JP6167814B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission mounted on a vehicle, and relates to a stepped automatic transmission provided with a planetary gear set and a frictional engagement element.

  In recent years, in the technical field of stepped automatic transmissions, research and development for multi-stage automatic transmissions has been conducted for the purpose of improving vehicle fuel efficiency.

  Patent Document 1 proposes a technique in which a planetary gear set is added to increase the number of automatic transmissions. And, according to Patent Document 1, since there are fewer frictional engagement elements in a disengaged state (non-engaged state: a state where hydraulic pressure is not supplied) in each shift stage as compared to multistage by adding frictional engagement elements, Multiple stages can be performed while reducing the friction loss due to the frictional engagement elements in the released state.

  However, in Patent Document 1, since the automatic transmission is enlarged in the axial direction due to the addition of the planetary gear set, the mountability of the automatic transmission on the vehicle may be deteriorated. In particular, when the automatic transmission is mounted on the vehicle such that the axial direction is the same as the vehicle width direction of the vehicle, the mounting property on the vehicle is deteriorated.

  Patent Document 2 discloses a technique in which a planetary gear set is disposed on the inner and outer circumferences. According to the technique disclosed in Patent Document 2, since it is possible to prevent the axial dimension of the automatic transmission from increasing even when a planetary gear set is added, the problem of Patent Document 1 described above is solved. can do.

JP 2009-174626 US Patent Application Publication No. 2012/0295754 (FIG. 9)

  According to the technique of Patent Document 2, an increase in the axial dimension of the automatic transmission can be prevented by arranging the planetary gear sets so as to overlap the inner and outer peripheries (hereinafter referred to as a multi-stage planetary gear set). However, as disclosed in Patent Document 2, a connecting member (a planetary gear set and a frictional engagement element or a planetary gear set) that connects each component in the automatic transmission between the input shaft and the multi-stage planetary gear set in the radial direction. Therefore, the automatic transmission has a larger radial dimension than the radial dimension in which the planetary gear sets are overlapped on the inner and outer circumferences.

  Therefore, when a planetary gear set is added to increase the number of stages of the automatic transmission in order to prevent an increase in friction loss, the automatic transmission has a problem of increasing axial and radial dimensions.

  In response to this problem, the present invention increases the axial dimension of the automatic transmission by changing the planetary gear set added at the time of multi-stage to a multi-stage planetary gear set in which a plurality of planetary gear sets are arranged on the inner and outer circumferences. In addition, the arrangement of the power transmission elements is devised in order to increase the number of stages while preventing the increase in the radial dimension without disposing a member between the radial direction of the multi-stage planetary gear set and the input shaft. is there.

A first invention related to the present application is an automatic transmission that includes an input shaft, a transmission mechanism having three planetary gear sets disposed on a concentric shaft of the input shaft, and an output unit. The mechanism is a multi-stage planetary gear set configured by superimposing two planetary gear sets on the inner and outer circumferences of the three planetary gears, the other planetary gear sets that are the remaining planetary gear sets of the three planetary gear sets, and an output unit, has an output connecting portion to contact a plurality of stages planetary gear set and other planetary gear sets, and one side in the axial direction than the plural stages planetary gears, and an output unit, and other of the planetary gear set is disposed, further, the automatic The transmission includes a first sun gear, a first carrier, and a first ring gear, and a single pinion The first planetary gear set configured by type, the second sun gear, the second carrier, and the second ring gear, and the second planetary gear set configured by double pinion type, the third sun gear, the third carrier, and the third A third planetary gear set including a ring gear and configured with a single pinion type; a fourth planetary gear set including a fourth sun gear, a fourth carrier and a fourth ring gear and configured with a double pinion type; And the second brake, the first, second, and third clutches, the transmission case, the first carrier and the second sun gear that are always in communication with the input shaft, and the first that is in constant communication with the output unit. Before connecting and disconnecting one ring gear and the fourth ring gear, and the first sun gear and the third sun gear The first clutch, the second clutch that connects and disconnects the third sun gear and the third ring gear, the third clutch that connects and disconnects the second carrier and the third sun gear, the second carrier, and the transmission case A first brake that connects and disconnects the second carrier, a second brake that connects and disconnects the fourth carrier and the transmission case, the third carrier and the second ring gear that are always in contact, and the third ring gear that is always in contact. The fourth sun gear, and the multi-stage planetary gear set includes the third planetary gear set disposed on the inner peripheral side thereof and the fourth planetary gear set disposed on the outer peripheral side thereof. In addition, the other planetary gear set is constituted by the first planetary gear set .

  According to the first invention, the output portion and the other planetary gear set are collectively arranged on one side in the axial direction from the multiple-stage planetary gear set, so that the output communication portion (the output portion and the multiple-stage planetary gear set and the other Is connected to one side in the axial direction of the multi-stage planetary gear set.

As a result, the output connecting member does not exist compared to the case where the output connecting member is disposed between the multi-stage planetary gear set and the input shaft in the radial direction. An increase in the radial dimension of the machine can be prevented. Further, according to the first aspect of the present invention, the output communication for communicating the fourth ring gear of the fourth planetary gear set and the first ring gear of the first planetary gear set arranged on the outer peripheral side of the multi-stage planetary gear set and the output unit. The portion is arranged on one side in the axial direction with respect to the multi-stage planetary gear set. Thereby, compared with the case where an output connection member needs to be disposed between the inner peripheral surface of the multistage planetary gear set (the third sun gear of the third planetary gear set) and the outer peripheral surface of the input shaft, the output connection member Since the number of members can be reduced, the diameter of the plurality of planetary gear sets stacked on the inner and outer circumferences can be reduced, and an increase in the radial dimension of the automatic transmission can be prevented.

According to a second invention related to the present application, in the first invention, the automatic transmission is mounted on the vehicle such that the axial direction thereof is the vehicle width direction of the vehicle.

According to the second invention, since the planetary gear set is disposed in the automatic transmission so as to overlap the inner and outer circumferences (multiple planetary gear set), the overall length (axial direction) of the automatic transmission can be shortened.

  Accordingly, it is possible to prevent deterioration in the mounting property on the vehicle when the automatic transmission is mounted on the vehicle such that the axial direction of the automatic transmission is the vehicle width direction of the vehicle.

  According to the present invention, when a planetary gear set is added to increase the number of stages of an automatic transmission in order to prevent an increase in friction loss, the automatic transmission can be prevented from increasing in axial and radial dimensions.

1 is a skeleton diagram of an automatic transmission according to an embodiment of the present invention. It is a table | surface which shows the relationship between the combination of a fastening of a friction fastening element, and a gear stage. 1 is a skeleton diagram of an automatic transmission as a comparative example.

  Hereinafter, the best mode for carrying out the present invention will be described.

  FIG. 1 is a skeleton diagram showing the configuration of an automatic transmission according to an embodiment of the present invention. The automatic transmission 1 is mounted on a front engine front drive vehicle.

  The automatic transmission 1 includes an input shaft 2 whose one end is connected to a power source P (for example, an engine), an output unit (output gear) 3 disposed on a concentric shaft with the input shaft 2, an input A transmission mechanism 4 for shifting between the shaft 2 and the output unit 3, a counter drive mechanism 6, and a differential mechanism 7 are provided. The components of the automatic transmission 1 are accommodated in a transmission case 5. Yes.

  The counter drive mechanism 6 includes a first counter gear 6b and a second counter gear 6c fixed on the counter drive shaft 6a, and the first counter gear 6b meshes with the output unit 3. The differential mechanism 7 has a diff ring gear 7a that meshes with the second counter gear 6c, and an axle 7b for driving the left and right wheels.

  The driving force output from the output unit 3 is transmitted to a wheel (not shown) via the counter mechanism 6 and the differential mechanism 7.

  Next, the transmission mechanism 4 will be described in detail. The transmission mechanism 4 is composed of a plurality of parts disposed on the concentric shaft of the input shaft 2, and includes a first planetary gear set 10, a second planetary gear set 20, a third planetary gear set 30 as planetary gear type planetary gear sets. A fourth planetary gear set 40, and further includes a first clutch 50, a second clutch 60, a third clutch 70, a first brake 80, and a second brake 90 as friction engagement elements.

  The first planetary gear set 10, the first clutch 50, the second clutch 60, the output unit 3, the third and fourth planetary gear sets 30 and 40, and the second brake 90 are sequentially arranged from the power source P toward the counter power source side. A third clutch 70, a second planetary gear set 20, and a first brake 80 are provided.

  A first planetary gear set 10 constituted by a single pinion type planetary gear set includes a first sun gear 11, a first carrier 12, and a first ring gear 13, and the first carrier 12 includes the input shaft 2 and the first ring gear. 13 is always in communication with the output unit 3 without using a clutch or the like.

  The second planetary gear set 20 constituted by a double pinion type planetary gear set has a second sun gear 21, a second carrier 22, and a second ring gear 23, and the second sun gear 21 together with the first carrier 121 has an input shaft 2. And always contacted without going through the clutch.

  The third planetary gear set 30 constituted by a single pinion type planetary gear set includes a third sun gear 31, a third carrier 32, and a third ring gear 33. The third carrier 32 is connected to the second ring gear 23, a clutch, and the like. It is always informed without going through.

  The fourth planetary gear set 40 configured by a double pinion type planetary gear set includes a fourth sun gear 41, a fourth carrier 42, and a fourth ring gear 43. The fourth ring gear 43 together with the first ring gear 13 is the output unit 3. And always contacted without going through the clutch.

  Further, as shown in FIG. 1, the output connection for connecting the input connecting portion 2 a and the output portion 3 to the first ring gear 13 and the fourth ring gear 43 for connecting the input shaft 2 and the first carrier 12. Each has a portion 3a.

  The first clutch 50 is between the first sun gear 11 and the third sun gear 31, the second clutch 60 is between the third sun gear 31, the third ring gear 33 and the fourth sun gear 41, and the third clutch 70 is the second carrier. 22 is a clutch for connecting and disconnecting between the second sun gear 31 and the third sun gear 31.

  The first brake 80 is a brake that connects and disconnects between the second carrier 22 and the transmission case 5, and the second brake 90 is a brake that connects and disconnects between the fourth carrier 42 and the transmission case.

  Each friction engagement element (clutch / brake) according to the present embodiment is a hydraulic control type, and engagement and release are controlled by a hydraulic control mechanism (not shown).

  Next, the engaged state of each frictional engagement element (clutch / brake) at each shift stage will be described with reference to FIG.

  The reverse speed is a reverse gear used when the vehicle is moved backward, and the first clutch 50, the first brake 80, and the second brake 90 are engaged.

  The first speed is a forward shift stage used mainly when the vehicle starts, and the second clutch 60, the first brake 80, and the second brake 90 are engaged. Further, the gear ratio of the first speed is set to the largest value (4.800 in the present embodiment) in the forward shift speed.

  The second speed is a forward shift stage used mainly when the vehicle travels at a low vehicle speed, and the third clutch 70, the first brake 80, and the second brake 90 are engaged. Further, the gear ratio of the second speed is set to a value (3.5573 in the present embodiment) next to the first speed in the forward shift speed.

  The third speed is a forward shift stage used mainly when the vehicle travels at low to medium vehicle speeds, and the second clutch 60, the third clutch 70, and the second brake 90 are engaged. Further, the gear ratio of the third speed is set to a value next to the second speed (2.400 in the present embodiment).

  The fourth speed is a forward shift stage used mainly when the vehicle travels at a medium vehicle speed, and the first clutch 50, the third clutch 70, and the second brake 90 are engaged. Further, the gear ratio of the fourth speed is set to a value (1.790 in the present embodiment) next to the third speed.

  The fifth speed is a forward shift stage used mainly when the vehicle travels at a medium vehicle speed, and the first clutch 50, the second clutch 60, and the second brake 90 are engaged. Further, the gear ratio of the fifth speed is set to a value (1.412 in the present embodiment) next to the fourth speed.

  The sixth speed is a forward shift stage used mainly when the vehicle travels at medium to high vehicle speeds, and the first clutch 50, the second clutch 60, and the third clutch 70 are engaged. Further, the gear ratio of the sixth speed is set to a value that is the second largest after the fifth speed (1,000 in the present embodiment) (the input speed to the speed change mechanism 4 and the output speed are the same speed). ).

  The seventh speed is a forward shift stage used mainly when the vehicle travels at a high vehicle speed, and the first clutch 50, the second clutch 60, and the first brake 80 are engaged. In addition, the gear ratio of the seventh speed is set to the next largest value after the sixth speed (0.828 in the present embodiment), and the speed of the overdrive (the output speed is lower than the input speed to the transmission mechanism 4). It is a step.

  The eighth speed is a forward shift stage mainly used when the vehicle travels at a high vehicle speed, and the first clutch 50, the third clutch 70, and the first brake 80 are engaged. Further, the overdrive (the output rotational speed is lower than the input rotational speed to the speed change mechanism 4) set to the lowest value (0.706 in the present embodiment) of the forward shift speed is the gear ratio of the eighth speed. Is the gear position. The eighth speed is the fastest forward shift speed in this embodiment.

  The automatic transmission 1 according to this embodiment includes two single pinion type planetary gear sets, two double pinion type planetary gear sets, three clutches, and two brakes, and the maximum forward shift speed is 8th. However, the automatic transmission according to the present embodiment is the first speed higher than that of Patent Document 1, while the direct-coupled gear position of Patent Document 1 is the fifth speed. The difference is that a direct gear is set for the speed. The reason will be described next.

  In the automatic transmission of Patent Document 1, since the direct-coupled shift stage in which the input rotational speed (turbine rotational speed) and the output rotational speed to the automatic transmission are set to the same speed is set to the fifth speed, The shift speed is overdrive (the output speed is higher than the input speed of the automatic transmission). Generally, the gear ratio difference (gear step) between the respective gears is set within a predetermined range from the viewpoint of preventing rapid fluctuations in driving force. The gear ratio of the first gear (especially the highest gear) is set to a relatively high speed side.

  As a result, when the automatic transmission of Patent Document 1 is applied to an engine having a relatively small displacement with respect to the vehicle case, a driving scene in which the vehicle driving force is insufficient at an overdrive gear stage (particularly the highest gear stage) Occurs. On the other hand, by changing the final gear ratio of the differential mechanism to the low speed side, it is possible to prevent the vehicle driving force from being insufficient. As a result, the differential mechanism (differing gear) becomes larger, and as a result There is a problem that the automatic transmission becomes larger.

  Therefore, it is conceivable to change the direct coupling stage to a higher speed side by further adding a frictional engagement element. However, if the frictional engagement element is added as described above, the frictional engagement element released at each shift stage is considered. As the number increases, the problem of increased friction loss remains.

  In response to this problem, the automatic transmission 1 according to the present embodiment is configured such that the direct drive speed is set to the sixth speed, which is one speed higher than that of Patent Document 1, so that the vehicle driving force is insufficient particularly at the highest speed. While preventing the occurrence of a scene, the differential mechanism 7 is increased in size and an increase in friction loss due to the addition of a frictional engagement element is prevented.

  Next, returning to FIG. 1, the peripheral structure of the multi-stage planetary gear set 100 will be described.

In the present embodiment, the third and fourth planetary gear sets 30 and 40 are arranged on the inner and outer circumferences on the reaction power source side of the output unit 3, thereby configuring the multistage planetary gear set 100.

  Here, the third planetary gear set 30 is disposed on the inner peripheral side of the multi-stage planetary gear set 100, and the fourth planetary gear set 40 is disposed on the outer peripheral side between the third ring gear 33 and the fourth sun gear. This is because there is no rotation.

  That is, when the first planetary gear set 10 and the second planetary gear set are stacked on the inner and outer circumferences to form a multi-stage planetary gear set, the ring gear of the planetary gear set disposed on the inner circumferential side and the planetary gear disposed on the outer circumferential side. Since differential rotation occurs between the sun gear of the set, both planetary gear sets need to be separated in the radial direction, and as a result, the radial dimension of the multistage planetary gear set increases.

  From the above, in the present embodiment, the multi-stage planetary gear set 100 is constituted by the third and fourth planetary gear sets 30 and 40.

  An output unit 3 and a first planetary gear set 10 are disposed on one axial side (power source P side) of the multistage planetary gear set 100. Therefore, the output connecting portion 3a that connects the output portion 3 and the fourth ring gear 43 of the fourth planetary gear set 40 located on the outer peripheral side of the multi-stage planetary gear set 100 and the ring gear 13 of the first planetary gear set 10 is provided with the multi-stage planetary gear set. 100 is disposed on one axial side (power source P side).

  Accordingly, there is no output communication portion 3 a between the input shaft 2 and the third sun gear 31 on the inner peripheral portion of the multistage planetary gear set 100, so that the multistage planetary gear set 100 can be brought closer to the input shaft 2. . As a result, the diameter of the multistage planetary gear set 100 is reduced, and an increase in the radial dimension of the automatic transmission 1 is prevented.

  On the other side in the axial direction of the multistage planetary gear set 100 (reaction power source side), the second carrier 42 and the transmission case 5 of the fourth planetary gear set 40 located on the outer peripheral side of the multistage planetary gear set 100 are connected and disconnected. A brake 90 is provided.

  Next, FIG. 3 as a comparative example will be described. In addition, the code | symbol of each site | part of FIG. 3 is matched with the code | symbol of each site | part of FIG. 1 in order to show the corresponding relationship with each site | part of FIG.

  In the comparative example of FIG. 3, the output unit 203 is disposed on one side (power source P side) in the axial direction of the multistage planetary gear set 200, and the first planetary gear set 210 is disposed on the other side (reverse power source side). That is, the output unit 30 and the first planetary gear set 210 are separately arranged on one side (power source P side) and the other side (reverse power source side) of the multistage planetary gear set 200.

  Therefore, since the output unit 30 and the first planetary gear set 210 are separately provided on one side (power source P side) and the other side (reverse power source side) of the multi-stage planetary gear set 200, the output An output connecting portion 203 a that connects the portion 203 and the fourth ring gear 243 of the fourth planetary gear set 240 and the first ring gear 213 of the first planetary gear set 210 located on the outer peripheral side of the multi-stage planetary gear set 200 includes the input shaft 202 and a plurality of The stage planetary gear set 200 needs to be disposed between the inner peripheral portion of the step planetary gear set 200 and the third sun gear in the radial direction.

  Here, the output communication portion 203a is disposed between the input shaft 202 and the third sun gear in the inner peripheral portion of the multistage planetary gear set 200 in the radial direction. This is because it can be made lighter than passing through the outer peripheral side of the fourth ring gear 243 on the outer peripheral side.

  However, in the comparative example shown in FIG. 3, since the output communication portion 203 a exists between the input shaft 202 and the third sun gear at the inner peripheral portion of the multi-stage planetary gear set 200, the multi-stage planetary gear set 200 is present. Cannot be brought close to the input shaft 202 well. As a result, the diameter of the multi-stage planetary gear set 200 increases, and the radial dimension of the automatic transmission 1 may increase.

  In contrast to the comparative example shown in FIG. 3, in the present embodiment shown in FIG. 1, the output unit 3 and the other planetary gear set (first planetary gear set) are provided on one axial side (power source side) of the multi-stage planetary gear set 100. 100). That is, the output unit 3 and the other planetary gear set (first planetary gear set 100) are arranged on one side (power source side) in the axial direction of the multistage planetary gear set 100.

  Thereby, since there is no output communication part 3a between the radial directions of the input shaft 2, the multistage planetary gear set 100, and the sun gear 31, the multistage planetary gear set 100 can be brought closer to the input shaft 2. . Therefore, the diameter of the multistage planetary gear set 100 is reduced, and an increase in the radial dimension of the automatic transmission 1 is prevented.

  The automatic transmission 1 according to the present embodiment includes a first sun gear 11, a first carrier 12, and a first ring gear 13, and a first planetary gear set 10 configured of a single pinion type, a second sun gear 21, A second planetary gear set 20 including a second carrier 22 and a second ring gear 23, and a double pinion type, a third sun gear 31, a third carrier 32, and a third ring gear 33, and a single pinion type. A third planetary gear set 30 constituted by a fourth sun gear 41, a fourth carrier 42 and a fourth ring gear 43, and a fourth planetary gear set 44 constituted by a double pinion type, and first and second brakes. 80, 90, first, second and third clutches 60, 70, 80, A first case 12 and a second sun gear 21 that are always in communication with the input shaft 2, a first ring gear 13 and a fourth ring gear 43 that are always in communication with the output unit 3, a first sun gear 11 and a third sun gear. A first clutch 50 that connects and disconnects 31, a second clutch 60 that connects and disconnects the third sun gear 31 and the third ring gear 33, a third clutch 70 that connects and disconnects the second carrier 22 and the third sun gear 31, A first brake 80 for connecting / disconnecting the carrier 22 and the transmission case 5, a second brake 90 for connecting / disconnecting the fourth carrier 42 and the transmission case 5, a third carrier 32 and a second ring gear 23 that are always connected, The third ring gear 33 and the fourth sun gear 41 that are always in contact are provided, and the multi-stage planetary gear set 100 is disposed on the inner peripheral side thereof. A serial third planetary gear set 30, a fourth planetary gear set 40 disposed on the outer peripheral side thereof, provided with a further, other planetary gear sets are those wherein the first planetary gear set 10.

  Accordingly, the output communication unit 3a that communicates the fourth ring gear 43 of the fourth planetary gear set 40, the first ring gear 13 of the first planetary gear set 10 and the output unit 3 disposed on the outer peripheral side of the multi-stage planetary gear set 100. The multi-stage planetary gear set 100 is disposed on one side in the axial direction.

  Thereby, compared with the case where the output connection part 3a needs to be arrange | positioned between the radial directions of the multi-stage planetary gear set 100 (the third sun gear 31 of the third planetary gear set 30) and the input shaft, the output connection part 3a As much as possible, the diameter of the multi-stage planetary gear set 100 stacked on the inner and outer circumferences can be reduced, and an increase in the radial dimension of the automatic transmission 1 can be prevented.

  In the present embodiment, the automatic transmission 1 is mounted on the vehicle such that its axial direction is the vehicle width direction of the vehicle. Since the planetary gear set is arranged in the automatic transmission so as to overlap the inner and outer peripheries (multi-stage planetary gear set 100), the overall length (axial dimension) of the automatic transmission 1 can be shortened. Thereby, it is possible to prevent the mounting property on the vehicle from deteriorating when the automatic transmission 1 is mounted on the vehicle such that the axial direction of the automatic transmission 1 is the vehicle width direction of the vehicle.

  In the present embodiment, the automatic transmission 1 is described as being mounted on a front engine front drive vehicle. However, the axial direction of the automatic transmission 1 is the vehicle width direction in the engine room provided at the rear of the vehicle. The automatic transmission 1 may be mounted on the vehicle so that the axial direction of the automatic transmission 1 is the vehicle front-rear direction.

  In the present embodiment, the automatic transmission having the maximum forward shift speed of 8 speed has been described as an example. However, the maximum forward shift speed is set to a shift speed lower than the 8th speed or a shift speed higher than the 8th speed. You may apply to the automatic transmission 1. FIG.

  In the present embodiment, the engine is described as the power source P. However, a motor may be used, and both the engine and the motor may be used as the power source.

  In the present embodiment, the example in which the output unit 3 and the other planetary gear set (first planetary gear set 10) are disposed on the power source side of the multiple-stage planetary gear set 100 has been described. The output unit 3 and other planetary gear sets (first planetary gear set 10) may be disposed on the power source side.

  INDUSTRIAL APPLICABILITY The present invention is useful for preventing an automatic transmission from increasing in axial and radial dimensions when a planetary gear set is added to increase the number of stages of the automatic transmission in order to prevent an increase in friction loss. is there.

1, 201 Automatic transmission 2, 202 Input shaft 3, 203 Output unit 3a, 203a Output communication unit 4, 204 Transmission mechanism 5, 205 Transmission case 6, 206 Secondary mechanism 7, 207 Differential mechanism 10, 210 First planetary gear set ( Other planetary gear sets)
11, 211 First sun gear 12, 212 First carrier 13, 213 First ring gear 20, 220 Second planetary gear set 21, 221 Second sun gear 22, 222 Second carrier 23, 223 Third ring gear 30, 230 Third planetary gear set 31, 231 Third gear 32, 232 Third carrier 33, 233 Third ring gear 40, 240 Fourth planetary gear set 41, 241 Fourth sun gear 42, 242 Fourth carrier 43, 243 Fourth ring gear 50, 250 First clutch 60 260 Second clutch 70, 270 Third clutch 80, 280 First brake 90, 290 Second brake 100, 200 Multi-stage planetary gear set
P Power source

Claims (2)

An input shaft;
A speed change mechanism having three planetary gear sets disposed on a concentric shaft of the input shaft;
An output section;
An automatic transmission with
The transmission mechanism is
Among the three planetary gears, a multi-stage planetary gear set configured by overlapping two planetary gear sets on the inner and outer circumferences;
Other planetary gear sets that are the remaining planetary gear sets of the three planetary gear sets;
An output communication unit that communicates the output unit, the multi-stage planetary gear set and the other planetary gear set;
The output section and the other planetary gear set are arranged on one side in the axial direction from the multi-stage planetary gear ,
The automatic transmission is
A first planetary gear set including a first sun gear, a first carrier, and a first ring gear, and configured by a single pinion type;
A second planetary gear set including a second sun gear, a second carrier, and a second ring gear, and a double pinion type;
A third planetary gear set including a third sun gear, a third carrier, and a third ring gear, and a single pinion type;
A fourth planetary gear set comprising a fourth sun gear, a fourth carrier, and a fourth ring gear, and of a double pinion type;
First and second brakes;
First, second and third clutches;
Mission case and
The first carrier and the second sun gear always in communication with the input shaft;
The first ring gear and the fourth ring gear always in communication with the output unit;
The first clutch connecting and disconnecting the first sun gear and the third sun gear;
A second clutch that connects and disconnects the third sun gear and the third ring gear;
A third clutch that connects and disconnects the second carrier and the third sun gear;
A first brake that connects and disconnects the second carrier and the transmission case;
A second brake for connecting and disconnecting the fourth carrier and the transmission case;
The third carrier and the second ring gear, which are always in contact,
The third ring gear and the fourth sun gear, which are always in contact,
The multi-stage planetary gear set is composed of the third planetary gear set disposed on the inner peripheral side thereof and the fourth planetary gear set disposed on the outer peripheral side thereof,
The other planetary gear set is composed of the first planetary gear set.
An automatic transmission characterized by that. The automatic transmission is mounted on the vehicle such that its axial direction is the vehicle width direction of the vehicle.
The automatic transmission according to claim 1 .