JPH06147279A - Power transmission device for automatic transmission - Google Patents

Abstract

PURPOSE:To facilitate molding of a part to be detected for detecting the number of revolutions and to improve mounting ability of a sensor arranged in correspondence to a part to be detected. CONSTITUTION:A power transmission device for an automatic transmission is formed such that a first gear shifting mechanism A arranged on an input shaft 11 and operated such that a power transmission route is switched through operation to select a plurality of frictional fastening elements and a second gear shifting mechanism B arranged on an output shaft 12 arranged in parallel to the input shaft 11 and operated such that a power transmission route is switched through operation to select a plurality of frictional fastening elements are intercoupled through a counter gear 5, arranged on the output shaft 12, such that a power is transmittable. A counter gear 5 is spline-coupled with the input element 43 of a planetary gear mechanism 40 of which the second gear shifting mechanism B consists, and a spline part formed to the input element 43 of the planetary gear mechanism 40 is extended in the direction of the width of a tooth and a part to be detected for detecting the number of revolutions is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device for an automatic transmission.

[0002]

2. Description of the Related Art In an automatic transmission, as means for increasing the number of gears and ensuring a smoother gear shifting characteristic, for example, a first gear shift mechanism of three-speed gear shift and a second gear shift mechanism of two-speed gear shift are used as counter gears. It is known to obtain a five-speed or six-speed transmission by connecting via a gear (for example, Japanese Patent Laid-Open No. 4-1
25343).

[0003]

By the way, in an automatic transmission having such a gear structure, the power transmission paths of both the first gear mechanism and the second gear mechanism may be simultaneously switched depending on the gear position. In such a case, from the viewpoint of mitigating shift shock, it is also necessary to appropriately control the shift timing of both. In this case, at least the rotational speeds of the output shaft of the torque converter, the output shaft of the first speed change mechanism or the input shaft of the second speed change mechanism, and the output shaft of the second speed change mechanism are detected as factors for determining the speed change timing. It is necessary.

On the other hand, the rotation speed of the output shaft or the like is detected by detecting the rotational position of a gear-shaped detected portion formed on the output shaft or the like with a sensor. It has been a general method in the past to mount a dedicated member formed as a single unit on the output shaft or the like.

However, in the method of forming the detected portion by using the dedicated member as described above, the cost is increased due to an increase in the number of parts or the assembly man-hour, or the shaft of the automatic transmission is installed by the installation of the dedicated member. There are problems such as an increase in directional length, and the development of means for solving these problems is being demanded.

Therefore, the present invention provides a power transmission device for an automatic transmission having a first speed change mechanism and a second speed change mechanism,
The detected part for rotation speed detection can be easily molded without increasing the number of parts, the number of assembly steps, and the axial length of the automatic transmission, and also supports the detected part. The purpose of this is to improve the mountability of the sensors arranged in the same manner.

[0007]

In the present invention, as a concrete means for solving such a problem, in the invention of claim 1, power transmission is performed by selective operation of a plurality of friction engagement elements provided on the input shaft. The first transmission mechanism whose path is switched, and the second transmission mechanism which is provided on the output shaft arranged in parallel with the input shaft and whose power transmission path is switched by the selective operation of the plurality of friction engagement elements are output. In a power transmission device of an automatic transmission that is power-transmittable via a counter gear provided on a shaft, an input of a counter gear provided on the output shaft and a planetary gear mechanism constituting the second transmission mechanism. The element is spline-coupled, and the spline portion formed on the input element of the planetary gear mechanism is extended in the tooth width direction to form a detected portion for detecting the rotational speed. And butterflies.

According to a second aspect of the present invention, in the power transmission device of the automatic transmission according to the first aspect, the operation of the second speed change mechanism is provided on one axial side of the planetary gear mechanism that constitutes the second speed change mechanism. The friction engagement element for switching is arranged with the output gear on the other side, while the ring gear of the planetary gear mechanism is used as the input element, and the detected portion is formed on the outer peripheral portion of the ring gear. It is characterized by

[0009]

With each of the inventions of the present application, the following effects can be obtained by adopting such a configuration.

According to the first aspect of the invention, the spline portion formed in the input element of the planetary gear mechanism on the side of the second speed change mechanism, which is spline-coupled to the counter gear, extends in the tooth width direction and is detected. Since this is a part, the detected part can be easily molded in the same step as the molding of the spline part.

According to the second aspect of the present invention, the frictional engagement element is arranged on one side in the axial direction of the planetary gear mechanism constituting the second speed change mechanism, the output gear is arranged on the other side, and the ring gear of the planetary gear mechanism is arranged. As the input element that is spline-coupled to the counter gear, and the spline portion formed on the outer peripheral portion of the ring gear is extended and used as the detected portion, the outer side in the radial direction of the detected portion is space-wise. The dead space has a sufficient margin, and the sensor can be arranged by using this dead space.

[0012]

Therefore, according to the power transmission device of the automatic transmission of each invention of the present application, the following effects can be obtained.

According to the power transmission device of the automatic transmission of the first aspect, the detected portion is formed integrally with the input element of the planetary gear mechanism by extending the spline portion of the input element. Therefore, for example, compared to the case where the detected portion is formed of a dedicated member as in the conventional case, the number of parts is reduced, the number of assembly steps is reduced, and the cost can be reduced, and the axial direction of the automatic transmission can be made compact. That is the effect that can be obtained.

According to the power transmission device of the automatic transmission of the second aspect, in addition to the effects described above, the sensor is arranged by using the dead space on the outer peripheral side of the planetary gear mechanism of the second transmission mechanism. Therefore, the space efficiency of the automatic transmission can be improved, which can contribute to the downsizing of the automatic transmission.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A power transmission device for an automatic transmission according to the present invention will be specifically described below with reference to the embodiments shown in the accompanying drawings.

First, the overall structure of the automatic transmission 1 and its shift characteristics will be briefly described with reference to FIG. 1. The automatic transmission 1 of this embodiment has a transmission case 2 in which a first planetary gear, which will be described later, is provided. A first speed change mechanism A including a gear mechanism 20 and a second planetary gear mechanism 30 and a second speed change mechanism B including a third planetary gear mechanism 40.
And the first transmission mechanism A and the second transmission mechanism A are arranged in parallel.
The transmission mechanism B is connected via a counter gear 5 which will be described later, and the power transmission path of each of the planetary gear mechanisms 20, 30, 40 is switched by the selective operation of a plurality of friction engagement elements such as clutches and brakes described later. Go forward 5
It is designed to form a shift stage of one shift stage and one reverse stage.

In the first speed change mechanism A, the first planetary gear mechanism 20 and the second planetary gear mechanism 30 as speed change gear elements are provided on the input shaft 11 to which the output of the torque converter 10 is transmitted.
, First clutch 51, first brake 52, second brake 53, second clutch 54, third brake 55, and first
One-way clutch 61 and second one-way clutch 62
Are arranged respectively.

The torque converter 10 is a pump 1 fixed in a case 13 connected to the engine output shaft 3.
4 and the pump 14 disposed to face the pump 14.
A turbine 15 driven by hydraulic oil by means of a hydraulic fluid, and a stator 17 interposed between the pump 14 and the turbine 15 and connected to the transmission case 2 side via a one-way clutch 16 to increase the torque. , Case 1 above
3 and the turbine 15, and is constituted by a lock-up clutch 18 that directly connects the engine output shaft 3 and the turbine 15 via the case 13, and the rotation of the turbine 15 is transmitted via the input shaft 11. Is output to the planetary gear mechanisms 20 and 30 arranged on the input shaft 11. Reference numeral 19 is an oil pump that is connected to the case 13 and is driven as the case 13 rotates.

The first planetary gear mechanism 20 includes a sun gear 21 loosely fitted on the input shaft 11 and the sun gear 21.
A plurality of pinion gears 22, 22, ...
And a ring gear 23 that meshes with each pinion gear 22,
A carrier 24 that rotatably supports the pinion gears 22 is provided. The second planetary gear mechanism 30 has a sun gear 31 loosely fitted on the input shaft 11.
, A plurality of pinion gears 32, 32, ... That mesh with the sun gear 31, a ring gear 33 that meshes with each pinion gear 32, and a carrier 34 that rotatably supports each of the pinion gears 32. And
The ring gear 23 of the first planetary gear mechanism 20 and the sun gear 31 of the second planetary gear mechanism 30 are integrally connected, and the carriers 24 and 34 are respectively connected to the first output gear 4.

On the other hand, a first clutch 51 is arranged in series between the sun gear 21 and the input shaft 11, and a first brake 52 is provided between the first clutch 51 and the transmission case 2. There is. Further, the first one-way clutch 6 is provided between the first clutch 51 and the transmission case 2.
The second brake 53 is provided through the first brake 53. Further, the second clutch 54 is arranged in series between the sun gear 31 and the input shaft 11, and the third brake 55 and the second one-way clutch 62 are respectively provided between the carrier 34 and the transmission case 2. It is provided.

The second speed change mechanism B has a third planetary gear mechanism 40 mounted on the output shaft 12 arranged in parallel with the input shaft 11.
The third clutch 56 and the third one-way clutch 63 are arranged. The third planetary gear mechanism 40 is
A sun gear 41 integrally attached to the output shaft 12,
.. which are respectively meshed with the sun gear 41, a ring gear 43 which is meshed with each pinion gear 42, and a carrier 44 which rotatably supports each pinion gear 42. The ring gear 43 is connected to the counter gear 5 which is loosely fitted on the output shaft 12 and meshes with the first output gear 4, and the carrier 44 is loosely fitted on the output shaft 12. And is connected to the second output gear 6. Further, a third clutch 56 is provided between the counter gear 5 and the output shaft 12, and the third clutch 56 is provided.
The third one-way clutch 63 and the fourth brake 57 are respectively interposed between and the transmission case 2, and the rotation of the counter gear 5 meshing with the first output gear 4 causes the rotation of the third planetary gear mechanism. It is adapted to be transmitted to the second output gear 6 via 40.

As a result, each of the planetary gear mechanisms 20, 3 described above is
A plurality of friction engagement elements 51 to 55 such as clutches and brakes and each one-way clutch 6 are connected to the power transmission paths of 0 and 40.
The output of the engine output shaft 3 is changed in speed according to the operating state and is transmitted to the second output gear 6 by switching by selecting operation of Nos. 1 and 62.

The friction engagement elements 51 to 57 such as the above-mentioned clutches and brakes, and the one-way clutches 61 to 6 are also included.
Table 1 shows the relationship between the operating state of No. 3 and the shift speed.

[0024]

[Table 1]

That is, as shown in Table 1, in the first speed, the second clutch 54, the third brake 55, and the fourth brake 57 are engaged, and the second one-way clutch 62 and the third one-way clutch 63 are connected. Are brought into the power transmission state.

In the second speed, the second clutch 54 and the third clutch
The clutch 56 and the third brake 55 are engaged, and only the second one-way clutch 62 is in the power transmission state.

In the third speed, the third clutch 56 engaged in the second speed is released, while the first brake 52 is released.
The second brake 53 and the fourth brake 57 are respectively engaged, and the first one-way clutch 61 and the third one-way clutch 63 are both in the power transmission state.

In the fourth speed, the first clutch 51 and the second clutch 51
The clutch 54, the second brake 53, and the fourth brake 57 are engaged, and only the third one-way clutch 63 is in the power transmission state.

At the fifth speed, the first clutch 51 and the second clutch 51
Clutch 54, third clutch 56, and second brake 53
Are respectively engaged, and all the one-way clutches 61 to 63 are idling.

At the reverse speed, only the first clutch 51 and the third clutch 56 are engaged, all other brakes are released, and all the one-way clutches 61 to 63 are idling.

The above is the overall structure and operating characteristics of the automatic transmission 1.

By the way, in the embodiment,
In order to control the shift timing between the first speed change mechanism A and the second speed change mechanism B to realize a speed change operation with a small speed change shock,
The rotation speed of the input shaft 11 and the third planetary gear mechanism 40.
The rotational speed of the ring gear 43 (that is, the rotational speed of the input shaft of the second speed change mechanism B) and the rotational speed of the output shaft 12 are respectively detected. Therefore, the first rotational speed is set in the second clutch 54 portion. The sensor 71 is connected to the third planetary gear mechanism 4 described above.
A second rotation speed sensor 72 is arranged in the 0 ring gear 43 portion, and a third rotation speed sensor 73 is arranged in the second output gear 6 portion. The present invention is applied to the second rotation speed sensor 72 of the rotation speed sensors 71 to 73. Hereinafter, the specific structure will be described in detail with reference to FIGS.

FIG. 2 shows the third planetary gear mechanism 40 and its peripheral portion in a state corresponding to the reference numerals in FIG. In FIG. 2, the third clutch 56 and the fourth brake 57 are arranged on one side in the axial direction of the counter gear 5 that meshes with the first output gear 4 of the first speed change mechanism A, and on the other side. The third planetary gear mechanism 40 is arranged in close proximity to each other.

As shown in FIGS. 1 to 3, the counter gear 5 has an annular projection 5a of a predetermined diameter integrally formed on the side surface on the side of the third planetary gear mechanism 40 and the annular projection 5a. A spline portion 5b is formed on the inner peripheral portion of 5a. On the other hand, the ring gear 43 of the third planetary gear mechanism 40 has a gear 43a that meshes with the pinion gear 42 on its inner peripheral portion.
And the spline portion 43 is formed on the outer periphery of the
forming b. The spline portion 5b of the counter gear 5 and the spline portion 43b of the ring gear 43 are spline-engaged with each other, whereby the counter gear 5
The power is transmitted from the side to the third planetary gear mechanism 40 side.

In this case, the counter gear 5 has a small tooth width. Therefore, as shown by the chain line in FIG. 4, the spline portion 43b of the ring gear 43 originally has a correspondingly small tooth width. In this embodiment, the present invention is applied to apply the spline portion 4 of the ring gear 43.
As shown by the solid line in FIG. 4, 3b is extended further in the tooth width direction beyond the required tooth width, and this extended portion serves as a detected portion 45 corresponding to the second rotation speed sensor 72. The second rotation speed sensor 72 is arranged on the radially outer side so as to correspond to the detected portion 45.

When the spline portion 43b formed on the ring gear 43 is extended in the tooth width direction to form the detected portion 45, for example, the third portion indicated by reference numeral 46 in FIG.
Like the detected member 46 for the rotation speed sensor 73, the annular plate body is bent and the gear-shaped detected portion 46a is provided on the outer peripheral portion thereof.
As compared with the conventional structure for forming the
In addition to b, the detected part 45 can be formed in the same process, the number of processing steps can be reduced, and the dedicated assembly step is not required, so that the cost can be reduced, and the space for disposing the detected part 45 can be reduced. Since it is not necessary to secure the axial direction, the axial length of the automatic transmission 1 can be reduced and the automatic transmission 1 can be made compact.

Further, although one side of the third planetary gear mechanism 40 has no space in terms of space because the third clutch 56 and the like are arranged via the counter gear 5, the other side of the third planetary gear mechanism 40 is not provided. Is a dead space with a sufficient space because only the small-diameter second output gear 6 is arranged. Since the second rotation speed sensor 72 is arranged in this dead space,
The rotation speed sensor 72 can be easily and easily arranged. For example, the mountability thereof is improved as compared with the case where a dedicated space for disposing the second rotation speed sensor 72 has to be separately secured. In addition, it can contribute to downsizing of the automatic transmission 1.

In this embodiment, in order to restrict the movement of the counter gear 5 in the axial direction, the spline portion 5b of the counter gear 5 and the ring gear 4 are prevented.
A snap ring 49 formed by forming linear gripping portions 49b and 49b at both ends of an annular portion 49a that is bent in a substantially C shape is disposed between the three connecting portions with the spline portion 43b. That is, as shown in FIGS. 3 and 4, the annular groove 48 is formed in the spline portion 5b of the counter gear 5, while the spline portion 43b of the ring gear 43 is formed.
An annular groove 47 is formed at a position corresponding to the annular groove 48, and the snap ring 49 is fitted and arranged between the annular grooves 48, 47 to restrict movement between the two.

In this case, when the snap ring 49 is mounted, the snap ring 49 is first fitted in the annular groove 47 of the ring gear 43 in the state where the counter gear 5 and the ring gear 43 are separated from each other, and the snap ring 49 is attached to the pair of snap rings. Gripping part 4
9b and 49b are gripped and reduced in diameter so that the annular portion 49a has a smaller diameter than the inner diameter of the spline portion 5b of the counter gear 5. In this state, the ring gear 43 is moved to the counter gear 5 side so that the spline portion 43b is fitted into the spline portion 5b of the counter gear 5, and when the annular grooves 47 and 48 are overlapped, the snap ring 49 is inserted. The gripping force is released, and the elastic restoring force expands the gripping force to perform a predetermined movement restriction action.

At this time, in order to avoid interference between the gripping portions 49b, 49b of the snap ring 49 and the annular projection 5a of the counter gear 5, as shown in FIGS. 3 and 5, the annular projection of the counter gear 5 is prevented. Notches 5c, 5c having a predetermined width are formed at two positions in the circumferential direction of the portion 5a, and the grips 49b, 49b of the snap ring 49 are positioned in the notches 5c.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing a power transmission system in a power transmission device for an automatic transmission according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view showing a specific structure of a third planetary gear mechanism portion shown in FIG.

FIG. 3 is an enlarged view of a portion III in FIG.

FIG. 4 is an enlarged view of an IV portion of FIG.

FIG. 5 is a reduced front view of the input gear shown in FIG.

[Explanation of symbols]

1 is an automatic transmission, 2 is a transmission case, 3 is an engine output shaft, 4 is a first output gear, 5 is a counter gear, and 6 is a second
Output gear, 7 is ring gear, 10 is torque converter,
11 is an input shaft, 12 is an output shaft, 13 is a case, 14 is a pump, 15 is a turbine, 16 is a one-way clutch, 1
7 is a stator, 18 is a lockup clutch, 19 is an oil pump, 20 is a first planetary gear mechanism, 21 is a sun gear, 22 is a pinion gear, 23 is a ring gear, 24 is a carrier, 30 is a second planetary gear mechanism, and 31 is a sun gear. Three
2 is a pinion gear, 33 is a ring gear, 34 is a carrier, 40 is a third planetary gear mechanism, 41 is a sun gear, 42 is a pinion gear 4, 43 is a ring gear, 44 is a carrier,
Reference numeral 45 is a detected portion, 46 is a detected member, 46a is a detected portion, 47 is an annular groove, 48 is an annular groove, 49 is a snap ring, 51 is a first clutch, 52 is a first brake, 53 is a second brake. , 54 is the second clutch, 55 is the third brake, 56 is the third clutch, 57 is the fourth brake, 61 is the first one-way clutch, 62 is the second one-way clutch, 63 is the third one-way clutch, and 71 is the first. A rotation speed sensor, 72 is a second rotation speed sensor, 73 is a third rotation speed sensor, A is a first speed change mechanism, and B is a second speed change mechanism.

Claims (2)

[Claims] 1. A first transmission mechanism provided on an input shaft, the power transmission path of which is switched by a selective operation of a plurality of friction engagement elements; and a plurality of output gears provided on an output shaft arranged in parallel with the input shaft. A power transmission device for an automatic transmission, the power transmission path being switched by a selective operation of the frictional engagement element, and a second transmission mechanism which is capable of power transmission via a counter gear provided on the output shaft. A spur coupling between a counter gear provided on the output shaft and an input element of a planetary gear mechanism that constitutes the second speed change mechanism, and a spline portion formed in the input element of the planetary gear mechanism in a tooth width direction. A power transmission device for an automatic transmission, characterized in that a detected portion for detecting the number of revolutions is extended to the power transmission device. 2. The friction engaging element for switching the operation of the second speed change mechanism on one axial side of the planetary gear mechanism constituting the second speed change mechanism, and the output gear on the other side of the planetary gear mechanism according to claim 1. , Respectively, while the ring gear of the planetary gear mechanism is used as the input element, and the detected portion is formed on the outer peripheral portion of the ring gear.