JPS62258261A - Planetary gear row for automatic transmission - Google Patents

Abstract

PURPOSE:To improve the performance with simple structure by coupling a turbine and a sun gear of one planetary gear through a turbine shaft while coupling a first stator and the other sun gear through a stator tubular shaft then regulating the rotations respectively by means of brakes and connecting/ disconnecting both shafts by means of a clutch. CONSTITUTION:A tubular shaft 44 of a first stator 36 is arranged concentrically with the shaft 40 of a turbine 34 for a torque converter 30 and only the reverse rotary force of the first stator 36 is transmitted through a unilateral clutch 42 to said shaft 44. A second stator 38 is coupled through a unilateral clutch 46 to a fixed tubular shaft 48. The turbine shaft 40 is coupled to a sun gear 14 of a planetary gear 10. The reverse rotary force of the first stator 36 is transmitted through the tubular shaft 44 to a sun gear 16 of a planetary gear 12. The stator tubular shaft 44 can be connected/disconnected with the turbine shaft 40 by means of a clutch C while brakes B1, B2 and B3 are arranged on a coupling shaft 29 between both shafts and the planetary gears 10, 12. When combining these brakes and clutches variously, the speed change performance at each stage can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a planetary gear train having two pairs of simple planetary gear assemblies sharing a planetary carrier and a ring gear with each other;
Concerning the improvement of an automatic transmission consisting of an m-engaging device and a three-element single-stage torque converter.

It is something that

(Prior art and its problems) A conventional automatic transmission of this type is constructed as shown in FIG.

That is, a three-element torque converter consisting of a stator, a turbine, and a pump has two pairs of mutually separated simple gear assemblies 10.12 consisting of a planetary gear, a planetary carrier, a sun gear, and a ring gear i at the rear stage of the three-element torque converter consisting of a stator, a turbine, and a pump. The two sun gears 14 and 16 are individually rotatably supported, and one T! Place the star carry r18 on the other ring gear 2.
0 and output from this planet ↑ Yariya 18.

Brake for each of these gears 81.82
, clutches C1, C2, and C3 are provided, and as shown in Table 1 below, each brake and clutch is turned ON (marked with O) to perform a speed change of four forward speeds and one penetration speed.

Table 1 However, the conventional T1! ! There is 1BlfII in which the number of clutches is large in the GiV train, and the structure and control are night fog.

(Objective of the Invention) The present invention aims to improve the tractive force performance that is limited in the first and second speed regions, and to simplify the structure and control while reducing the number of gears by one compared to the conventional II4 construction.

(Structure of the Invention) (1) Technical Means The present invention provides a replica of the 41111 torque converter consisting of two stators, a turbine, and a pump, and a planetary gear,
It has two pairs of mutually divided simple idler gear assemblies consisting of a planetary carrier, a sun gear, and a ring gear, and each of the two sun gears is independently rotatably supported, and one N-star Kipriya is connected to the other ring gear. In an automatic transmission equipped with a series of planetary gears connected to the planetary carrier and output from the planetary carrier, a turbine shaft is provided that connects the turbine with the sun gear of one of the planetary gear assemblies, and the rotation of the turbine shaft is A stator cylindrical shaft is provided to connect the first stator and the other sun gear, and a brake is provided to limit the rotation of the stator cylindrical shaft. An automatic transmission characterized by being provided with a clutch and a brake that controls the rotation of the other 111 carrier! It is an i-star gear train.

(2) In the first gear, the planetary carrier that is not connected to the output side is fixed with a brake, and the forward rotation force of the turbine and the reverse rotation force of the first gear are combined by both planetary gear assemblies, resulting in a high torque ratio. , obtain high efficiency.

In the second speed, the first stator is fixed by the brake, and the first stator is idled in a speed ratio range before the second stator idles, thereby obtaining a high torque ratio and high efficiency.

(Embodiments) (1) First embodiment Front wheel Il adopting the present invention! 3-speed front play for ribbed passenger tables,
An automatic transmission with one reverse speed will be explained with reference to FIG.

In FIG. 1, parts given the same reference numerals as in FIG. 3 indicate the same or equivalent parts.

It is a 1R1v4 medium t'30Lt4fi element 2m type torque converter, and the torque converter 30 is composed of a pump 32, a turbine 34, a first stator 36, a second stay 938, and the like.

The turbine 34 is connected to the turbine shaft 40, and the first stator 36 is connected to the stator cylinder shaft 4 via a one-way clutch 42.
It is connected to 4. The stator cylinder shaft 44 is the turbine shaft 40
It is arranged concentrically so that it can rotate freely. The one-way clutch 42 has a first stator 36 connected to the turbine 3.
The first stator 36 rotates in the same direction as the first stay 936, that is, rotates idly when in the forward rotation direction, and locks when the first stator 36 is in the reverse rotation direction, thereby transmitting the reversal force of the first stay 936 to the stator cylinder shaft 44. The second stator 38 is the one-way clutch 4
6 to the fixed sleeve 48. Fixed cylinder shaft 4
8 is provided concentrically radially outward of the stator coax 44. The fixed cylinder shaft 48 is continuous with the housing 50. Further, the turpin 34 is equipped with a lock-up clutch 52.

The rear stage of the torque converter 30 described above is combined with a TI star-type vehicle train, which will be described in detail later, to constitute an automatic transmission.

The turbine shaft 40 corresponds to the planetary gear assembly 10 in FIG.
The sun gear 14 (of the planetary gear assembly 10) extends to the right of the
61 number: za2). The sun gear 14 meshes with a planet gear 24 held by a planet carrier 18. An output gear 26 is connected to the right end of the planetary carrier 18, and a ring gear 25 (number of teeth near rl) is fixed to the left end of the planetary carrier 18 in the drawing. turbine shaft 4
0 in the radial direction, the rotation of the turbine shaft 40 is Mti
A second brake B3 is provided.

The M planet gear 28 of the planet gear assembly 12 is connected to the planet carrier 29
The planetary carrier 29 is connected to the ring gear 20 (number of teeth: Zr2) of the planetary gear assembly 10, and a brake B2 is provided radially outward of the planetary carrier 29. Sun gear 16 of planetary gear assembly 12 (number of teeth: Zal
) A clutch C1 is interposed between the stator cylinder shaft 44 and the turbine shaft 40, which are connected to the turbine shaft 40.
0, the stator cylinder shaft 44 is connected intermittently.

Further, a stator cylinder shaft 44 is disposed radially outward of the clutch C1.
A brake B1 is provided to restrict the rotation of the motor.

Next, the effect will be explained. In the planetary gear train as described above, as shown in Table 2 described later in detail, the brakes 81 to B3,
Clutch C1 is selectively turned ON to achieve 3 forward speeds and 1 reverse speed.
Shift speed.

At the first speed when only the brake B2 is ON, the reverse rotation force of the first stator 36 is transmitted from the stator cylinder shaft 44 to the sun gear 16 of the planetary gear assembly 12, and is output as a forward rotation force from the ring gear 25 integrated with the output shaft. The first stator 36
The reversing force of the first stator 36 is increased to improve efficiency and torque ratio in the region where the first stator 36 is reversed.

That is, as shown in FIG. 1a, which shows the change in the torque ratio t1 efficiency η with respect to the speed ratio e, in the range below P where the rotation direction of the first stator 36 changes to normal rotation, the efficiency changes from the conventional efficiency characteristic ηO. In the characteristic η1, the torque ratio is the torque ratio characteristic 1
The torque ratio characteristic improves from 0 to t1. Note that in the range of point 1 or higher, the first stator 36 idles due to the action of the one-way clutch 42.

Next, in the second gear where only the brake B1 is ON, the first
The first stator 3 in the speed ratio range until the stator 36 idles.
6 to increase the fishing force transmitted from the turbine 34,
Obtain high torque ratio and high efficiency.

In this second speed region, as shown in Fig. 1b, the efficiency characteristic η
0 to the efficiency characteristic η2, and the torque ratio characteristic t.

The torque ratio characteristic improves from t2 to t2.

Furthermore, in the third gear where only the clutch C1 is ON, the first
The efficiency characteristic η3 and the torque ratio characteristic t3 are shown in diagram C.

Finally, when the brake B3 is turned on during reverse movement, the turbine 34 is fixed, and only the reversing force from the first steering wheel 36 is transmitted from the sun gear 16 to the planetary gear assembly 12, causing the ring gear 20 and the output gear 26 to rotate in reverse. During this backward movement, as shown in the first dail, the efficiency characteristic ηR and the torque ratio characteristic tR are exhibited.

The gear ratios at each gear stage as described above are detailed in Table 3, which will be described later.

(2) Second Embodiment An automatic transmission with four forward speeds and one reverse speed for a front-wheel drive passenger car, which also employs the present invention, will be explained with reference to FIG.

In FIG. 2, a clutch C2 is interposed between the sun gear 14 and the turbine shaft 40, and a clutch C1 is interposed between the planetary gear 29 and the turbine shaft 40.

In the planetary gear train as described above, each brake and clutch is selectively turned on as shown in Table 2 below, and four forward
1 speed and 1 reverse speed.

Table 2 When each brake and clutch are operated as shown in Table 2 above, the gear ratios of the turbine 34 and first stator 36 are as shown in Table 3 below.

Table 3 In Table 3, the number of teeth is Zal-36, Za2-42, zrl-Z
When set to r2-75, the gear ratio of the turbine 34 at the first speed is 2.786, and the gear ratio of the first stator 36 is -2.
,083, in the second gear the turbine 34 is 1.579, in the third gear
In speed, the turbine 34 is 1, and in 4th speed, the turbine 34 is 0.
．． 676, in reverse, the first stator 36 becomes 2.726.

(Effects of the Invention) As explained above, the idle gear train of the automatic transmission according to the present invention has the following effects.

At the first speed, the reversing force of the first stator 36 is transmitted from the stator cylinder shaft 44 to the ring gear IP16 of the 121 gear assembly 12, and is output as normal rotation force from the ring gear 'P25 integrated with the output shaft, and is output through the ring gear P14 to the turbine. The turbine 34 is output from the planetary carrier 18 integral with the output shaft via the ring gear 20 of the planetary gear assembly 10 from the shaft 40.
By adding the reverse rotation force of the first stator 36 to the normal rotation force of , the efficiency and torque ratio can be improved in the region where the first stator 36 rotates in reverse rotation.

Therefore, as shown in FIG. 1a, in the range below the point P where the rotational direction of the first stator 36 changes to normal rotation, the efficiency is changed from the conventional efficiency characteristic ηO to the efficiency characteristic η1, and the torque ratio is changed from the torque ratio characteristic 10 to the torque The specific characteristics can be improved to t1.

Next, in the second gear where only the brake B1 is ON, the first
The first stator 3 in the speed ratio range until the stator 36 idles.
6 to increase the power transmitted from the turbine 34,
As shown in Figure 1b, from the efficiency characteristic ηO to the efficiency characteristic η2
In addition, the torque ratio characteristic to can be improved to the torque ratio characteristic t2, and a high torque ratio and high efficiency can be exhibited.

In this way, the torque ratio and efficiency are improved in the first and second speeds.

Moreover, since the structure is IIIM, there is only one clutch which is longer in the axial direction, making the entire automatic transmission more compact.

[Brief explanation of drawings]

Fig. 1 is a structural diagram showing an embodiment according to the present invention, Fig. 1a is a graph showing changes in torque ratio and efficiency with respect to speed ratio in 1st speed, and Fig. 1b is a graph showing the same in 2nd and 4th speeds. Graphs, Figure 1C is the same graph in 3rd gear, Figure 1D is the same graph in reverse, Figure 2 is a structural diagram showing the second embodiment adopting the present invention, and Figure 3 is the conventional example. This is a schematic diagram of the structure. 10.12... Planet gear assembly, 14.16... Sun gear, 18... Planetary carrier, 20... Ring gear V126... Output gear, 30... Torque converter patent applicant Dai Co., Ltd. Gold Manufacturing Agent Patent Attorney Tadataka Daigari: j1- I-'i::i+ Figure 3 Figure 1a Figure 1c Progress ratio a Figure 1b Figure 1d Progress ratio C

Claims (1)

[Claims] A planetary gear, a planetary carrier,
It has two pairs of mutually divided simple planet gear assemblies consisting of a sun gear and a ring gear, each of the two sun gears is rotatably supported individually, one planet carrier is connected to the other ring gear, and the planet carrier is connected to the other ring gear. In an automatic transmission in which a planetary gear train is arranged such that output is output from a carrier, a turbine shaft is provided for connecting a turbine and a sun gear of one of the planetary gear assemblies, a brake is provided for regulating the rotation of this turbine shaft, and a first A stator cylinder shaft is provided to connect the stator and the other sun gear, a brake is provided to restrict the rotation of the stator cylinder shaft, a clutch is provided between the stator cylinder shaft and the turbine shaft to connect and connect both shafts, and a clutch is provided between the stator cylinder shaft and the turbine shaft to connect and connect both shafts. A planetary gear train for an automatic transmission characterized by being equipped with a brake that regulates rotation.