JPH01203740A - Planetary gear type change gear - Google Patents

Abstract

PURPOSE:To perform a changeover between high speed and low speed smoothly with a simple structure by installing a planetary gear unit interposingly between an input member and an output member, having a carrier slidden by a selector means, and connecting this carrier to the output member. CONSTITUTION:When a selector sleeve 21 is situated in a direct driving position, a spline 21c is engaged with a spline 12a of an input shaft 12 and a spline 30a of a transfer sleeve 30. Torque of the input shaft 12 is directly transmitted to an output shaft 10A which is therefore rotated at a high speed mode. When being selected to a reduction gear ratio driving position, the spline 21c is engaged with a spline 15a of a sun gear 15 and simultaneously a carrier 17 is also interlocked and slidden, so that a spline 17c is engaged with a spline 31a. Accordingly, the output shaft 10A is rotated at a low speed mode. Thus, a changeover between the high speed mode and the low speed mode is smoothly performable by dint of light operating force through a simple structure.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to improvements in planetary gear transmissions.

(Prior Art) Conventionally, as shown in FIG. 3, in a planetary gear type transmission, an input shaft and a sun gear 2 are fixed, and a carrier 4 is spline-coupled to an output shaft 3 so as to be movable in the axial direction. A planetary gear 6 that meshes with the sun gear 2 and ring gear 5 is supported on the carrier 4. The ring gear 5 is supported by the planetary gear 6, and the carrier 4. A system in which a planetary gear 6 and a ring gear 5 constitute a planetary gear unit U has been proposed (see Japanese Patent Publication No. 7419/1983).

During direct drive (high speed mode), the planetary gear unit U is moved to the right as shown in the figure, and the ring gear 5 is
is set free to prevent over-rotation of the planetary gear 6, while at the time of reduction ratio drive (low speed mode), the planetary gear unit U is moved to the left as shown in FIG.
is connected to the casing 7 to cause the planetary gear 6 to perform planetary rotational motion.

On the other hand, as shown in FIG. 5, a sun gear 2 is fixed to the input shaft (2), and a carrier 4 is provided that supports a ring gear 5 fixed to a casing 7 and a planetary gear 6 that meshes with the sun gear 2. (fast mode),
The first coupling sleeve 8 and the second coupling sleeve 9 are moved to the illustrated positions to free the planetary gear unit U and prevent the planetary gear 6 from over-rotating. While moving the coupling sleeve 8 to the right to connect the input shaft I and the sun gear 2, the second
It has been proposed to connect the carrier 4 and the output shaft 3 by moving the coupling sleeve 9 to the right (Utility Model Application No. 61-7).
(See Publication No. 3860).

(Problem to be Solved by the Invention) However, in the former prior art, switching between high-speed mode and low-speed mode involves moving the entire planetary gear unit U, which requires a large operating force and complicates the structure. There was a problem.

Further, in the latter prior art, switching between the high-speed mode and the low-speed mode requires moving the two coupling sleeves 8.9 at the same time, which poses a problem in that the switching structure becomes complicated.

The present invention was made to solve the above-mentioned conventional problems, and its basic purpose is to enable smooth switching between high-speed mode and low-speed mode with a simple structure and with light operating force. It is something to do.

(Means for Solving the Problems) Therefore, in the present invention, a planetary gear unit consisting of a sun gear, a ring gear, and a planetary gear meshing with both gears and supported by a carrier is interposed between an input member and an output member. The switching means switches between the input and output members so as to bypass the gear system of the planetary gear unit and directly drive the input and output members, and also decelerates the input and output members via the gear system of the planetary gear unit. In the planetary gear type transmission that switches to drive, the switching means connects the input member and the transmission member that rotatably supports the planetary gear unit on the outer periphery and is connected to the output member during direct drive. , the input member and the sun gear are connected during deceleration driving, and when the input member and the sun gear are connected by the switching means, the carrier is slid by the switching means to connect the carrier and the output member. It is characterized by the following.

(Operations and Effects of the Invention) According to the present invention, the carrier is slid from the switching means 1 to selectively connect the transmission member and the sun gear.

Therefore, by simply sliding the carrier supporting the planetary gear using the switching means, over-rotation of the planetary gear can be effectively prevented during direct drive (high-speed mode). , there is no need to move the two coupling sleeves at the same time,
The operating force is light, the switching operation is smooth, and the structure is simple.

(Embodiments) Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

As shown in FIG. 1, in the transmission of a four-wheel drive vehicle, an input shaft 12 as an input member and an output shaft 10A for rear wheel drive are arranged in the upper part of a cage jig 11, and a front wheel drive output shaft 10A is arranged in the lower part of the casing II. The output shaft 10B for
2 and the output shafts 10A, 10B, a planetary gear type auxiliary transmission device A and a planetary gear type differential device B are interposed, and the basic configuration is as follows.

As shown in FIG. 2, an output shaft 10A is rotatably supported by a bearing (not specifically shown) in a casing It, and an input shaft 12 is supported coaxially with the output shaft 10A by a bearing 13 in a casing 11. It is rotatably supported.

The tip of the output shaft 10A is rotatably supported by a needle bearing 14 interposed between the output shaft 10A and the shaft hole of the input shaft 12.

A transmission sleeve (transmission member) 30 is fitted to the output shaft 10A in proximity to the input shaft 12, and a spline 30a is formed on the rising end 30b of the transmission sleeve 30 on the input shaft I2 side, and A transmission ring (transmission member) 31 is fixed to the side end.

A spline 31a is formed on the inner periphery of the transmission ring 31, and a spline 31b is formed on the outer periphery of the transmission ring 3I.
is formed, and the outer peripheral spline 3tb is spline connected to a ring gear 32 of a planetary gear type differential device (output member) B.

The differential device B has a planetary gear 33 of a double type (double pinion type), and a carrier 34 as shown in FIG.
On the other hand, gear 5 is controlled to be attached and detached (connected only during 4-wheel drive).
0 and the carrier 51 of the front output shaft lOB are connected to the chain 5.
2, and a sun gear 35 is fixed to the rear output shaft 10A.

Therefore, when the transmission ring 31 rotates together with the transmission sleeve 30, the ring gear 32. Planetary gear 33. At the same time as the front output shaft 10B is rotated via the carrier 34 etc., the ring gear 32. Planetary gear 33. The rear output shaft 10A is rotated via the sun gear 35 and the like.

A sun gear 15 of a planetary gear sub-transmission bag mA is rotatably fitted into the upper transmission sleeve 30 via a needle bearing 16.

On the other hand, a plurality of planetary gears 18 meshing with the sun gear 15 and the ring gear 20 are mounted on the carrier 17 on the shaft I9.
Each is supported by

The ring gear 20 is fixedly supported by the casing [1 by spline connection.

A spline 12a is formed on the outer periphery of the input shaft 12, and the spline 30a of the rising end 30b of the transmission sleeve 30 faces the spline 12a, and the flange 15b of the sun gear 15 faces the spline 12a. A spline 15a is formed.

The input shaft 12 has a spline +2a of the input shaft 12.
A switching sleeve 21 is provided which has a spline 21a that constantly engages.

The spline 21a of the switching sleeve 21 has
In the illustrated direct drive position, the sleeve 21 engages the splines 30a of the transmission sleeve 30, and the sleeve 21
At the reduction ratio drive position (see the two-dot chain line) where the gear has moved axially to the right in the figure, it is disengaged from the spline 30a.
A notch 21b is formed for engaging with the spline 15a of the sun gear 15.

A shift fork 23 is engaged with the switching sleeve 21, and the switching sleeve 21 is switched between a direct drive position and a reduction ratio drive position via the shift fork 23.

Further, the switching sleeve 21 is engaged with the engaging portion 17b of the carrier 17, and the carrier 17 is formed with a spline 17c facing the spline 31a of the transmission ring 31. The carrier 17 is slid, and the spline 17c and the spline 31a are disengaged at the direct drive position of the carrier 17, and the spline 1 is disengaged from the spline 31a at the reduction ratio drive position of the carrier 17.
7c and the spline 31a are engaged with each other, and if the configuration is as described above, in the state shown in FIG. 1, the switching sleeve 21 is in the direct driving position, and the switching sleeve 2
1 spline 21c is the spline 12a of input shaft 12
and the spline 30a of the transmission sleeve 30,
The splines 17c of the carrier 17 and the splines 31a of the transmission ring 31 are disengaged from each other.

Therefore, the rotational force of the input shaft 12 is transferred to the switching sleeve 2
1 → Transmission sleeve 30 → Transmission ring 31 - Ring gear 3
2nd grade - output shaft 10A, directly transmitted to IOB, output shaft 1
0A, IOB is rotated in high speed mode.

During this direct drive, the sun gear 15. Carrier 17th class is a person,
Output shaft 12.10A, l OB, switching sleeve 21.
Since the transmission sleeve 30 and the transmission ring 31 become free, and the planetary gear 18 comes to a halt, over-rotation is effectively prevented. Next, shift lever 2
3, when the switching sleeve 2I is axially moved rightward in the figure and switched to the reduction ratio drive position, the spline 21c of the switching sleeve 21 and the spline 30 of the transmission sleeve 30
When the spline 21c is disengaged from the spline 15a of the sun gear 15, the carrier 17 is also slid in conjunction with the spline 15a of the carrier I7.
7a meshes with the spline 31a of the transmission ring 31.

Therefore, the rotational force of the input shaft 12 is transferred to the switching sleeve 2
1 → sun gear 15 → planetary gear 18 - carrier 17
→ Transmission ring 31 → Ring gear 32 etc. → Output tube 10A,
The deceleration is transmitted to the IOB, and the output shaft 10A and IOB are rotated in a low speed mode.

Switching between direct drive and reduction ratio drive is achieved by simply moving the switching sleeve 21 and carrier 17 back and forth using the shift fork 23, so that the operating force is light and the switching operation can be performed smoothly.

[Brief explanation of the drawing]

Fig. 1 is a sectional side view of the main part of a planetary gear type transmission according to the present invention, Fig. 2 is an enlarged sectional view of the main part of Fig. 1, and Fig. 3 is a direct drive state of a conventional planetary gear type transmission. 4 is an enlarged sectional view of the main part of FIG. 3 when driven by a reduction ratio, and FIG. 5 is a sectional view of another conventional planetary gear type transmission when it is directly driven. 10...Output shaft, 11...Casing,! 2...
Input shaft (input member), 15... sun gear, 15a,
l5c, l5d-Spline, 17...Carrier, 17c...Spline, 18...Planetary gear, 20...Ring gear, 2I...Switching sleeve, 2
1a...Spline, 30...Transmission sleeve, 30
a...Spline, 31...Transmission ring, 31a,
31c... Spline, 34... Carrier, A... Planetary gear type transmission, B... Planetary gear type differential device (output member).

Claims (1)

[Claims] (1) A planetary gear unit consisting of a sun gear, a ring gear, and a planetary gear meshed with both gears and supported by a carrier is interposed between the input member and the output member, and a switching means is used to connect the input and output members. In a planetary gear type transmission device, the input/output member is switched to be driven directly by bypassing the gear system path of the planetary gear unit, and the input/output member is switched to be driven at a reduced speed via the gear system path of the planetary gear unit, The switching means rotatably supports the input member and the planetary gear unit on the outer periphery during direct drive, and connects the transmission member connected to the output member, and connects the input member and the sun gear during deceleration drive. In addition, when the input member and the sun gear are connected by the switching means, the carrier is slid by the switching means to connect the carrier and the output member. .