of the first brake B1.
[0067]
Therefore, in the third planetary gear G3, the forward reduction rotation that is decelerated by the first planetary gear G1 is input to the third sun gear S3, the third carrier PC3 is fixed to the case, and from the third ring gear R3, The decelerated reverse rotation passes through the second connecting member M2 and is output to the output gear Output.
[0068]
That is, as shown in the collinear diagram of FIG. 3, the first reverse speed is determined by the engagement point of the second clutch C2 in which the reduced rotation from the first planetary gear G1 is the input rotation to the third sun gear S3, and the third carrier. It is defined by a line connecting the engagement point of the first brake B1 that stops the rotation of the PC3, and the rotation input from the input shaft Input is decelerated in the reverse direction and output from the output gear Output.
[0069]
The torque flow at the first reverse speed is as shown in FIG. 7, and the second clutch C2, the first brake B1, each member indicated by a bold line, the first planetary gear G1 and the third planetary gear G3 indicated by hatching ( Torque is applied to the third sun gear S3). As for the second planetary gear G2, the unconstrained second ring gear R2 only revolves around the second sun gear S2 along with the output rotation of the second pinion P2, and only functions as a rotating member. It is not involved in torque transmission.
[0070]
FIG. 8 is an actual configuration diagram of the gear transmission of the above configuration.
In the transmission case 3, the input shaft 1 is rotatably supported with respect to the transmission case 3. The front end opening of the transmission case 3 on the engine side is closed by a pump case comprising a pump housing 5 and a pump cover 6, and the pump shaft passes through the input shaft 1 and is supported by a torque converter ( An engine (not shown), which is a power source, is drivingly coupled via a not shown.
[0071]
The rear end of the input shaft 1 is rotatably supported by an end lid 7 at the rear end of the transmission case 3. An intermediate wall 8 is provided in the middle of the transmission case 3 in the axial direction, the output gear 2 is rotatably supported on the intermediate wall 8, and the input shaft 1 is rotatable through a hollow shaft 9 in the center hole of the intermediate wall 8. To support.
[0072]
The first planetary gear G1 is disposed in a front portion (front end portion of the transmission) defined between the oil pump case including the pump housing 5 and the pump cover 6 and the intermediate wall 8, and the first planetary gear. The second clutch C2 is arranged so as to surround the gear G1. The first planetary gear G1 engages with the central boss portion 6a projecting rearward of the pump cover 6 so as to function as a reaction force receiver, so that the first planetary gear G1 cannot rotate at all times. The ring gear R1 is coupled to the outer periphery of the flange 10 extending radially outward from the input shaft 1.
[0073]
A clutch drum 11 is provided so as to extend radially outward from the drum support portion 6b of the pump cover 6 so as to surround the first ring gear R1, and is connected to the inner periphery of the clutch drum 11 and the second sun gear S2. The clutch plate 12 and the clutch piston 13 which are alternately arranged as friction materials splined to the outer periphery of the clutch hub 4 and the clutch piston 13 constitute a second clutch C2, and the second clutch C2 is arranged on the outer periphery of the first planetary gear G1. Deploy.
[0074]
The clutch piston 13, which is the operating piston of the second clutch C2, is disposed between the oil pump case including the pump housing 5 and the pump cover 6 and the first planetary gear G1. Thus, the clutch piston 13 is accommodated in the end wall 11a of the clutch drum 11 facing the first planetary gear G1.
[0075]
The second clutch piston 13 receives the hydraulic pressure supplied from the control valve body via the oil passage 14 and strokes to the right in the drawing to fasten the second clutch C2.
[0076]
A drum-shaped connecting member 53 extending radially outward from the front end of the hollow shaft 9 on the engine side and surrounding the second clutch C2 is provided, and the front end of the connecting member 53 is connected to the clutch drum 11. By coupling, the first carrier PC1 is coupled. Here, the first carrier PC1 constitutes a rotating outer member of the first planetary gear G1.
[0077]
In the rear space defined between the intermediate wall 8 and the end lid 7, the second planetary gear G2 and the third planetary gear G3, the first clutch C1 and the third clutch C3, the first brake B1 and the second Brake B2 is stowed. As shown in FIGS. 8 and 9, the second planetary gear G2 is arranged closer to the oil pump than the third planetary gear G3.
[0078]
The second sun gear S2 of the second planetary gear G2 and the third sun gear S3 of the third planetary gear G3 are integrated by the first connecting member M1 and are rotatably supported on the input shaft 1. A first clutch C1 is provided on the outer side in the radial direction of the second planetary gear G2. The first clutch C1 extends radially outward from the hollow shaft 9, and then extends rearward in the axial direction to reach the outer periphery of the second ring gear R2, and the first clutch drum The clutch plates 16 alternately arranged as friction materials splined to the inner periphery of the ring 15 and the outer periphery of the ring gear R2 and the clutch piston 19 as an actuator for pressing the clutch plate 16 constitute a first clutch C1.
[0079]
The clutch piston 19 is a radially extending portion of the first clutch drum 15 and is housed in a piston housing portion provided on the second planetary gear G2 side. Then, the first clutch C1 is engaged and released by supplying and discharging hydraulic pressure through an oil passage provided in the first clutch drum.
[0080]
The third planetary gear G3 is the double sun gear type planetary gear set described above, but the tooth width of the third ring gear R3 is made smaller than the tooth width of the third pinion P3. Thereby, a space can be secured radially outward of the third pinion P3 (a position where the third ring gear R3 is not configured). Then, the third ring gear R3 is positioned so as to mesh with the third pinion P3 at the end close to the second planetary gear set G2, and the third ring gear R3 is connected to the second carrier PC2 of the second planetary gear set G2. Bind at M2.
[0081]
The second connecting member M2 is connected to an outer member 17 that extends to the axial direction engine side on the outer peripheral side of the first clutch drum 15. The second planetary gear G2 is provided between the intermediate wall 8 and connected to the output gear 2 rotatably supported by the output gear support 8a of the intermediate wall 8.
[0082]
A third clutch C3 is disposed on the rear end side of the axial transmission of the third planetary gear G3. The third clutch C3 is connected to the rear end of the input shaft 1 and is rotated integrally with the input shaft 1. The third clutch C3 is connected to the center member CM and is rotated integrally therewith. The clutch plate 21 and the clutch piston 23 that are alternately arranged as friction materials splined to the inner periphery of the clutch drum 22 and the outer periphery of the third clutch hub 20 constitute a third clutch C3. As described above, the third clutch C3 is arranged so as to overlap the third planetary gear G3 in the axial direction, thereby reducing the radial size.
[0083]
A part of the second planetary gear G2 and a part of the third planetary gear G3 overlap in the radial direction, and a first brake B1 and a one-way clutch OWC are disposed on the outer peripheral side of the outer member 17. The first brake B1 and the one-way clutch OWC are connected to the third carrier PC3, and extend to the outer peripheral side of the outer member 17, the inner periphery of the transmission case 3, and the first brake hub 27. The clutch plate 28 and the clutch piston 29, which are alternately arranged as friction materials splined to the outer circumference, constitute the first brake B1. A one-way clutch OWC is fixed between the first brake hub 27 and the transmission case 3 by spline engagement, and only one-way rotation of the first brake hub 27 is allowed.
[0084]
First A second brake B2 is disposed outside the three planetary gear G3 in the radial direction. The second brake B2 is connected to the fourth sun gear S4, extends radially outward along the third planetary gear G3, the inner periphery of the transmission case 3, and the second brake. Clutch plates alternately arranged as friction materials splined to the outer periphery of the hub 24 25 The clutch piston 26 constitutes the second brake B2. The clutch pistons 26 and 29 of the first and second brakes B1 and B2 are provided with disc springs 26a and 29a, respectively, and urged to the release side. Therefore, there is no need to configure a spring retainer or the like, and the configuration can be made compact.
[0085]
FIG. 9 is a schematic diagram showing the arrangement of the first to third planetary gears G1, G2, and G3, the arrangement of the first to third clutches C1, C2, and C3, and the arrangement of the first brake B1 and the second brake B2. is there. In the drawing, P represents an arrangement of pistons (fastening actuators) of the respective fastening elements. Hereinafter, the effects of the present embodiment will be listed below.
[0086]
(1) The second clutch C2 is disposed radially outward of the first planetary gear G1 so as to overlap the first planetary gear G1 in the radial direction, and the second planetary gear G2 is radially outward of the second planetary gear G2. The first clutch C1 is disposed so as to overlap the gear G2 in the radial direction, and the input portion and the third planetary gear G3 are arranged at a position overlapping the axial direction in the rear end side of the transmission of the third planetary gear G3. By arranging the third clutch C3 that is directly connected to the outer periphery of the transmission mechanism, the outer periphery of the transmission mechanism end can be significantly reduced, and a space for passing side members or the like can be secured widely (corresponding to claim 1). ).
[0087]
(2) The third clutch C3 is composed of a clutch drum 22 having a drum bottom surface on the rear end side of the transmission. The second planetary gear is located on the inner periphery of the clutch drum 22 with the third planetary gear G3 interposed therebetween. By disposing the piston 23 on the side opposite to G2, it is possible to supply hydraulic pressure from the end lid 7 side to the third clutch, and it is possible to simplify the oil passage compared to hydraulic supply from the shaft center. Yes (corresponding to claim 3).
[0088]
(3) Since the first brake B1 and the second brake B2 are arranged closer to the rear end side of the transmission than the second planetary gear G2, the members from the third carrier PC3 to the first brake B1 are shortened, and The members from the fourth sun gear S4 to the second brake B2 can be shortened, and the weight can be reduced (corresponding to claim 4).
[0089]
(4) Since the first brake B1 is disposed radially outward from the first clutch C1 and the second clutch C2, the axial direction can be shortened (corresponding to claim 5).
[0090]
(5) Since the second brake B2 is arranged radially outward of the pinion P3 so as to overlap with a part of the double sun gear type third planetary gear G3, the ring gear of the third planetary gear G3 It is possible to shorten the members from the fourth sun gear S4 while effectively using the space where the is not configured, and to reduce the weight and size of the transmission (corresponding to claim 6). .
[0091]
(6) By arranging the first brake B1 closer to the reduction planetary gear than the second brake B2, it is possible to shorten the members from the third carrier PC3 and the fourth sun gear S4, and to reduce the weight of the transmission. And compactness can be achieved (corresponding to claim 8).
[0092]
(7) Since the shift hydraulic pressure control device that obtains the sixth forward speed and the first reverse speed is provided, the effects listed below can also be obtained (corresponding to claim 9).
(1) Ring gear input can be achieved for the so-called Ishimaru type planetary gear train composed of the second planetary gear G2 and the third planetary gear G3 in the first and second gears, which are large torque inputs, The transmission can be made compact.
(2) Since the torque circulation is eliminated at the second speed, the transmission efficiency at the second speed is improved and the fuel efficiency can be improved.
[0093]
(Second embodiment)
The second embodiment is a gear transmission for an automatic transmission corresponding to the inventions described in claims 2, 3, 4, 5, 7, 8, 9, and 11. Since the skeleton diagram is the same as that of the first embodiment, and the actual configuration diagram is the same on the axial engine side from the output gear 2, only different points will be described.
[0094]
FIG. 10 is an actual configuration diagram of a gear transmission showing a gear transmission for an automatic transmission according to a second embodiment.
[0095]
A third clutch C3 is disposed radially outward and overlaps a part of the third planetary gear G3 on the rear end side of the transmission in the radial direction. The third clutch C3 is connected to the rear end portion of the input shaft 1, is extended to the outer periphery of the third radial planetary gear G3, and is connected to the third clutch drum 220 that rotates integrally with the input shaft 1 and the center member CM. The third clutch hub 200 that extends to the outer periphery of the third planetary gear G3 in the radial direction and rotates integrally with the center member CM, and the spline mesh with the inner periphery of the third clutch drum 220 and the outer periphery of the third clutch hub 200, respectively. As the friction material, the clutch plate 21 and the clutch piston 23 which are alternately arranged constitute a third clutch C3.
[0096]
The third clutch drum 220 is provided with a piston receiving portion 220a on the inner circumference of the drum bottom portion provided on the rear end side of the transmission. A drum support portion 302 protruding from the transmission case 3 is provided on the outer peripheral side of the transmission of the third clutch drum 220 and on the inner diameter side of the piston housing portion 220a. In addition to supporting in the direction, a hydraulic supply / discharge port to the piston 23 is provided.
[0097]
A first brake B1 and a one-way clutch OWC are disposed on the outer peripheral side of the outer member 27 that radially overlaps a part of the second planetary gear G2 and a part of the third planetary gear G3. The first brake B1 and the one-way clutch OWC are provided on the outer peripheral side of the outer member 27 connected to the third carrier PC3. The first brake hub 27a provided on the outer peripheral side of the outer member 27 and the first brake housing portion 301b on the inner peripheral side of the brake housing 301 provided in the transmission case 3 are spline-fitted, respectively. As a material, the clutch plate 28 and the clutch piston 29 which are alternately arranged constitute a first brake B1. A one-way clutch OWC is fixed by spline engagement between the first brake hub 27a and the transmission case 3, and only one-way rotation of the outer member 27 is allowed.
[0098]
Further, a second brake B2 is provided on the outer peripheral side of the first brake B1 and on the outer periphery of the rear end side of the transmission of the brake housing 301. The second brake B2 is connected to the fourth sun gear S4, and as a friction material splined to the radial member 240 extending to the outer periphery of the brake housing 301 in the radial direction and the inner peripheral side of the transmission case 3, respectively. The clutch plate 25 and the clutch piston 26 which are alternately arranged constitute the second brake B2.
[0099]
That is, the brake housing 301 is provided, the first brake B1 is disposed on the transmission front end side of the brake housing 301, and the second brake B2 is disposed on the transmission rear end side of the brake housing 301 and on the outer peripheral side of the first brake B1. By arranging this, the axial direction is shortened.
[0100]
FIG. 11 is a schematic diagram showing the arrangement of the first to third planetary gears G1, G2, and G3, the arrangement of the first to third clutches C1, C2, and C3, and the arrangement of the first brake B1 and the second brake B2. is there. In the drawing, P represents an arrangement of pistons (fastening actuators) of the respective fastening elements. The operational effects of the second embodiment are listed below in addition to the operational effects described in (2), (3), (4), (6), (7) of the first embodiment.
[0101]
(8) A second clutch C2 is arranged radially outward of the first planetary gear G1 so as to overlap the first planetary gear G1 in the radial direction, and the second planetary gear G2 is radially outward of the second planetary gear G2. The first clutch C1 is arranged so as to overlap the gear G2 in the radial direction, and the third clutch C3 that directly connects the input unit and the third planetary gear G3 is arranged outside the third planetary gear G3 in the radial direction. As a result, the axial length of the transmission can be greatly reduced, and vehicle mountability can be secured (corresponding to claim 2).
[0102]
(9) Since the first brake B1 and the second brake B2 are arranged so as to overlap in the radial direction, the axial length of the transmission can be further shortened (corresponding to claim 7).
[0103]
(10) First clutch C 1 and The first brake B1 and the second brake B2 are arranged radially outward without overlapping in the axial direction, and the first brake B1 and the second brake B2 are arranged so as to overlap in the radial direction. The axial length of the machine can be further shortened (corresponding to claim 11).
[0104]
(Third embodiment)
The third embodiment is a gear transmission for an automatic transmission corresponding to the inventions described in claims 1, 3, 4, 5, 6, 8, 9, and 10. Since the skeleton diagram and the actual configuration diagram are the same as those in the first embodiment, only different points will be described.
FIG. 12 is a schematic diagram showing the arrangement of the first to third planetary gears G1, G2, and G3, the arrangement of the first to third clutches C1, C2, and C3, and the arrangement of the first brake B1 and the second brake B2. is there. In the drawing, P represents an arrangement of pistons (fastening actuators) of the respective fastening elements.
[0105]
In the third embodiment, a double pinion type planetary gear is provided as the first planetary gear G1. In the first embodiment, the rotation of the input shaft Input is input to the first ring gear R1 and output from the first carrier PC1, but in the third embodiment, it is input to the first carrier PC1 and output from the first ring gear R1. The output point is different. Hereinafter, the operational effects of the third embodiment are the same as the operational effects described in (1), (2), (3), (4), (5), (6), (7) of the first embodiment. In addition, the following effects can be obtained.
[0106]
(11) The first planetary gear G1 is a double pinion planetary gear, and the first carrier PC1 input and the first ring gear R1 output reduce the radial member from the input shaft Input to the first carrier PC1. And the strength can be improved (corresponding to claim 10).
[0107]
(Fourth embodiment)
The fourth embodiment is a gear transmission for an automatic transmission corresponding to the inventions described in claims 2, 3, 4, 5, 7, 8, 9, 10, and 11. Since the skeleton diagram and the actual configuration diagram are the same as those of the second embodiment, only different points will be described.
FIG. 13 is a schematic diagram showing the arrangement of the first to third planetary gears G1, G2, and G3, the arrangement of the first to third clutches C1, C2, and C3, and the arrangement of the first brake B1 and the second brake B2. is there. In the drawing, P represents an arrangement of pistons (fastening actuators) of the respective fastening elements.
[0108]
In the fourth embodiment, a double pinion type planetary gear is provided as the first planetary gear G1. In the second embodiment, the rotation of the input shaft Input is input to the first ring gear R1 and output from the first carrier PC1, but in the fourth embodiment, it is input to the first carrier PC1 and output from the first ring gear R1. The output point is different. Regarding the operational effects of the fourth embodiment, in addition to the operational effects of the second embodiment, the same operational effects as the operational effects of the third embodiment can be obtained.
[0109]
Although the gear transmission for automatic transmission according to the present invention has been described based on the first to fourth embodiments, the specific configuration is not limited to these embodiments, and Design changes and additions are allowed without departing from the scope of the present invention described in the claims of the scope. Further, the gear transmission for an automatic transmission according to the present invention is useful as a transmission for a vehicle that requires a multi-stage shift stage, and in particular, a drive source output shaft of an automobile in which an engine or a motor is mounted as a drive source. It is suitable for use in a gear transmission part of an automatic transmission connected to the.
[Brief description of the drawings]
FIG. 1 is a skeleton diagram showing a gear transmission for an automatic transmission according to a first embodiment.
FIG. 2 is a fastening table of a gear transmission for an automatic transmission according to a first embodiment.
FIG. 3 is an alignment chart in the gear transmission for an automatic transmission according to the first embodiment.
FIG. 4 is a torque flow diagram of first speed and second speed in the gear transmission for an automatic transmission according to the first embodiment.
FIG. 5 is a third- and fourth-speed torque flow diagram in the automatic transmission gear transmission according to the first embodiment;
FIG. 6 is a torque flow diagram of fifth and sixth speeds in the gear transmission for an automatic transmission according to the first embodiment.
FIG. 7 is a torque flow diagram of the first reverse speed in the gear transmission for an automatic transmission according to the first embodiment.
FIG. 8 is a cross-sectional view showing an actual configuration diagram of a gear transmission for an automatic transmission according to a first embodiment.
FIG. 9 is a schematic diagram showing a clutch and brake arrangement of the gear transmission for an automatic transmission according to the first embodiment.
FIG. 10 is a sectional view showing an actual configuration diagram of a gear transmission for an automatic transmission according to a second embodiment.
FIG. 11 is a schematic diagram showing the arrangement of clutches and brakes of a gear transmission for an automatic transmission according to a second embodiment.
FIG. 12 is a schematic view showing a clutch and brake arrangement of a gear transmission for an automatic transmission according to a third embodiment.
FIG. 13 is a schematic view showing a clutch and brake arrangement of a gear transmission for an automatic transmission according to a fourth embodiment.
[Explanation of symbols]
C1 1st clutch
C2 Second clutch
C3 3rd clutch
B1 First brake
B2 Second brake
G1 1st planetary gear
G2 Second planetary gear
G3 3rd planetary gear

Claims (11)

An input unit for inputting rotation from a driving source;
An output unit that is coaxially disposed in the input unit and transmits the output rotation of the gear transmission,
A plurality of planetary gear sets including a compound planetary gear train capable of providing a large number of conduction paths between the input unit and the output unit;
Selectively connect / disconnect to select one of the conduction paths of the plurality of planetary gear sets, shift the rotation from the input unit at a corresponding gear ratio, and output to the output unit. Three clutches and two brakes,
In a gear transmission for an automatic transmission in which at least six forward speeds and one reverse speed can be selected by a combination of engagement and release of these clutches and brakes,
One planetary gear set of the plurality of planetary gear sets is a reduction planetary gear set that constantly decelerates and outputs the input rotation,
A compound planetary gear train composed of the remaining two planetary gear sets, one planetary gear set having two sun gears, a common pinion meshing with the two sun gears, and one meshing with the pinion A double sun gear type planetary gear set comprising a ring member, a carrier rotatably supporting the pinion, a center member extending from between the two sun gears and rotating integrally with the carrier, and the other planetary gear set. The gear set is a single pinion type planetary gear set including one sun gear, a pinion meshing with the sun gear, a ring gear meshing with the pinion, and a carrier that rotatably supports the pinion.
An input member for reducing rotation from the planetary gear set for reduction to the compound planetary gear train is a member that is connected to the ring gear of the single pinion type planetary gear set ,
From the power source to the planetary gear set for deceleration, single pinion type planetary gear set, double sun gear type planetary gear set,
Of the three clutches, two clutches are connected to a reduction rotation output from the reduction planetary gear set, a member connected to the ring gear of the single pinion planetary gear set, and a sun gear of the single pinion planetary gear set. The first and second clutches that selectively connect and disconnect the member, and the remaining one clutch is the third clutch that selectively connects and disconnects the rotation of the input portion and the center member ,
A multi-plate friction element of a second clutch, which is a jump transmission clutch including a reverse gear among two clutches that connect and disconnect the reduction rotation, is arranged on the outer side in the radial direction of the planetary gear set for reduction,
Radially outwardly of the single pinion type planetary gear set, the multi-plate friction of the first clutch is a low speed stage clutch that Sessu sectional and members for connecting to the single-pinion type planetary gear set ring gear and the reduced rotation Place the element,
A multi-plate of a third clutch which is a high-speed transmission clutch that directly connects the input portion and the double sun gear planetary gear set at a position overlapping the double sun gear planetary gear set on the rear end side of the transmission and in the axial direction. A gear transmission for an automatic transmission, wherein a friction element is arranged. An input unit for inputting rotation from a driving source;
An output unit that is coaxially disposed in the input unit and transmits the output rotation of the gear transmission,
A plurality of planetary gear sets including a compound planetary gear train capable of providing a large number of conduction paths between the input unit and the output unit;
Selectively connect / disconnect to select one of the conduction paths of the plurality of planetary gear sets, shift the rotation from the input unit at a corresponding gear ratio, and output to the output unit. Three clutches and two brakes,
In a gear transmission for an automatic transmission in which at least six forward speeds and one reverse speed can be selected by a combination of engagement and release of these clutches and brakes,
One planetary gear set of the plurality of planetary gear sets is a reduction planetary gear set that constantly decelerates and outputs the input rotation,
A compound planetary gear train composed of the remaining two planetary gear sets, one planetary gear set having two sun gears, a common pinion meshing with the two sun gears, and one meshing with the pinion A double sun gear type planetary gear set comprising a ring member, a carrier rotatably supporting the pinion, a center member extending from between the two sun gears and rotating integrally with the carrier, and the other planetary gear set. The gear set is a single pinion type planetary gear set including one sun gear, a pinion meshing with the sun gear, a ring gear meshing with the pinion, and a carrier that rotatably supports the pinion.
An input member for reducing rotation from the planetary gear set for reduction to the compound planetary gear train is a member that is connected to the ring gear of the single pinion type planetary gear set ,
From the power source to the planetary gear set for deceleration, single pinion type planetary gear set, double sun gear type planetary gear set,
Of the three clutches, two clutches are connected to a reduction rotation output from the reduction planetary gear set, a member connected to the ring gear of the single pinion planetary gear set, and a sun gear of the single pinion planetary gear set. The first and second clutches that selectively connect and disconnect the member, and the remaining one clutch is the third clutch that selectively connects and disconnects the rotation of the input portion and the center member ,
A multi-plate friction element of a second clutch, which is a jump transmission clutch including a reverse gear among two clutches that connect and disconnect the reduction rotation, is arranged on the outer side in the radial direction of the planetary gear set for reduction,
Radially outwardly of the single pinion type planetary gear set, the multi-plate friction elements of the first clutch is a low speed stage clutch that Sessu cross members for connecting to the single-pinion type planetary gear set ring gear and the reduced rotation And place
A multi-plate friction element of a third clutch, which is a high-speed transmission clutch that directly connects the input portion and the double sun gear planetary gear set, is arranged radially outward of the double sun gear planetary gear set. Gear transmission for transmission. The gear transmission for an automatic transmission according to claim 1 or 2,
The third clutch is engaged with the input portion, and a drum having a drum bottom portion on the rear end side of the transmission with respect to the actuator that presses the multi-plate friction element of the third clutch, and on the inner peripheral side of the drum Composed of arranged multi-plate friction elements,
An automatic transmission gear characterized in that an actuator for pressing the third clutch is arranged on the opposite side of the single type planetary gear set across the double sun gear type planetary gear set and on the inner periphery of the drum. Transmission device. The gear transmission for an automatic transmission according to any one of claims 1 to 3,
The two brakes are first and second brakes capable of fixing the sun gear and the carrier of the double sun gear type planetary gear set, and these two brakes are closer to the transmission rear end side than the single pinion type planetary gear set. A gear transmission for an automatic transmission, characterized by being arranged. The gear transmission for an automatic transmission according to claim 4,
A gear transmission for an automatic transmission, wherein the first brake is disposed radially outward from the first and second clutches. The gear transmission for an automatic transmission according to claim 4,
A gear transmission for an automatic transmission, wherein the second brake is arranged radially outward of the pinion so as to overlap a part of the double sun gear type planetary gear set in the radial direction. In the automatic transmission transmission according to any one of claims 2 to 5,
A gear transmission for an automatic transmission, wherein the first brake and the second brake are arranged to overlap in a radial direction. The gear transmission for an automatic transmission according to any one of claims 4 to 7,
The first brake is a brake for fixing a carrier of a double sun gear type planetary gear set, and the second brake is a brake for fixing a sun gear of the double sun gear type planetary gear set on the side far from the single pinion type planetary gear set, A gear transmission for an automatic transmission, wherein the first brake is disposed closer to the planetary gear set for reduction than the second brake. The gear transmission for an automatic transmission according to any one of claims 1 to 8,
Of the three planetary gear sets, the planetary gear set for reduction closest to the input unit is a planetary gear set comprising a first sun gear, a first ring gear, and a first carrier supporting a pinion meshing with these gears. Configure
The single pinion type planetary gear set in a position close to the input unit is constituted by a planetary gear set comprising a second sun gear, a second ring gear, and a second carrier supporting a pinion meshing with these gears,
The double sun gear type planetary gear set located farthest from the input unit is supported by a third sun gear on the side close to the input unit and a fourth sun gear on the side far from the input unit, and a common pinion that meshes with these sun gears. A planetary gear set comprising three carriers and one third ring gear meshing with the common pinion;
Coupling the input to the first ring gear;
Coupling the output part to the second carrier and the third ring gear combination;
A first clutch that selectively connects and disconnects the first carrier and the second ring gear;
A second clutch that selectively connects and disconnects the first carrier, the second sun gear, and the third sun gear;
A third clutch capable of selectively connecting and disconnecting the third carrier and the input unit;
A first brake for selectively fixing a third carrier;
A second brake for selectively fixing the fourth sun gear;
The first speed is achieved by engaging the first clutch and the first brake, the second speed is achieved by engaging the first clutch and the second brake, the third speed is established by engaging the first clutch and the second clutch, and the first speed and the third clutch 4th speed by engagement, 5th speed by engagement of 2nd clutch and 3rd clutch, 6th speed by engagement of 3rd clutch and 2nd brake, and reverse gear by engagement of 2nd clutch and 1st brake, respectively A gear transmission for an automatic transmission, characterized in that it can be selected. The gear transmission for an automatic transmission according to any one of claims 1 to 8 ,
A double pinion comprising a planetary gear set for reduction closest to the input portion among three planetary gear sets, a first sun gear, a first ring gear, and a first carrier supporting two pinions engaged with these gears. It consists of a type planetary gear set,
The single pinion type planetary gear set in a position close to the input unit is constituted by a planetary gear set comprising a second sun gear, a second ring gear, and a second carrier supporting a pinion meshing with these gears,
The double sun gear type planetary gear set located farthest from the input unit is supported by a third sun gear on the side close to the input unit and a fourth sun gear on the side far from the input unit, and a common pinion that meshes with these sun gears. A planetary gear set comprising three carriers and one third ring gear meshing with the common pinion;
Coupling the input to a first carrier;
Coupling the output part to the second carrier and the third ring gear combination;
A first clutch that selectively connects and disconnects the first ring gear and the second ring gear;
A second clutch that selectively connects and disconnects the first ring gear, the second sun gear, and the third sun gear;
A third clutch capable of selectively connecting and disconnecting the third carrier and the input unit;
A first brake for selectively fixing a third carrier;
A second brake for selectively fixing the fourth sun gear;
The first speed is achieved by engaging the first clutch and the first brake, the second speed is achieved by engaging the first clutch and the second brake, the third speed is established by engaging the first clutch and the second clutch, and the first speed and the third clutch 4th speed by engagement, 5th speed by engagement of 2nd clutch and 3rd clutch, 6th speed by engagement of 3rd clutch and 2nd brake, and reverse gear by engagement of 2nd clutch and 1st brake, respectively A gear transmission for an automatic transmission, characterized in that it can be selected. The gear transmission for an automatic transmission according to claim 9 or 10,
The output unit is disposed between the planetary gear set for reduction and the single pinion type planetary gear set, and is coupled to an interconnected body of the second carrier and the third ring gear via a cylindrical connecting member,
It said first clutches are arranged radially inwardly of the tubular connecting member and the first and second brakes arranged radially outward without overlapping tubular connection member and the axial direction ,
The first brake is disposed radially inward of the second brake so as to overlap in the radial direction,
The first brake is disposed radially inward from the second brake and coupled to an outer member extending radially outward from the third carrier,
A second brake coupled to a radial member extending radially outward from the fourth sun gear;
A gear transmission for an automatic transmission, wherein a third clutch is disposed radially outward of the double sun gear planetary gear set and is coupled to a third carrier via the center member.

Images