JPS62258246A - Planetary gear train for automatic transmission - Google Patents

Abstract

PURPOSE:To simplify the structure and the control, by providing respective brakes on a turbine shaft for connecting a turbine with a sun gear of a compound planetary gear train and on a stator sleeve shaft for connecting a first stator with a sun gear of a single planetary gear train, and thereby generating an output from a ring gear of the single planetary gear train. CONSTITUTION:At the first gear speed, a reversing force of a first stator 36 is transmitted from a stator sleeve shaft 44 to a sun gear 16, and the reversing force of the stator 36 is added to a forward force of a turbine 34 to be transmitted from a turbine shaft 40 through a planetary gear 10 to a sun gear 18 and a planetary gear 12, thereby improving the efficiency and the torque ratio in a reversing region of the stator 36. Then, at the second gear speed where a brake B1 only is operated to go on, the stator 36 is locked in a speed ratio region until the stator 36 becomes idling, thereby increasing a power to be transmitted from the turbine 34. Further, as the stator 36 becomes idling in the speed ratio region before a second stator 38 become idling, the loss due to a fluid in a stator section is reduced to thereby improve the efficiency in this speed ratio region. Accordingly, the effect caused by an increase in the number of gear speeds may be obtained by simply increasing one guide vane of a torque converter and connecting same to the sun gear.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to an improvement in a so-called Rapigneaux planetary gear train having a single row TI star gear and a double row planet gear that share one planet carrier. .

(Prior Art and its Problems) A conventional general Rapigneaux planetary gear train of this type is constructed as shown in FIG.

That is, 10 is a relatively good planetary gear in the axial direction,
The sun gear 16 and the ring gear 20 mesh to form a single-row planetary gear. Moreover, the M star gear 10 is a planetary carrier 14.
The planetary gear 12 is held in the planetary carrier 14.
are held in mesh with the planet gear 10, and the planet gear 12 meshes with the sun gear 18 to form a double-row planet gear.

Furthermore, a ring gear 20 meshing with the outer periphery of the planetary gear 10 is connected to an output gear 22.

Brakes Bl, B2 that υItll each of these gears
・Clutches C1, C2, and C3 are provided, and each brake and clutch has an ON operation (O
mark) to change gears to 4 forward speeds and 1 reverse speed.

Note that in the case of the third forward speed, the clutch C3 is deleted.

Table 1 Incidentally, in recent years, in order to improve tractive force performance, the number of gears has been increased from three forward speeds to four forward speeds and then five forward speeds.

However, in the conventional planetary gear train, the number of clutches increases as the number of gears increases, and the structure and Illm become complicated.

(Objective of the Invention) The present invention improves the tractive force performance in 1st gear, which is the number of starting gears, and the tractive force performance obtained in the 2nd and 4th gear regions, thereby reducing the number of gears by one compared to the conventional one, and improving the structure and control. It's meant to be simple.

(Structure of the Invention) (1) Technical Means The present invention provides a four-element torque converter consisting of two stays, a turbine, and a pump. In an automatic transmission equipped with a Rapigneaux planetary gear train having a planetary gear V, a turbine shaft is provided that connects the turbine and the sun gear of the double-row planetary gear, and a stator sleeve is provided that connects the first stator and the sun gear of the single-row planetary gear. Provided, the rotation of this stator cylinder shaft,
This planetary gear train of an automatic transmission is characterized in that a brake is provided to restrict rotation of a planetary carrier, and power is output from a ring gear of a single row planetary gear.

(2) At the first speed, the reversing force of the first stator is input to the single-row planetary gear to add weight to the turbine output.

In the second and fourth speeds, the first stator is fixed, and in the speed ratio range before the second stator idles, the first stator is idled to obtain high efficiency.

During reverse movement, the turbine is fixed and the reversing force of the first stator is output.

(Embodiments) (1) First Embodiment An automatic transmission with three forward speeds and one reverse speed for a front-wheel drive passenger car employing the present invention will be explained with reference to FIG.

In FIG. 1, parts given the same reference numerals as those in FIG. 5 indicate the same or equivalent parts.

In FIG. 1, 30 is a four-element two-stage torque converter, and the torque converter 30 includes a pump 32, a turbine 34,
It is composed of a first stator 36 and a second stator 38'8.

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.
When the first stator 36 rotates in the same direction as the first stator 4, that is, rotates normally, it rotates idly, and when the first stator 36 reverses, it locks and transmits the reversing force of the first stator 36 to the stator cylinder shaft 44. The second stator 38 is the one-way clutch 4
It is connected to the fixed cylinder @48 via 6. Fixed cylinder shaft 4
8 is provided concentrically outside the stator cylinder shaft 44 in the radial direction. The fixed cylinder shaft 48 is continuous with the housing 50. Furthermore, the turbine 34 is equipped with a lock-up clutch 52.

A so-called Rapigneaux-type planetary gear train, which will be described in detail later, is combined with the rear stage of the torque converter 30 to constitute an automatic transmission.

The turbine shaft 40 is connected to a sun gear 18 (number of teeth: Za2), and a planetary carrier 14 is provided at the rear end of the turbine shaft 40 via a clutch C1. A brake B2 is provided radially outward of the planetary brake rear 14. A brake B3 is provided at the rearmost end of the turbine shaft 40.

In addition, the stator cylinder shaft 44 has a sun gear 16 (number of teeth = 7a1).
A brake B1 is connected to the middle part of the stator cylinder shaft 44.
is provided. A ring gear 20 (number 61: zrl) meshing with the outer periphery of the planetary gear 10 is connected to an output gear 22 so that power is output from the output gear 22.

Next, the operation of the automatic transmission shown in FIG. 1 will be explained.

Yusei T! In the i4 vehicle convoy, brakes 81 to B3 and clutch C
1 is selectively turned ON (fixed), 3 forward speeds and 1 reverse speed.
Shift speed.

At the first speed when only the brake B2 is ON, the reversing force of the first stator 36 is transmitted from the stator cylindrical shaft 44 to the sun gear 16, and from the turbine shaft 40 to the sun gear t718 and the planet gear 12 through the planetary gear 10.
The reverse rotation force of the first stator 36 is added to the normal rotation force of the first stator 36 to improve efficiency and torque ratio in the region where the first stator 36 rotates in reverse rotation.

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 t
o to torque ratio characteristic 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, only brake B1 is ON! ! In the second speed, which makes one work,
The first stator 36 is locked in a speed ratio range until the first stator 36 idles, and the power transmitted from the turbine 34 is increased. Furthermore, since the first stator 36 is idled in a speed ratio range before the second stator 38 idles, loss due to fluid in the stator portion is reduced, and efficiency can be improved in that speed ratio range.

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.

It is possible to improve the torque ratio characteristic 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.

When the brake B3 is finally turned ON and the turbine 34 is moving in reverse, the turbine 34 is fixed and only the reversing force from the first stator 36 is transmitted from the sun gear 16 to the planetary gear 10.
20, the output key y22 is reversed. When going backwards, the 1d
As shown in the figure, the efficiency characteristic ηR and the torque ratio characteristic tR are exhibited.

(2) Second embodiment In FIG. 2 showing the second embodiment, brake B3 (FIG. 1)
is deleted, and a crab clutch C2 is provided on the planetary carrier 14. Each of these brakes and clutches is turned ON as shown in Table 2 to be described later, to perform gear changes between 3!3 front speed and 3!1 rear speed.

(3) Third Embodiment In FIG. 3 showing a third embodiment with four forward speeds and one reverse speed, a clutch C1 is interposed between the sun gear 18 and the turbine shaft 40. Each of these brakes and clutches is turned on as shown in Table 2, which will be described later, to perform a speed change of four forward speeds and one reverse speed.

The characteristics of the torque ratio characteristic t and the efficiency characteristic η at the fourth speed are similar to those shown in FIG. 1b.

(4) Fourth Embodiment In FIG. 4 showing the fourth embodiment, the brake B3 is removed and the clutch C1 is placed between the sun gear 18 and the turbine shaft 40.
A clutch C3 is interposed in the planetary carrier 14. Each of these brakes and clutches is turned ON as shown in Table 2 below to perform a speed change of four forward speeds and one reverse speed.

Table 2 When each brake and clutch are operated as shown in Table 2, the gear ratios of the turbine 34 and first stator 36 are as shown in Table 3 below. At this time, the number of teeth of sun gear 16.18 and ring gear 20 is Zal-34, Za2=29, Z
When r1 is set to 74-(1), the gear ratio of the turbine 34 in the first speed is 2,552, the gear ratio of the first stator 36 is -2°176, and in the second gear the turbine 34 is 1.552.
489, in 3rd speed the turbine 34 is 1, in 4th speed the turbine 34 is 0.685, in reverse the first stator 36 is 3
．． 047 respectively.

Table 3 (Effects of the Invention) As explained above, the idle II vehicle train of the automatic transmission according to the present invention has the following effects.

At the first speed, the reverse rotation force of the first stator 36 is transmitted from the stator cylindrical shaft 44 to the sun gear V16, and the normal rotation force of the turbine 34 is transmitted from the turbine shaft 40 to the sun gear 18 and the planet gear 12 through the planetary gear 10. The reversal force of the stator 36 can be increased to improve efficiency and torque ratio in the region where the first stator 36 is reversed.

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 η0 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.

In addition, in the speed ratio region before the second stator 38 idles, the first
Since the stator 36 is idled, loss due to fluid in the stator portion is reduced, and efficiency can be improved in that speed ratio range.

As shown in Figure 1b, from the efficiency characteristic η0 to the efficiency characteristic η2
In addition, the torque ratio characteristic t can be improved to the torque ratio characteristic t2, and a high torque ratio and high efficiency can be exhibited. In addition, in the embodiments shown in FIGS. 3 and 4, the fourth
The effect shown in FIG. 1b can be obtained quickly.

In this way, the torque ratio and efficiency are improved in 1st, 2nd, and 4th speeds, so in the present invention, the conventional 4 forward speeds are changed to 3 forward speeds.
The same tractive force performance can be achieved with the same number of speeds as 5 forward speeds and 4 forward speeds. Therefore, simply by adding one guide vane of the torque converter to the conventional automatic transmission and connecting it to the sun gear, the result is the same as increasing the number of gears by one stage, simplifying the structure and control.

Moreover, in the case of FIG. 1, there is only one clutch which has a complicated structure and a long axial dimension, making the entire automatic transmission compact.

[Brief explanation of drawings]

FIG. 1 is a structural diagram showing a first embodiment of the present invention;
Figure a is a graph showing changes in torque ratio and efficiency with respect to speed ratio in first gear, Figure 1b is the same graph in second and fourth gear, Figure 1C is the same graph in third gear, and Figure 1C is the same graph in third gear. Figure 1d is the same graph in reverse, Figure 2 is a structural diagram showing the second embodiment of the present invention, Figure 3 is a structural diagram showing the third embodiment, and Figure 4 is the same diagram showing the fourth embodiment. 1 is a schematic structural diagram, and FIG. 5 is a schematic structural diagram showing a conventional example. 10...Single-row planetary gear V112...Double-row planetary gear V114...Player spacer, 16.18...Sun gear, 20...Ring gear,
22...Output gear, 30...Torque converter patent applicant Daikin Seisakusho Co., Ltd. Agent Patent attorney Tadataka Oshiki "・ Figure 5 Figure 1a Figure 1c Figure 7f ratio C Figure 1b Figure 1d Progress Ratio C

Claims (1)

[Claims] In an automatic transmission in which a Rapigneaux planetary gear train having a single-row planetary gear and a double-row planetary gear that share one planetary carrier is arranged after a four-element torque converter consisting of two stators, a turbine, and a pump, A turbine shaft is provided to connect the turbine and the sun gear of the double-row planetary gear.
A stator cylinder shaft is provided that connects the first stator and the sun gear of the single-row planetary gear, a brake is provided for regulating the rotation of the stator cylinder shaft, a brake is provided for regulating the rotation of the planetary carrier, and the ring gear of the single-row planetary gear is connected to the first stator. A planetary gear train for an automatic transmission characterized by outputting power.