JPH01203741A - Planetary gear type change gear - Google Patents

Abstract

PURPOSE:To select operating force lightly and smoothly by performing a changeover between direct drive and reduction radio drive with a shift fork, and reciprocating a sleeve. CONSTITUTION:When a selector sleeve is situated in a direct driving position, a spline 21c is engaged with a spline 17a. Therefore an output shaft 10A is rotated at a high speed mode. Next, when it is selected by a shaft fork 23 and transferred to a reduction ratio driving position with the selector sleeve 21 moved, a spline 20c is engaged with a spline 25a. 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 can be done smoothly with light operating force.

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. 4, in a planetary gear type transmission, a sun gear 2 is fixed to an input shaft l, a carrier 4 is spline-coupled to an output shaft 3 so as to be movable in the axial direction, and 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. It has been proposed that the planetary gear 6 and the ring gear 5 constitute a planetary gear unit U (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 locked to the casing 7, and the planetary gear 6 is caused to rotate planetarily.

(Problem to be solved by the invention) However, since switching between high speed mode and low speed mode avoids moving the entire planetary gear unit U, there are problems in that a large operating force is required and the structure is complicated. .

The present invention has been made to solve the above-mentioned problems in the prior art, and its basic purpose is to enable smooth switching between high-speed mode and low-speed mode with a light operating force.

(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 path of the planetary gear unit and drive directly, and between the surface input and output members through the gear system path of the planetary gear unit. In a planetary gear type transmission that switches to deceleration drive, the switching means includes:
Selectively connects the input stamp material and the carrier connected to the output member during direct drive, and selectively connects the input member and sun gear during deceleration drive, and fixes the ring gear and casing to the switching means during deceleration drive. However, the present invention is characterized in that a switching member is provided for releasing the fixation between the ring gear and the casing during direct driving.

The switching member may have a retaining portion that moves on an engaging portion provided on the ring gear and the casing, or may be integrated with the ring gear whose rotational direction is regulated relative to the casing and is slidable in the axial direction. Any of the combined configurations can be employed.

(Operations and Effects of the Invention) The present invention selectively connects an input member and a sun gear, and an input member and a carrier using a switching member, so that when a carrier is selected (
During direct drive), the fixation between the ring gear and the casing is released.

Therefore, since the ring gear becomes free during direct drive (high speed mode), over-rotation of the planetary gear can be effectively prevented.

In addition, since the sun gear and carrier are only selectively connected using the switching member, there is no need to move the entire planetary gear unit as in the conventional case, and the operating force is light and switching can be performed smoothly, resulting in a simple structure. .

Furthermore, since the switching member is separate from the planetary gear unit and is small and has an engaging part that moves on the engaging part provided on the ring gear and the casing, the operating force is extremely light and smooth. Can be switched.

Furthermore, the switching member has a configuration in which the rotational direction is regulated relative to the casing and is integrally coupled with a ring gear that can slide in the axial direction, so that the engaging portion is separately machined like the switching member type described above. There is no need for it and the processability can be improved.

(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 casing II, and a front wheel drive output shaft 10A is arranged in the lower part of the casing 11. The output shaft 10B for
2 and the output shafts 10A, 10B, a planetary gear type differential device B as a planetary gear type differential device member is interposed, basically.

FIG. 2 shows a planetary gear type transmission in which a ring gear 20 does not move in the axial direction with respect to the casing 11.

The output shaft is connected to the bearing (not specifically shown) in the casing 11! OA is rotatably supported, and an inlet J shaft 12 is rotatably supported by a bearing 13 of a casing 11 coaxially with the output shaft 10A.

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 sun gear 15 of a planetary gear sub-transmission device A is rotatably fitted to the output shaft 10A in close proximity to the input shaft 12 via a needle bearing I6.

The output shaft! A carrier 17 is fitted into the OA in close proximity to the sun gear 15, and a spline +7b is formed on the outer periphery of the carrier I7, and the spline 17b is spline-coupled with the ring gear 32 of the planetary gear differential B. has been done.

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 gear 51 of the front output shaft 10B are connected by a chain 52, and the sun gear 35 is fixed to the rear output shaft 10A.

Therefore, when the carrier 17 rotates, the ring gear 3
2. 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. Rear output shaft +O via sun gear 35
A is rotated.

The carrier 17 includes the sun gear 15 and the ring gear 2.
A plurality of planetary gears 18 meshing with each other are supported by shafts 19, respectively.

The ring gear 20 is supported by a planetary gear 18.

A spline 12a is formed on the outer periphery of the input shaft 12, and a spline 15a facing the spline +2a is formed on the flange portion 15b of the sun gear 15, and a switching switch has a spline 21a that always meshes with both splines 12a and 15a. A sleeve 21 is provided.

The flange portion 21b of the switching sleeve 21? A spline 21c is formed here, and the spline 21c meshes with the spline 17a of the carrier 17 when the sleeve 21 is in the illustrated direct drive position, and when the sleeve 21 is in the reduction ratio drive position (secondary drive position where the sleeve 21 is axially moved to the right in the figure). (see dotted chain line), the mesh with the spline 17a is disengaged.

A shift fork 23 is engaged with the switching sleeve 21, and the shift fork 23 is connected to the man/output shaft +2. I
It is fitted and supported by a shift rod 22 that is slidably supported by the casing 11 parallel to the OA and IOB, and the switching sliding of the shift rod 22 moves the switching sleeve 21 via the shift fork 23 to the direct drive position. and the reduction ratio drive position.

The switching sleeve 21 has splines 24a on the outer periphery.
A spline 20a is formed on the inner periphery of the ring gear 20 to engage with the spline 24a when the switching sleeve 21 moves to the reduction ratio drive position.

A casing fixing member (iron-based member) 25 is fixed to the casing (made of aluminum casting) 11 with a gap from the ring gear 20 by spline connection, and the casing fixing member 25
A spline 25a facing the spline 20a of the ring gear 20 is formed on the flange portion 25b, and the spline 24a of the switching member 24 is formed on the spline 25a.
They always mesh together.

With the above configuration, the switching sleeve 2I is now in the direct drive position in the state shown in FIG.
7aA meshing, and the splines 24a of the switching member 24 and the splines 20a of the ring gear 20 are out of mesh.

Therefore, the rotational force of the input shaft 12 is
1 → carrier 17 → ring gear 32 etc. → output shaft 10A,
It is directly transmitted to IOB, and the output shafts IOA and IOB are rotated in high speed mode.

During this direct drive, the ring gear 20 becomes free with respect to the casing 11, so over-rotation of the planetary gear 18 is effectively prevented.

Next, the shift fork 23 is used to move the switching sleeve 21 in the axial direction to the right in the figure to switch it to the reduction ratio drive position.
7 disengages from the spline 17a, and the switching member 2
4 spline 24a is spline 2 of ring gear 20
It meshes with 0a.

Therefore, the ring gear 20 includes the spline 20a, the spline 24a of the switching member 24, and the casing fixing member 25.
Since the input shaft 12 is fixed to the casing 11 via the spline 25a, the rotational force of the input shaft 12 is decelerated and transmitted to the sun gear 15, the planetary gear 18, the carrier I7, the ring gear 32, etc., and the output shafts 10A and IOB. ,
Output shaft IOA, 1013 is rotated in low speed mode.

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

FIG. 3 shows a planetary gear type transmission in which a ring gear 20 moves in the axial direction with respect to the casing 11. Note that parts having the same structure and function as those in FIG. 2 are given the same numbers, and detailed explanations will be omitted.

In this embodiment, the ring gear 20 is extended and the switching section 2
4° is integrally formed, and the switching portion 24° is engaged with the switching sleeve 21, while the outer periphery of the ring gear 20 has a
A spline 20c is formed that engages with a spline 25a of the casing fixing member 25 when the switching sleeve 21 moves to the reduction ratio drive position.

With the above configuration, the switching sleeve 21 is now in the direct drive position in the state shown in FIG.
7a, and the spline 20c of the ring gear 20 and the spline 25a of the casing fixing member 25 are disengaged.

Therefore, the rotational force of the input shaft 12 is transferred to the switching sleeve 2
1 → carrier 17 → ring gear 32 etc. → output shaft 10A,
It is directly transmitted to IOB, and the output shafts IOA and IOB are rotated in high speed mode. During this direct drive, the ring gear 20
is free with respect to the casing 11, so over-rotation of the planetary gear 18 is effectively prevented.

Next, when the switching sleeve 21 is axially moved to the right in the figure by the shift fork 23 and switched to the reduction ratio drive position, the spline 21c of the switching sleeve 21 and the carrier 1
7 disengages from the spline 17a, and the spline 20C of the ring gear 20 engages with the spline 25a of the casing fixing member 25.

Therefore, since the ring gear 20 is fixed to the casing 11, the rotational force of the input shaft 12 is transmitted to the sun gear! 5 - planetary gear 18 -> carrier 17 - ring gear 32 etc. -> deceleration is transmitted to output shafts 10A, 10B,
The output shafts 10A, 1013 are rotated in low speed mode.

This switching between direct drive and reduction ratio drive is also possible with shift
Since the switching sleeve 21 is simply moved back and forth by the lever 23, 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 a main part of a planetary gear type transmission according to the present invention, FIG. 2 is an enlarged sectional view of a main part of FIG. 1 of a first embodiment,
Fig. 3 is an enlarged sectional view of the main part of Fig. 1 of the second embodiment, Fig. 4 is a sectional view of the conventional planetary gear type transmission during direct drive, and Fig. 5 is the reduction ratio drive of Fig. 4. FIG. IO...output shaft, 1...casing, I2...
...Input shaft (input member), 15...Sun gear, 15a...Spline, 17...Carrier, 17a
... Spline, 18... Planetary gear, 20.
...Ring gear, 20a, 20c...Spline,
21... Switching sleeve, 21a, 21c... Spline, 24... Switching member, 24'... Switching part, 24a... Spline, 25... Casing fixing member, 25a... Spline, 34...Carrier, A...
・Planetary gear type transmission, B...Planetary gear type differential device. Figure 1 10th

Claims (3)

[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, in which the input and output members are switched to be driven directly by bypassing the gear path of the planetary gear unit, and the input and output members are switched to be driven at a reduced speed via the gear path of the planetary gear unit. The switching means selectively connects the input member and the carrier connected to the output member during direct driving, and the input member and the sun gear during deceleration driving, and causes the switching means to selectively connect the carrier connected to the input member and the output member during deceleration driving. 1. A planetary gear type transmission, comprising a switching member that fixes a gear and a casing and releases the fixation between the ring gear and the casing during direct drive. (2) The planetary gear type transmission according to claim 1, wherein the switching member has an engaging portion that moves on an engaging portion provided on the ring gear and the casing. (3) The planetary gear according to claim 1, wherein the switching member is integrally connected to a ring gear whose rotational direction is regulated with respect to the casing and which is slidable in the axial direction. type transmission.