JP6107725B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission mounted on a vehicle, and belongs to the technical field of a vehicle transmission.

  An automatic transmission mounted on a vehicle such as an automobile generally includes a transmission mechanism having a plurality of planetary gear sets (planetary gear mechanisms) and a plurality of friction engagement elements such as clutches and brakes, and selectively selects these friction engagement elements. Are connected to each other to switch the power transmission path through each planetary gear set to achieve a predetermined gear position according to the driving state of the vehicle.

  As such an automatic transmission, in the case of a horizontal automatic transmission whose shaft center extends in the vehicle body width direction, the output rotation of the transmission mechanism arranged on the axis of the input shaft is arranged on the axis of the input shaft. There is known one in which transmission is performed from a counter drive gear provided to a differential device via a counter drive mechanism.

  This counter drive mechanism includes a large-diameter counter driven gear that meshes with the counter drive gear and a small-diameter final drive gear that meshes with the differential ring's diff ring gear on a counter shaft disposed in parallel with the input shaft. The output rotation of the mechanism is decelerated and transmitted to the differential device.

  For example, Patent Document 1 discloses such an automatic transmission. FIG. 4 shows a schematic arrangement of the components thereof. In this automatic transmission 100, the transmission case 105 is disposed on the axis of an input shaft 102 connected to a drive source E composed of an engine and a torque converter, for example. A speed change mechanism 110 and a counter drive gear 120 are provided, a counter driven gear 130 and a final drive gear 140 are provided on a counter shaft 103 parallel to the input shaft 102, and the output rotation of the speed change mechanism 110 is controlled by the counter drive gear. 120, the counter driven gear 130 and the final drive gear 140 are transmitted to the differential ring differential gear 150.

  Although the speed change mechanism 110 may be disposed only on the counter drive source side of the counter drive gear 120, it is disposed across the drive source side and the counter drive source side of the counter drive gear 120 as indicated by reference numerals 110A and 110B. Sometimes it is done. The planetary gear set and the frictional engagement element constituting the transmission mechanism 110 may be arranged in a radial direction so as to suppress the axial dimension of the entire transmission.

  Further, in this automatic transmission 100, a parking gear 160 is integrally coupled to the counter driven gear 130 on the axis of the counter shaft 103 and adjacent to the counter driven source side of the counter driven gear 130. The drive source side is supported on the transmission case 105 by countershaft bearings 170 and 180, respectively.

JP 2009-2423 A

  In recent years, multistage automatic transmissions have been promoted for the purpose of improving the fuel efficiency of vehicles, etc., and along with this, the number of planetary gear sets constituting the transmission mechanism tends to increase, but the number of planetary gear sets is increasing. If it increases, the axial direction dimension of the whole transmission will increase and the problem of in-vehicle property will occur.

  On the other hand, by increasing the radial dimension of the planetary gear set and the frictional engagement element constituting the speed change mechanism, the axial dimension is secured while ensuring the strength required for the planetary gearset and the torque capacity required for the frictional engagement element. It can be shortened, and an increase in the axial dimension of the entire transmission can be suppressed.

However, when the radial dimension of the planetary gear set or the frictional engagement element is increased, a region where the predetermined member such as a parking gear or a counter shaft bearing disposed on the counter shaft occupies the transmission mechanism in an axial direction overlaps. If it is provided, there is a risk of interference with the predetermined member. In particular, when a planetary gear set or a frictional engagement element has a speed change mechanism that is arranged so as to overlap in the radial direction, such a tendency may become more prominent.

As shown in FIG. 4, when an area occupied in the bearing 170 the axial direction for transmission mechanism 110 and the parking gear 160 and the counter shaft is provided at a position overlapping, planetary gear sets and frictional engagement constituting the speed change mechanism 110 If the radial dimension of the element is increased, there is a risk of interference with the parking gear 160 and the counter shaft bearing 170.

  In this way, even when the radial dimension of the planetary gear set and frictional engagement element constituting the speed change mechanism is increased, the countershaft is moved in the longitudinal direction of the vehicle body relative to the input shaft to increase the distance between the two shafts. Thus, it is possible to prevent the transmission mechanism from interfering with the parking gear and the counter shaft bearing. However, in such a case, the vehicle body longitudinal dimension of the entire transmission increases, and the in-vehicle performance deteriorates.

  Accordingly, the present invention addresses the above-mentioned problems associated with the multi-stage automatic transmission, and increases the axial dimension and the longitudinal dimension of the vehicle body in a horizontal automatic transmission whose axial center extends in the vehicle body width direction. It is an object of the present invention to provide an automatic transmission capable of preventing interference between a transmission mechanism and a predetermined member on a counter shaft while suppressing the above-described problem.

  In order to solve the above-described problems, an automatic transmission according to the present invention is configured as follows.

First, according to the first aspect of the present invention, a transmission mechanism having a plurality of planetary gear sets and a counter drive gear are arranged on an axis of an input shaft connected to a drive source in a transmission case. A horizontal automatic transmission in which a counter driven gear that meshes with the counter drive gear is disposed on a counter shaft that is disposed in parallel with an input shaft, and is adjacent to the counter driven gear on an axis of the counter shaft. The planetary gear set of the plurality of planetary gear sets is arranged independently on the axis of the input shaft at a position where an area occupied in the axial direction overlaps the predetermined member. The predetermined member is a parking gear .

The invention according to claim 2, in the automatic transmission according to claim 1, wherein the counter shaft is supported by the transmission case through a bearing two counter shaft disposed on both sides The counter driven gear is provided such that an outer peripheral portion on which teeth meshing with the counter drive gear are formed is offset to one side in the axial direction with respect to an inner peripheral portion attached to the counter shaft, and one of the counter shaft bearings is provided. Is arranged at a position where an area occupied in the axial direction overlaps the outer peripheral portion on the inner peripheral side of the outer peripheral portion of the counter driven gear.

According to a third aspect of the present invention, in the transmission case, a transmission mechanism having a plurality of planetary gear sets and a counter drive gear are arranged on an axis of an input shaft connected to a drive source, and the input shaft A horizontal automatic transmission in which a counter driven gear that meshes with the counter drive gear is disposed on a counter shaft disposed in parallel with the counter drive gear, and is disposed adjacent to the counter driven gear on the axis of the counter shaft. Provided with a predetermined member, and one planetary gear set of the plurality of planetary gear sets is independently disposed on the axis of the input shaft at a position where an area occupied in the axial direction overlaps the predetermined member, The predetermined member is a counter shaft bearing that supports the counter shaft on the transmission case.

With the above configuration, first, according to the invention described in claim 1 of the present application, a transmission mechanism having a plurality of planetary gear sets on the axis of the input shaft and a counter drive gear are arranged in the transmission case, In an automatic transmission in which a counter driven gear is disposed on a counter shaft, a predetermined member is provided adjacent to the counter driven gear on an axis of the counter shaft, and one planetary gear set of a plurality of planetary gear sets is the predetermined member. Are arranged on the axis of the input shaft independently at a position where the areas occupied in the axial direction overlap.

  As a result, the portion where the planetary gear set on the axis of the input shaft is arranged alone has a smaller space in the radial direction compared to the case where the planetary gear set and the frictional engagement element are arranged in the radial direction. Even if a predetermined member on the axis of the counter shaft is disposed at this axial position, there is no interference.

For example, when planetary gear sets are added due to multistage automatic transmissions, the radial dimensions of the planetary gear sets and frictional engagement elements that constitute the speed change mechanism are increased in order to suppress an increase in the axial dimension. In the case where this interferes with a predetermined member such as a parking gear or a counter shaft bearing on the axis of the counter shaft, the predetermined member is disposed at a portion where an area occupied in the axial direction overlaps the planetary gear set. Accordingly, it is possible to increase the radial dimension of the planetary gear set and the frictional engagement element constituting the transmission mechanism while avoiding interference with the planetary gear set on the axis of the input shaft. Therefore, it is possible to prevent the interference between the speed change mechanism and the predetermined member on the counter shaft while suppressing the increase in the axial dimension and the longitudinal dimension of the vehicle body. For example, addition of a planetary gear set for multistage automatic transmission, etc. Is possible.

The front Symbol predetermined member, by a parking gear, interfere with the parking gear when the enlarged radial dimension of the planetary gear sets and frictional engagement elements constituting the shift mechanism to suppress an increase in the axial dimension In this case, the parking gear can be arranged at a portion where the area occupied in the axial direction overlaps with the planetary gear set to avoid interference with the planetary gear set on the axis of the input shaft. Can be played.

According to the second aspect of the present invention, the counter driven gear is provided such that the outer peripheral portion on which the teeth engaging with the counter drive gear are formed is offset to one side in the axial direction with respect to the inner peripheral portion attached to the counter shaft. The counter shaft bearing is disposed at a position where an area occupied in the axial direction overlaps with the outer peripheral portion on the inner peripheral side of the outer peripheral portion of the counter driven gear.

As a result, when the radial dimension of the planetary gear set or the frictional engagement element constituting the speed change mechanism is increased in order to suppress an increase in the axial dimension, the countershaft bearing may be interfered with. The bearing can be arranged on the inner peripheral side of the outer peripheral portion of the counter driven gear at a position where the outer peripheral portion occupies the area in the axial direction and the interference with the planetary gear set on the axis of the input shaft can be avoided. Can be played effectively.

According to the third aspect of the invention, as in the first aspect of the invention, the transmission case having the plurality of planetary gear sets on the axis of the input shaft and the counter drive gear are disposed in the transmission case. In the automatic transmission in which the counter driven gear is disposed on the counter shaft, a predetermined member is provided adjacent to the counter driven gear on the axis of the counter shaft, and one planetary gear set of the plurality of planetary gear sets includes: It is independently arranged on the axis of the input shaft at a position where the region occupying the predetermined member and the axial direction overlaps.
As a result, the portion where the planetary gear set on the axis of the input shaft is arranged alone has a smaller space in the radial direction compared to the case where the planetary gear set and the frictional engagement element are arranged in the radial direction. Even if a predetermined member on the axis of the counter shaft is disposed at this axial position, there is no interference.
For example, when planetary gear sets are added due to multistage automatic transmissions, the radial dimensions of the planetary gear sets and frictional engagement elements that constitute the speed change mechanism are increased in order to suppress an increase in the axial dimension. In the case where this interferes with a predetermined member such as a parking gear or a counter shaft bearing on the axis of the counter shaft, the predetermined member is disposed at a portion where an area occupied in the axial direction overlaps the planetary gear set. Accordingly, it is possible to increase the radial dimension of the planetary gear set and the frictional engagement element constituting the transmission mechanism while avoiding interference with the planetary gear set on the axis of the input shaft. Therefore, it is possible to prevent the interference between the speed change mechanism and the predetermined member on the counter shaft while suppressing the increase in the axial dimension and the longitudinal dimension of the vehicle body. For example, addition of a planetary gear set for multistage automatic transmission, etc. Is possible.
In addition, the predetermined member is a bearing for the counter shaft that supports the counter shaft on the transmission case, so that the radial dimension of the planetary gear set and the frictional engagement element constituting the transmission mechanism in order to suppress the increase in the axial dimension. If the counter shaft bearing interferes with the expansion of the planetary gear set, the counter shaft bearing is arranged in a portion where the region occupied in the axial direction overlaps the planetary gear set, and the planetary gear set on the axis of the input shaft Interference can be avoided, and the above effect can be effectively achieved.

It is a figure which shows roughly arrangement | positioning of the component of the automatic transmission which concerns on embodiment of this invention. It is sectional drawing which shows the structure of the principal part of the automatic transmission which concerns on embodiment of this invention. It is a figure which shows roughly arrangement | positioning of the component of the automatic transmission which concerns on another embodiment of this invention. It is a figure which shows roughly arrangement | positioning of the component of the conventional automatic transmission.

  Hereinafter, embodiments of the present invention will be described.

  FIG. 1 is a diagram schematically showing the arrangement of components of an automatic transmission according to an embodiment of the present invention. An automatic transmission 1 shown in FIG. 1 is a horizontal automatic transmission whose axis extends in the vehicle body width direction, and is connected to a drive source E including, for example, an engine and a torque converter in a transmission case 5. A transmission mechanism 10 having a plurality of planetary gear sets and a plurality of frictional engagement elements such as clutches and brakes and a counter drive gear 20 that is an output member of the transmission mechanism 10 are disposed on the axis of the input shaft 2. Yes.

  Each of the plurality of planetary gear sets constituting the speed change mechanism 10 is a single pinion type in which a pinion supported by a carrier directly meshes with a sun gear and a ring gear, and has a sun gear, a ring gear, and a carrier as rotating elements. . The planetary gear set may be a double pinion type planetary gear set.

  The automatic transmission 1 switches the power transmission path through the plurality of planetary gear sets by combining the engagement states of the plurality of friction engagement elements to change the gear ratio of the transmission mechanism 10 to obtain a predetermined gear stage. It is configured. For example, the automatic transmission 1 includes four planetary gear sets and five frictional engagement elements. By selectively engaging three of these frictional engagement elements, eight forward speeds and reverse speeds are formed. It is configured to be.

  Further, in the transmission case 5, a counter driven gear 30 that meshes with the counter drive gear 20 and a final drive gear 40 that meshes with the differential ring differential gear 50 on the counter shaft 3 disposed parallel to the input shaft 2. The final drive gear 40 has a smaller diameter than the counter driven gear 30 and rotates integrally with the counter driven gear 30. As a result, the output rotation of the speed change mechanism 10 is transmitted from the counter drive gear 20 to the diff ring gear 50 of the differential device via the counter driven gear 30 and the final drive gear 40.

  In the present embodiment, one planetary gear set PG1 among the plurality of planetary gear sets constituting the speed change mechanism 10 is disposed independently on the axis of the input shaft 2 adjacent to the drive source side of the counter drive gear 20. . The planetary gear set PG1 is arranged alone means that other planetary gear sets and frictional engagement elements constituting the speed change mechanism 10 excluding the planetary gear set PG1 are not arranged to overlap the planetary gear set PG1 in the radial direction. The other planetary gear set and the frictional engagement element are arranged at positions offset in the axial direction from the planetary gear set PG1.

  The transmission case 5 is located between the front vertical wall 5b provided at the end of the outer peripheral wall 5a on the drive source side and the rear vertical wall 5c provided at the end of the outer peripheral wall 5a on the counter drive source side. The intermediate wall 5d extends inwardly from the outer peripheral wall 5a, and the counter drive gear 20 and one planetary gear set PG1 are sequentially arranged on the drive source side of the intermediate wall 5d.

  In the speed change mechanism 10 shown in FIG. 1, other planetary gear sets and frictional engagement elements other than the planetary gear set PG1 are arranged on the counter drive source side of the counter drive gear 20, but the other planetary gear sets and frictional engagement elements are It may be arranged on the counter drive source side of the counter drive gear 20 and the drive source side of the planetary gear set PG1.

  In addition, one planetary gear set PG1 is arranged independently on the axis of the input shaft 2, but other planetary gear sets and frictional engagement elements except for one planetary gear set PG1 suppress the axial dimension of the entire transmission. In order to do so, they can be arranged in the radial direction.

  As described above, the counter driven gear 30 and the final drive gear 40 are disposed on the counter 3 shaft, and the counter drive mechanism 4 is configured by the counter shaft 3, the counter driven gear 30 and the final drive gear 40.

  The counter driven gear 30 includes an outer peripheral portion 30a formed with teeth that mesh with the counter drive gear 20, an inner peripheral portion 30b attached to the counter shaft 3, and a connecting portion 30c that connects the outer peripheral portion 30a and the inner peripheral portion 30b. And the outer peripheral portion 30a is offset from the inner peripheral portion 30b on the side opposite to the driving source, which is one side in the axial direction. The connecting portion 30c extends while being inclined toward the drive source side from the outer peripheral portion 30a toward the inner peripheral portion 30b.

  The final drive gear 40 is disposed on the drive source side of the counter driven gear 30, teeth that mesh with the diff ring gear 50 are formed on the outer peripheral side, and the inner peripheral side is attached to the counter shaft 3. The final drive gear 40 is integrally formed on the counter shaft 3 or is spline-fitted and attached to the counter shaft 3 so as to rotate integrally.

  The counter shaft 3 is, specifically, a counter shaft bearing 70 disposed on the counter drive source side of the counter shaft 3 via two counter shaft bearings 70 and 80 disposed on both sides of the counter shaft 3. And the countershaft bearing 80 disposed on the drive source side of the countershaft 3 is supported by the transmission case 5.

The counter shaft bearing 70 is disposed on the counter drive source side of the counter driven gear 30, and is disposed on the inner peripheral side of the outer peripheral portion 30 a of the counter driven gear 30 at a position where an area occupied in the axial direction overlaps with the outer peripheral portion 30 a. . The counter shaft bearing 80 is disposed on the drive source side of the final drive gear 40.

On the axis of the counter shaft 3, a parking gear 60 is disposed adjacent to the counter driven gear 30 on the drive source side. The parking gear 60 is for preventing rotation of the counter driven gear 30 in the parking range, and is integrally coupled to the inner peripheral portion 30b of the counter driven gear 30 by press fitting or welding on the drive source side of the outer peripheral portion 30a of the counter driven gear 30. Has been. The parking gear 60 is disposed at a position where the area occupied in the axial direction overlaps the planetary gear set PG1.

Thus, in the automatic transmission 1, one planetary gear set PG 1 of the speed change mechanism 10 is disposed independently on the axis of the input shaft 2 adjacent to the counter drive gear 20, and adjacent to the counter driven gear 30 on the counter shaft 3. Thus, the parking gear 60 is arranged, and the planetary gear set PG1 and the parking gear 60 are provided at positions where the areas occupied in the axial direction overlap.

In the automatic transmission 1, as shown in FIG. 1, the automatic transmission 1 is arranged on the counter shaft 3 at a position where an area occupied in the axial direction overlaps with the transmission mechanism 10 disposed on the counter drive source side of the transmission case 5. Predetermined members such as the provided parking gear 60 and counter shaft bearing 70 are not provided.

Here, the specific structure of the principal part of the automatic transmission 1 according to the embodiment of the present invention will be described.
FIG. 2 is a cross-sectional view showing the structure of the main part of the automatic transmission according to the embodiment of the present invention. As shown in FIG. 2, in the automatic transmission 1, the counter drive gear 20 is disposed on the axis 2 a of the input shaft 2, and the counter drive gear 20 is driven from the inner peripheral end of the intermediate wall 5 d of the transmission case 5. A counter drive gear bearing 25 is supported by a boss-like cylindrical portion 5e extending to the source side.

  On the axis 2 a of the input shaft 2, one planetary gear set PG <b> 1 that constitutes the speed change mechanism 10 is disposed independently adjacent to the drive source side of the counter drive gear 20. The planetary gear set PG1 includes a sun gear S1, a carrier C1, and a ring gear R1, and a pinion P1b supported by the carrier C1 via a pinion shaft P1a is directly meshed with the sun gear S1 and the ring gear R1.

  The sun gear S1 is connected to the power transmission member X1 by spline fitting on the drive source side of the power transmission member X1 extending in the axial direction on the outer peripheral side of the input shaft 2 on the sun gear S1. The non-driving source side of the power transmission member X1 is connected to another planetary gear set and frictional engagement element of the speed change mechanism 10 disposed on the counter driving source side from the intermediate wall 5d of the transmission case 5.

  The carrier C1 is connected to the power transmission member X2 by being spline-fitted to the drive source side of the power transmission member X2 extending in the axial direction on the outer peripheral side of the power transmission member X1. The non-drive source side of the power transmission member X2 is connected to other planetary gear sets and frictional engagement elements of the speed change mechanism 10 arranged on the counter drive source side from the intermediate wall 5d of the transmission case 5.

  The ring gear R1 is spline-fitted with the drive source side of the counter drive gear 20 on the counter drive source side and connected to the counter drive gear 20 so as to rotate integrally with the counter drive gear 30.

  On the other hand, a counter driven gear 30 and a final drive gear 40 are disposed on the axis 3 c of the counter shaft 3, and a parking gear 60 is coupled to the counter driven gear 30.

  The counter driven gear 30 includes an outer peripheral portion 30a formed with teeth that mesh with the counter drive gear 20, an inner peripheral portion 30b that is spline-fitted to the counter shaft 3, and a connecting portion that connects the outer peripheral portion 30a and the inner peripheral portion 30b. 30c, and the outer peripheral portion 30a is offset from the inner peripheral portion 30b on the side opposite to the driving source, and the connecting portion 30c is inclined toward the driving source side from the outer peripheral portion 30a toward the inner peripheral portion 30b. It extends.

  The final drive gear 40 is disposed on the drive source side of the counter driven gear 30, teeth that mesh with the diff ring gear 50 are formed on the outer peripheral side, and the final drive gear 40 is attached to the counter shaft 3 so that the inner peripheral side rotates integrally with the counter shaft 3. ing. In the present embodiment, the final drive gear 40 is integrally formed with the counter shaft 3. As a result, the output rotation of the speed change mechanism 10 is transmitted from the counter drive gear 20 to the diff ring gear 50 via the counter driven gear 30 and the final drive gear 40.

  The counter shaft 3 is supported via a counter shaft bearing 80 on a boss portion 5f projecting from the front vertical wall 5b of the transmission case 5 to the counter drive source side on the drive source side, and the counter drive source side of the transmission case 5 is A counter shaft bearing 70 is supported by a boss portion 5g protruding from the rear vertical wall 5c to the drive source side.

The countershaft bearing 70 is disposed on the counter drive source side of the counter driven gear 30 and is disposed on the inner peripheral side of the outer peripheral portion 30a of the counter driven gear 30 at a position where an area occupied in the axial direction overlaps with the outer peripheral portion 30a. Yes.

The parking gear 60 is disposed adjacent to the drive source side of the counter driven gear 30 and is coupled to the inner peripheral portion 30 b of the counter driven gear 30. In the present embodiment, the parking gear 60 is disposed at a position where the area occupied in the axial direction overlaps the planetary gear set PG1.

Thus, in the automatic transmission 1 according to the present embodiment, the transmission mechanism 5 having the plurality of planetary gear sets on the axis 2a of the input shaft 2 and the counter drive gear 20 are disposed in the transmission case 5. A counter driven gear 30 is disposed on the counter shaft 3, a parking gear 60 is provided adjacent to the counter driven gear 30 on the axis 3c of the counter shaft 3, and one planetary gear set PG1 of the plurality of planetary gear sets is a parking lot. It is independently arranged on the axis 2 a of the input shaft 2 at a position where the region that occupies the gear 60 in the axial direction overlaps.

  As a result, the space where the planetary gear set PG1 on the axis 2a of the input shaft 2 is disposed alone is a space that occupies in the radial direction compared to the case where the planetary gear set PG1 is disposed so as to overlap with other planetary gear sets and frictional engagement elements in the radial direction. Therefore, even if the parking gear 60 on the axis 3a of the counter shaft 3 is arranged at this axial position, there is no interference.

For example, when planetary gear sets are added due to multistage automatic transmissions, the radial dimensions of the planetary gear sets and frictional engagement elements that constitute the speed change mechanism are increased in order to suppress an increase in the axial dimension. When this will interfere with the parking gear on the axis of the countershaft, the parking gear is arranged at a location where the area occupied in the axial direction overlaps with the planetary gear set, so that the planetary gear on the axis of the input shaft It is possible to expand the radial dimension of the planetary gear set and the frictional engagement element constituting the transmission mechanism while avoiding interference with the set. Accordingly, it is possible to prevent interference between the transmission mechanism and the parking gear on the counter shaft while suppressing an increase in the axial dimension and the longitudinal dimension of the vehicle body. For example, addition of a planetary gear set for multistage automatic transmission, etc. Is possible.

Further, the counter driven gear 30 is provided with the outer peripheral portion 30 a offset from the inner peripheral portion 30 a on one side in the axial direction, and the counter shaft bearing 70 is provided on the inner peripheral side of the outer peripheral portion 30 a of the counter driven gear 30. 30a and the area which occupies an axial direction are arrange | positioned in the position which overlaps.

As a result, when the radial dimension of the planetary gear set or frictional engagement element constituting the speed change mechanism is increased in order to suppress an increase in the axial dimension, this interferes with the countershaft bearing on the countershaft axis. In this case, the counter shaft bearing is arranged on the inner peripheral side of the outer peripheral portion of the counter driven gear at a position where the outer peripheral portion and the area occupied in the axial direction overlap with each other to prevent interference with the planetary gear set on the axis of the input shaft. It can be avoided.

Next, another embodiment of the present invention will be described with reference to FIG.
FIG. 3 is a diagram schematically showing the arrangement of components of an automatic transmission according to another embodiment of the present invention. An automatic transmission 1 ′ according to another embodiment is different from the automatic transmission 1 in that the counter drive gear, the planetary gear set arranged alone, the counter driven gear, and the parking gear are different, and the same reference numerals denote the same components. The description is omitted.

  As shown in FIG. 3, in the automatic transmission 1 ′, a transmission mechanism 10 having a plurality of planetary gear sets and a plurality of frictional engagement elements on the axis of the input shaft 2 and a counter drive gear 20 ′ in the transmission case 5. And one planetary gear set PG1 ′ of the plurality of planetary gear sets constituting the speed change mechanism 10 is singly adjacent to the counter drive source side of the counter drive gear 20 ′ on the axis of the input shaft 2. Has been placed.

  Other planetary gear sets and frictional engagement elements other than the planetary gear set PG1 ′ constituting the speed change mechanism 10 are provided at positions offset in the axial direction from the planetary gear set PG1 ′, and overlap with the planetary gear set PG1 ′ in the radial direction. Not placed.

On the other hand, a counter driven gear 30 ′ and a final drive gear 40 are disposed on the counter shaft 3. The counter driven gear 30 ′ has an outer peripheral portion 30 a ′ formed with teeth that mesh with the counter drive gear 20 ′. The inner circumferential portion 30b 'that is spline-fitted with the inner circumferential portion 30b' is provided so as to overlap the area occupied in the axial direction.

  The final drive gear 40 is arranged on the drive source side of the counter driven gear 30 ′, teeth that mesh with the diff ring gear 50 are formed on the outer peripheral side, and the inner peripheral side is integrally formed with the counter shaft 3 or is spline-fitted. It is attached to the shaft 3 so as to rotate integrally.

  On the axis of the counter shaft 3, a parking gear 60 'is disposed adjacent to the counter driven gear 30'. The parking gear 60 'is integrated with the counter driven gear 30' on the drive source side of the counter driven gear 30 '. Are combined.

Also in the automatic transmission 1 ′, the counter shaft 3 is supported by the transmission case 5 via two counter shaft bearings 70 and 80 disposed on both sides of the counter shaft 3. 70 is disposed adjacent to the counter-driven source side of the counter driven gear 30 ′, and is disposed at a position where the area occupied in the axial direction overlaps the planetary gear set PG1 ′.

As described above, in the automatic transmission 1 ′, one planetary gear set PG 1 ′ of the speed change mechanism 10 is disposed independently on the axis of the input shaft 2 adjacent to the counter drive gear 20 ′, and the counter driven gear is mounted on the counter shaft 3. A counter shaft bearing 70 is disposed adjacent to 30 ', and is provided at a position where the regions occupied by the planetary gear set PG1' and the counter shaft bearing 70 in the axial direction overlap.

Also in the automatic transmission 1 ′, as shown in FIG. 3, the area occupied in the axial direction overlaps the transmission mechanism 10 disposed on the side opposite to the drive source of the transmission case 5 on the counter shaft 3. Predetermined members such as the parking gear 60 ′ and the counter shaft bearing 70 are not provided.

As described above, also in the automatic transmission 1 ′ according to the present embodiment, the transmission mechanism 5 having the plurality of planetary gear sets on the axis 2a of the input shaft 2 and the counter drive gear 20 ′ are arranged in the transmission case 5. A counter driven gear 30 ′ is disposed on the counter shaft 3, a counter shaft bearing 70 is provided on the axis of the counter shaft 3 adjacent to the counter driven gear 30 ′, and one of a plurality of planetary gear sets is provided. The planetary gear set PG1 ′ is independently arranged on the axis of the input shaft 2 at a position where an area occupied in the axial direction overlaps with the counter shaft bearing 70.

  As a result, the portion where the planetary gear set PG1 ′ on the axis 2a of the input shaft 2 is disposed alone occupies the radial direction as compared to the case where the planetary gear set PG1 ′ is disposed so as to overlap with other planetary gear sets and frictional engagement elements in the radial direction. Since the space is small, there is no interference even if the counter shaft bearing 70 on the axis of the counter shaft 3 is disposed at this axial position.

For example, when planetary gear sets are added due to multistage automatic transmissions, the radial dimensions of the planetary gear sets and frictional engagement elements that constitute the speed change mechanism are increased in order to suppress an increase in the axial dimension. When this will interfere with the countershaft bearing on the axis of the countershaft, the countershaft bearing is arranged at a portion where the area occupied in the axial direction overlaps with the planetary gear set. It is possible to expand the radial dimension of the planetary gear set and the frictional engagement element constituting the transmission mechanism while avoiding interference with the planetary gear set on the axis. Therefore, it is possible to prevent interference between the transmission mechanism and the countershaft bearing on the countershaft while suppressing an increase in the axial dimension and the longitudinal dimension of the vehicle body. For example, a planetary gear set for multistage automatic transmissions can be prevented. Addition is possible.

In the above-described embodiment, one planetary gear set of the speed change mechanism is arranged independently on the axis of the input shaft adjacent to the counter drive gear, and the parking gear or counter shaft is adjacent to the counter driven gear on the counter shaft. A bearing is disposed, and the planetary gear set and the parking gear or the countershaft bearing are provided in a position where an area occupied in the axial direction overlaps, but the speed change mechanism is configured to suppress an increase in axial dimension. When the radial dimension of the planetary gear set or the frictional engagement element is expanded, if this interferes with another predetermined member on the axis of the counter shaft, the region that occupies the predetermined member in the axial direction with the planetary gear set is You may make it provide in the position which overlaps.

  As described above, according to the present invention, an automatic transmission capable of preventing interference between a transmission mechanism and a predetermined member on a counter shaft while suppressing an increase in axial dimension and vehicle body longitudinal dimension is realized. Therefore, this type of automatic transmission or the vehicle in which it is mounted may be suitably used in the manufacturing industry.

1, 1 ', 100 Automatic transmission 2, 102 Input shaft 3, 103 Counter shaft 5, 105 Transmission case 10, 110, 110A, 110B Transmission mechanism 20, 20', 120 Counter drive gear 30, 30 ', 130 Counter Driven gears 30a, 30a 'Counter-driven gear outer peripheral parts 30b, 30b' Counter-driven gear inner peripheral parts 40, 140 Final drive gears 60, 60 ', 160 Parking gears 70, 80, 170, 180 Countershaft bearing E Drive source PG1, PG1 'planetary gear set

Claims (3)

In the transmission case, a transmission mechanism having a plurality of planetary gear sets and a counter drive gear are arranged on the axis of the input shaft connected to the drive source, and on the counter shaft arranged in parallel to the input shaft. A horizontal automatic transmission provided with a counter driven gear that meshes with the counter drive gear,
A predetermined member disposed adjacent to the counter driven gear on an axis of the counter shaft;
One planetary gear set of the plurality of planetary gear sets is disposed independently on the axis of the input shaft at a position where an area occupied in the axial direction overlaps the predetermined member ,
The predetermined member is a parking gear.
An automatic transmission characterized by that. The counter shaft is supported by the transmission case via two counter shaft bearings disposed on both sides,
The counter driven gear is provided with an outer peripheral portion formed with teeth meshing with the counter drive gear being offset to one side in the axial direction with respect to an inner peripheral portion attached to the counter shaft,
One of the counter shaft bearings is disposed at a position where an area occupied in the axial direction overlaps the outer peripheral portion on the inner peripheral side of the outer peripheral portion of the counter driven gear.
The automatic transmission according to claim 1 . In the transmission case, a transmission mechanism having a plurality of planetary gear sets and a counter drive gear are arranged on the axis of the input shaft connected to the drive source, and on the counter shaft arranged in parallel to the input shaft. A horizontal automatic transmission provided with a counter driven gear that meshes with the counter drive gear,
A predetermined member disposed adjacent to the counter driven gear on an axis of the counter shaft;
One planetary gear set of the plurality of planetary gear sets is disposed independently on the axis of the input shaft at a position where an area occupied in the axial direction overlaps the predetermined member,
The predetermined member is a countershaft bearing that supports the countershaft on the transmission case.
Automatic transmission you wherein a.

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