JPH11294545A - Planet gear type speed change device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a planet gear type speed change device capable of reducing its production cost and saving its floor space by simplifying its structure. SOLUTION: In a planet gear type speed change device providing 6 forward speed stages advancing and one back speed stage, the planet gear section 2a of the planet gear mechanism 2 corresponding to a clutch line C3 for third and fifth speed stages is constituted into two stages, and power is transmitted between the ring gear 2b of the mechanism and the ring gear 3b of the planet gear mechanism 3 corresponding to a clutch line C2 for second and sixth speed stages adjacent to the ring gear 2b and between the ring gear 5a of a planet gear mechanism 2 and the ring gear 5b of the planet gear mechanism 3 corresponding to a clutch line C2 for second and sixth speed stages adjacent to the ring gear 2b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a planetary gear type transmission mounted on an industrial vehicle such as a wheel loader or a forklift truck.

[0002]

2. Description of the Related Art As a planetary gear type transmission for a vehicle of this type, there is a conventional one as shown in FIG.

[0003] The power selectively transmitted from the lock-up clutch CL and the torque converter 1 is transmitted via a low-speed clutch CF, a high-speed clutch C5 and a reverse clutch C4 to a 3.5-speed clutch. A planetary gear mechanism 2 corresponding to C3, a planetary gear mechanism 3 corresponding to the 2.6-speed clutch C2, and a planetary gear mechanism 4 corresponding to the reverse / first-speed clutch C1 are three sets (three rows) of planetary gears. The transmission is transmitted to the mechanism, and the combination of these clutches and the planetary gear mechanism achieves the sixth forward speed and the first reverse speed (see FIG. 4).

[0004]

However, in the conventional planetary gear type transmission as described above, three sets (3
), The planetary gears (planetary gears) 2a, 3a, and 4a of the planetary gear mechanisms 2, 3, and 4 are constituted by one stage. Ring gears 2b, 3b, 4b from gear carriers 5a, 5b
Had to be communicated to That is, power transmission is performed between different rotating elements.

[0005] Therefore, it is necessary to connect the planetary gear carriers 5a, 5b and the ring gears 2b, 3b, 4b to each other by performing gear cutting or the like, which complicates the structure and leads to an increase in cost. This hindered space saving.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a planetary gear type transmission that can reduce the cost and space by simplifying the structure.

[0007]

A planetary gear type transmission according to the present invention for achieving the above object has a planetary gear mechanism and a rotary clutch mechanism provided in a plurality of rows from an engine side to a drive shaft side. In the transmission that achieves a plurality of speed stages by the combination of the above, the planetary gear portion of the planetary gear mechanism in the first row closest to the engine side is configured in two stages, and the ring gear of the mechanism and the planetary gears in the second row Power is transmitted between the ring gears of the gear mechanism and between the planetary gear carriers of the first row of planetary gear mechanisms and the second row of planetary gear mechanisms.

Further, in a transmission apparatus which achieves six forward speeds and one reverse speed by a combination of a planetary gear mechanism and a rotary clutch mechanism provided in three rows from the engine side to the drive shaft side. The planetary gear section of the planetary gear mechanism corresponding to the fifth-speed rotary clutch train is configured in two stages, and the ring gear of the mechanism and the adjacent ring gear of the planetary gear mechanism corresponding to the 2.6-speed rotary clutch train and The power is transmitted between the planetary gear carrier of the planetary gear mechanism corresponding to the 3.5-speed rotary clutch train and the planetary gear carrier of the planetary gear mechanism corresponding to the 2.6-speed rotary clutch train. And

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a planetary gear type transmission according to the present invention will be described in detail with reference to the drawings with reference to embodiments.

FIG. 1 is a conceptual diagram of a drive system of a planetary gear type transmission according to an embodiment of the present invention, and FIG. 2 is a power flow diagram when a 3/5 gear is operated. 3 is a power flow diagram when the 2.6-speed clutch operates, and FIG. 4 is a comparative explanatory diagram of the clutch combination, gear ratio, rotation speed and torque. In these drawings, the same members as those in FIG. 5 are denoted by the same reference numerals, and detailed description is omitted.

As shown in FIG. 1, the power selectively transmitted from the lock-up clutch CL and the torque converter 1 includes a low-speed (multi-plate) clutch CF and a high-speed (multi-plate) clutch CF.
The planetary gear mechanism 2 corresponding to the 3.5-speed (multi-plate) clutch C3 and the planetary gear corresponding to the 2.6-speed (multi-plate) clutch C2 via the clutch C5 and the reverse (multi-plate) clutch C4. The gears are transmitted to three sets (three rows) of planetary gear mechanisms, each of which includes a mechanism 3 and a planetary gear mechanism 4 corresponding to a reverse / first-speed (multi-plate) clutch C1. Achieving the first and second reverse speeds is the same as that of the transmission shown in FIG.

In this embodiment, the third and fifth-speed clutch C3 rows closest to the engine (not shown) (first row)
And the planetary gear mechanism 3 corresponding to the ring gear 2b of this mechanism and the adjacent 2nd- and 6th-speed clutch C2 row (second row). The planetary gear carriers 5a and 2 · 2 of the planetary gear mechanism 2 between the ring gears 3b and corresponding to the third and fifth speed clutch C3 rows.
The power transmission is performed between the planetary gear carriers 5b of the planetary gear mechanism 3 corresponding to the sixth-speed clutch C2 row,
Planetary gear mechanisms 2 and 2.6 corresponding to speed clutch C3
The ring gears 2b, 3b of the planetary gear mechanism 3 corresponding to the second row of speed clutches C and the planetary gear carriers 5a, 5b are integrally formed.

In FIG. 1, reference numerals 2c, 3c and 4c denote sun gears of the respective planetary gear mechanisms 2, 3 and 4, of which sun gear 2c is a reverse clutch C4 and a 3/5 speed clutch C3.
And the sun gears 3c and 4c are connected to the low speed clutch CF.
Is to be intermittent. Other configurations are the same as those in FIG.

[Operation / Effect] Because of such a configuration, as shown in FIG.
The combination of F, C5, C4, C3, C2, and C1 is changed to each clutch CF, C5, C4, C3, C2, C in the conventional example.
If the setting is made in the same manner as in the case of the combination of No. 1, the operation is as shown in the power flow diagram of FIG. 2 when the third- and fifth-speed clutch C3 is operated, and as the power flow diagram of FIG. In this case, power is transmitted, and the same functions as in the conventional example are achieved in the gear ratio and the like at each speed stage.

That is, at the time of the third speed in which the 3.5-speed clutch C3 and the low-speed clutch CF are connected, the power transmitted from the low-speed clutch CF (the input rotation on the engine side) passes through the sun gears 3c and 4c. And transmitted to the planetary gears 3a and 4a. The rotation of the planetary gear 3a is controlled by the planetary gear carrier 5a,
It is transmitted to the two-stage planetary gear 2a via the gear 5b and to the ring gear 4b via the planetary gear carrier 5b. The rotation of the two-stage planetary gear 2a is transmitted to the ring gear 2b and also to the ring gear 3b integral with the ring gear 2b. Thereby, the position of the planetary gear 4a rotates in the same direction as the input rotation direction on the engine side, and the carrier 5c
This rotation is transmitted to the drive shaft (not shown) (see FIG. 2A).

At the fifth speed when the third and fifth speed clutches C3 and C5 are connected, the power transmitted from the high speed clutch C5 (input rotation on the engine side) is transmitted to the planetary gear carriers 5a and 5b. Through two-stage planetary gear 2
a and the planetary gear 3a. Two-stage planetary gear 2a
Is transmitted to the ring gear 2b and also to the ring gear 3b integral with the ring gear 2b. The rotation of the planetary gear 3a is transmitted to the ring gear 4b via the planetary gear carrier 5b. Thereby, the position of the planetary gear 4a rotates in the same direction as the input rotation direction on the engine side, and this rotation is transmitted to the drive shaft side by the carrier 5c (see FIG. 2B).

On the other hand, at the second speed in which the 2.6-speed clutch C2 and the low-speed clutch CF are connected, the power (input rotation on the engine side) transmitted from the low-speed clutch CF is transmitted via the sun gears 3c and 4c. And transmitted to the planetary gears 3a and 4a. The rotation of the planetary gear 3a is directly transmitted to the ring gear 3b and also transmitted to the ring gear 4b via the planetary gear carrier 5b. Thereby, the position of the planetary gear 4a rotates in the same direction as the input rotation direction on the engine side, and this rotation is transmitted to the drive shaft side by the carrier 5c (see FIG. 3A).

At the sixth speed when the 2.6-speed clutch C2 and the high-speed clutch C5 are connected, the power transmitted from the high-speed clutch C5 (input rotation on the engine side) is transmitted via the planetary gear carrier 5b. And transmitted to the planetary gear 3a. The rotation of the planetary gear 3a is transmitted to the ring gear 4b via the planetary gear carrier 5b. Thereby, the position of the planetary gear 4a rotates in the same direction as the input rotation direction on the engine side, and this rotation is transmitted to the drive shaft side by the carrier 5c (see FIG. 3B).

As described above, in this embodiment, the planetary gear 2a of the planetary gear mechanism 2 corresponding to the third and fifth speed clutches C3 (first row) is configured in two stages, and the ring gear 2 of the mechanism is used.
b and between the ring gears 3b of the planetary gear mechanism 3 corresponding to the 2nd and 6th speed clutch C2 row (second row)
Even if power is transmitted between the planetary gear carrier 5a of the planetary gear mechanism 2 corresponding to the fifth speed clutch C3 row and the planetary gear carrier 5b of the planetary gear mechanism 3 corresponding to the 2.6 speed clutch C2 row, The same speed stage as the conventional example shown in FIG. 5 can be achieved at the same level in the gear ratio.

In this embodiment, since the power is transmitted between the same rotating elements as described above, the planetary gear mechanism 2 corresponding to the third and fifth speed clutches C3 and the second and sixth speed clutches C2 are provided. Ring gear 2 of planetary gear mechanism 3 corresponding to
b, 3b and the planetary gear carriers 5a, 5b can be integrally formed. As a result, cost and space can be reduced by simplifying the structure and reducing the number of parts.

It should be noted that the present invention is not limited to the above-described embodiment, and various changes can be made without departing from the spirit of the present invention.

[0022]

According to the first aspect of the present invention, there is provided a transmission which achieves a plurality of speed stages by combining a planetary gear mechanism and a rotary clutch mechanism provided in a plurality of rows from the engine side to the drive shaft side. , The planetary gear section of the planetary gear mechanism of the first row closest to the engine side is configured in two stages,
Power transmission is performed between the ring gear of the mechanism and the ring gear of the second row planetary gear mechanism and between the planetary gear carrier of the first row planetary gear mechanism and the planetary gear carrier of the second row planetary gear mechanism. Since the ring gear and the planetary gear carrier of the first row of planetary gear mechanisms and the second row of planetary gear mechanisms can be integrally formed, the structure is simplified and the number of parts is reduced. Thereby, cost reduction and space saving can be achieved.

According to the second aspect of the present invention, the sixth forward speed and the first reverse speed are achieved by a combination of the planetary gear mechanism and the rotary clutch mechanism provided in three rows from the engine side to the drive shaft side. In the transmission, the planetary gear mechanism of the planetary gear mechanism corresponding to the 3.5-speed rotary clutch train is configured in two stages, and the planetary gear corresponding to the ring gear of the mechanism and the adjacent 2.6-speed rotary clutch train. The power transmission is performed between the ring gears of the gear mechanism and between the planetary gear carrier of the planetary gear mechanism corresponding to the 3.5-speed rotary clutch train and the planetary gear carrier of the planetary gear mechanism corresponding to the 2.6-speed rotary clutch train. Since the present invention is characterized in that it is performed, the same effect as the first aspect of the invention can be obtained.

[Brief description of the drawings]

FIG. 1 is a conceptual diagram of a drive system of a planetary gear type transmission showing one embodiment of the present invention.

FIG. 2 is a power flow diagram when the clutch for the third and fifth speed is operated.

FIG. 3 is a power flow diagram when the clutch for the 2nd and 6th speeds is operated.

FIG. 4 is a comparative explanatory diagram of a combination of clutches, a gear ratio, a rotation speed, and a torque.

FIG. 5 is a conceptual diagram of a drive system of a planetary gear type transmission showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Torque converter 2, 3, 4 Planetary gear mechanism 2a, 3a, 4a Planetary gear (planetary gear) 2b, 3b, 4b Ring gear 2c, 3c, 4c Sun gear 5a, 5b, 5c Planetary gear carrier CL Lockup clutch CF Low-speed clutch C5 High-speed clutch C4 Reverse clutch C3 3.5-speed clutch C2 2.6-speed clutch C1 Reverse-first-speed clutch

Claims (2)

[Claims] 1. A transmission which achieves a plurality of speed stages by a combination of a planetary gear mechanism and a rotary clutch mechanism provided in a plurality of rows from an engine side to a drive shaft side, wherein a first row closest to the engine side is provided. The planetary gear unit of the second planetary gear mechanism is configured in two stages, between the ring gear of the mechanism and the ring gear of the second row planetary gear mechanism, and the planetary gear carrier and the second planetary gear mechanism of the first row of planetary gear mechanisms. A planetary gear type transmission, wherein power is transmitted between planetary gear carriers of a second-row planetary gear mechanism. 2. From the engine side to the drive shaft side
In a transmission that achieves six forward speeds and one reverse speed by a combination of a planetary gear mechanism and a rotary clutch mechanism provided over a row, a planetary gear mechanism corresponding to a 3.5-speed rotary clutch row is provided. The planetary gear section is configured in two stages, and between the ring gear of the mechanism and the adjacent ring gear of the planetary gear mechanism corresponding to the 2.6-speed rotary clutch train and the planet corresponding to the 3.5-speed rotary clutch train. A planetary gear-type transmission, wherein power is transmitted between a planetary gear carrier of a gear mechanism and a planetary gear carrier of a planetary gear mechanism corresponding to a 2.6-speed rotary clutch train.