JPH0446246A - Multistage transmission - Google Patents

Abstract

PURPOSE:To increase one stage of a shift stage without increase of the axial dimension of a transmission by arranging a pair of gears for adding a shift stage on the outer circumference of a planetary gear transmission mechanism. CONSTITUTION:The multistage transmission has same axial dimension as the one of forward three shift stages. Namely, when from the constitution shown in the figure a first clutch C1, a second clutch C2, a third gear 22, and a fourth gear 24 are removed and in addition a second gear 18 is set to always rotate in one body with a second shaft 12, it becomes an automatic transmission of forward three shift stages for FF. On the other hand, the third gear 22, the fourth gear 24, the first clutch C1, and the second clutch C2 arranged for provid ing an overdrive a fourth shift stage, are arranged so as to overlap in the axial position with a planetary gear transmission mechanism 14, the axial dimen sion of the transmission is not increased by arranging these members. Conse quently, the overdrive the fourth shift stage can be added without extending the total length and the device can be formed in small size.

Description

[Detailed description of the invention] (b) Industrial application field The present invention relates to a multi-speed transmission.

(B) Prior Art A conventional multi-stage transmission is disclosed in Japanese Patent Application Laid-Open No. 60-23657. The multi-stage transmission shown here has an input shaft and an output shaft arranged parallel to each other, and a three-speed forward planetary gear train section is provided on the input shaft side. A first gear pair and a second gear pair are provided between the output part and the output shaft, and between the input shaft and the output shaft, respectively, and the rotational force transmission state of the gear pair between the input shaft and the output shaft is controlled. It is equipped with a clutch for switching. 1st
．． In the case of second and third speeds, the clutch is kept in a released state. Thereby, the rotation of the input shaft is transmitted to the output shaft via the planetary gear train section and the first gear pair. The 1st, 2nd and 3rd speeds are obtained depending on the speed change of the planetary gear train. For the fourth speed, the clutch is engaged. Due to this.

Rotational force is transmitted via a second gear pair between the input shaft and the output shaft. With such a configuration, an overdrive gear can be added to the gears of the planetary gear train by adding a pair of gears and one clutch.

(c) Problems to be Solved by the Invention However, the conventional multi-stage transmission as described above has a problem in that the axial dimension of the transmission becomes large. That is, in addition to the first gear pair for transmitting the output rotation of the planetary gear train to the output shaft, a second gear pair for overdrive is arranged adjacent to the first gear pair, so that at least one gear The axial dimension of the entire transmission increases by the axial dimension required for arranging the transmission. Furthermore, in the embodiment shown in the above publication, the clutch for controlling the rotational force transmission of the overdrive gear pair is disposed adjacent to the overdrive gear pair, so that the axial dimension is further increased. Since this is basically an automatic transmission installed in a front-wheel drive vehicle with a horizontally mounted engine, a large axial dimension is not desirable in terms of vehicle installation.The present invention aims to solve this problem. There is.

(d) Means for Solving the Problems The present invention solves the problems described in "-" by arranging an overdrive gear pair on the outer periphery of a planetary gear transmission mechanism. That is, the multi-stage transmission according to the present invention includes a rotatably provided first shaft (10), a rotatable second shaft (12) arranged parallel to the first shaft, and a rotatable second shaft (12) that is integral with the first shaft. Or an input shaft (I) connected to rotate integrally with this, an output shaft (0) arranged concentrically with the input shaft at one end thereof, a planetary gear set (G, and G,), a clutch ( FC and HC)
and a planetary gear transmission mechanism (14) having brakes (B, , B, and 0WC) and capable of controlling the rotation ratio between the input shaft and the output shaft in multiple stages, and an output shaft of each planetary gear transmission mechanism. and a first gear (1
6) and a first gear set (20) consisting of a second gear (18)
When engaged, the rotational force can be transmitted between the output shaft of the planetary gear transmission mechanism and the second shaft through the first gear set, and when released, the rotational force of the planetary gear transmission mechanism can be transmitted through the first gear set. A first clutch (C1) that releases the rotational force transmission state between the output shaft and the second shaft, and a member (PC) other than the input shaft and output shaft of the planetary gear transmission mechanism are provided to rotate together. A second gear set (2
6) When engaged, it is possible to transmit rotational force between the member provided with the third gear of the planetary gear transmission mechanism and the second shaft via the second gear set, and when released, the second gear set is It has a second clutch (C2) that cancels the rotational force transmission state between the above-mentioned member and the second shaft via the second shaft.

Note that a part of the brake of the planetary gear transmission mechanism may be arranged on the second shaft side. That is, the third gear is fixed to the above-mentioned member of the planetary gear transmission mechanism, and the fourth gear is rotatably supported on the second shaft.

The second clutch can engage or release the fourth gear and the second shaft, and the brakes (B and 0WC) for fixing the above-mentioned members of the planetary gear transmission mechanism can fix the 461st wheel to a stationary part. It is provided on the second axis side.

Note that the symbols in parentheses indicate corresponding members in the embodiments described later.

(e) Operation When the first clutch is engaged and the second clutch is disengaged, the rotation of the output shaft of the planetary gear transmission mechanism is transmitted to the second shaft via the first gear and the second gear. If the planetary gear transmission mechanism has three forward speeds, the 1st, 2nd and 3rd speeds can be obtained depending on the speed change. Conversely, when the first clutch is released, the second clutch is engaged, and the planetary gear transmission mechanism is placed in a directly connected state (speed ratio 1 state), all rotating parts of the planetary gear transmission mechanism rotate together with the input shaft. state. Therefore, the rotation of the first shaft is caused by the third gear and the fourth gear.
It will be transmitted to the second shaft via the gear. If the gear ratio of the third gear and the fourth gear is set as an overdrive gear ratio, the fourth speed can be obtained.

Since the second gear set is provided on the outer periphery of the planetary gear transmission mechanism, the axial dimension of the entire transmission can be reduced by the axial dimension of the second gear set compared to the conventional example.
If the first clutch is arranged between the second gear and the fourth gear of the second shaft, the axial dimension of the first clutch can also be reduced. By arranging this on the second axis side, the axial dimension can also be reduced by this amount.

(F) Example (First Example) A first example is shown in FIGS. 1 and 2. As shown in FIG. 1, the multi-stage transmission has a rotatably provided first shaft 10, a first
a second shaft 12 arranged parallel to the shaft and rotatably supported; Planetary gear transmission mechanism 14, the first gears meshing with each other
A first gear set 20 consisting of a gear 16 and a second gear 18, a second gear set 26 consisting of a third gear 22 and a fourth gear 24 that mesh with each other, a first clutch CI and a second clutch C2.
have. The first shaft 10 is a member integral with the input shaft I of the planetary gear transmission mechanism 14. A first gear 16 is fixed to the output shaft O of the planetary gear transmission mechanism 14. On the other hand, a second gear 18 that meshes with the first gear 16 is rotatably supported by the second shaft 12.

The third gear 22 is fixed to the second pinion carrier PC1 of the planetary gear transmission mechanism 14. A fourth gear 24 that meshes with the third gear 22 is rotatably supported by the second shaft 12. When the first clutch C3 is engaged, the second gear 1
8 and the second shaft 12 can be connected to rotate together. When the second clutch C2 is engaged, the fourth gear 24 and the second shaft 12 can be connected to rotate together.

The planetary gear transmission mechanism 14 is a well-known Simpson type planetary gear transmission mechanism with three forward speeds and one reverse speed. This planetary gear transmission mechanism 14 includes an input shaft I, a first planetary gear set G1, a second planetary gear set G3, a forward clutch FC, and a high clutch HC.
, a second brake B2, a low and reverse brake B8, and a one-way clutch 0WC1 output shaft 0. The first planetary gear set G1 includes a first pinion gear P1
, a first sun gear S1, and a first internal gear R. The first pinion gear P meshes with the first sun gear S and the first internal gear R3 at the same time. Similarly, the second planetary gear set G8 also has a second pinion carrier PC that rotatably supports the IN2 pinion gear P2.
, second sun gear S8, and second internal gear R8
The second pinion gear P, which is configured from the above, meshes with the second sun gear S2 and the second internal gear R at the same time. The input shaft I can be connected to a first internal gear R via a forward clutch FC, and can also be connected to a first sun gear S1 and a second sun gear s2 via a high clutch HC. The output shaft O is always connected to the first pinion carrier PC1 and the second internal gear R2. The first sun gear S1 and the second sun gear S2 are always connected and can be fixed to a stationary part by a second brake B2. The second pinion carrier PCo can be fixed to a stationary part by a low and reverse brake B1. One way clutch O
WC is provided in parallel with low and reverse brake B1.

As shown in FIG. 2, this multi-stage transmission operates by selectively operating a first clutch C1, a second clutch C2, a forward clutch FC, a high clutch HC, a low and reverse brake B, and a second brake B. , four forward speeds and one reverse speed can be obtained.

First, the 1st, 2nd and 3rd speeds are achieved by shifting within the planetary gear transmission mechanism 14. That is, in gear other than 4th gear, the first clutch C3 is engaged and the second clutch C2 is engaged.
has been released. Therefore, the first gear 16 and the second gear
The rotational force is transmitted through the gear 18, and the third gear 22
The rotational force inputted to the planetary gear transmission #I14 from the sixth working shaft 10, in which the rotational force is not transmitted by the fourth gear 24, becomes a predetermined gear ratio according to the operation of each component, and the rotational force is transmitted to the output shaft O. transmitted to. The rotational force of the output shaft O is transferred to the first gear 16
and is transmitted to the second shaft 12 via the second gear 18. The gear ratio in this case is the gear ratio of the planetary gear transmission mechanism 14 multiplied by the gear ratio 11 between the first gear 16 and the second tooth i[18. If the first gear 16 and the second gear 18 are the same gear, the gear ratio i+ will be 1, and the gear ratio of the third speed will be 1.
00, and the gear ratios for the first speed and second speed are as shown in FIG. The same applies when reversing. In addition, ρ1 and ρ2 in FIG. 2 are the ratio of the number of teeth of the first internal gear R3 and the number of teeth of the first sun gear S, and the number of teeth of the second internal gear R2 and the number of teeth of the second sun gear SR, respectively. This is the ratio of

On the other hand, in the fourth speed, the first clutch C6 is released and the second clutch C2 is engaged. Further, the planetary gear transmission mechanism 14 is in a directly connected state, that is, both the forward clutch FC and the high clutch HC are engaged, and all rotating members are in a state in which they rotate together with the input axle load. ), the second pinion carrier PC3 also rotates at the same time as the input shaft ■, and the rotation of this is the third gear 22 and the fourth tooth! 24 to the second shaft 12. In this case, the gear ratio is 3rd
It is determined by the gear specific gravity 2 of the gear 22 and the fourth gear 24. By setting this gear ratio 12 to, for example, 075, an overdrive fourth speed can be obtained. Therefore, the gear ratio of the overdrive fourth speed can be set as desired by arbitrarily setting the third gear 22 and the fourth gear 24.

This multi-stage transmission has the same axial dimensions as the one for three forward speeds. That is, from the configuration shown in FIG. 1, the first clutch C1, the second clutch C2, the third gear 22, and the fourth gear 2
4 is removed and the second gear 18 is always rotated integrally with the second shaft 12, a three-speed forward FF automatic transmission is obtained. On the other hand, the third gear 22, the fourth gear 24, the first clutch C3, and the second clutch C2 arranged to provide the overdrive fourth speed are the planetary gear transmission W4.
14 and are arranged so that their axial positions overlap,
By arranging these members, the axial dimension is not increased. Therefore, the overdrive fourth speed can be added without increasing the overall length, and the device can be made smaller.

In the embodiment shown in FIG. 1, the first clutch C1 is provided on the second shaft 12 side, but the first clutch C1 is provided on the first shaft l
It can also be placed on the O side. That is, the first gear 16
is rotatably supported on the output shaft 0, and the first
A clutch C3 is disposed, while the second gear 18 is connected to the second shaft 1.
2 should always be connected.

Similarly, the second clutch C2 can also be arranged on the first shaft 10 side.

Further, in this embodiment, the third gear 22 is provided integrally with the second pinion carrier PC2, but the planetary gear transmission mechanism 14
Which rotating member is the third gear 22 included in?
may be provided. However, input work or output shaft 0 has a third
Providing the gear 22 is not preferable because it increases the axial dimension of the planetary gear transmission mechanism 14.

Further, in this embodiment, a Simpson-type 3-speed forward gear is used as the planetary gear transmission mechanism 14, but any other type of planetary gear such as a 3-speed forward gear, a 2-speed forward gear, a 4-speed forward gear, etc. Shift #! It doesn't matter if it's on the side.

(Second Embodiment) FIG. 3 shows a second embodiment. This second embodiment is a low and reverse brake B constituting a planetary gear transmission mechanism 14.
1 and one-way clutch OWC are arranged on the second shaft 12 side.

Since the low and reverse brake B+ and one-way clutch OWC are for fixing the second pinion carrier PCI to a stationary part, the second pinion carrier P
A similar function can be obtained by fixing the fourth gear 24, which rotates in a fixed relationship with the third gear 22, which rotates together with Ct, to a stationary part. By arranging the low and reverse brake B and the one-way clutch OWC on the second shaft 12 side, the axial dimension on the first shaft 10 side can be further shortened.

(Third Embodiment) FIG. 4 shows a third embodiment. In this third embodiment, the second axis 1
A planetary gear transmission mechanism 14 is arranged on the second side. Even with this arrangement, basically the same effect as in the first embodiment described above can be obtained.

(G) As described in detail, according to the present invention, the gear pair for adding a gear stage is disposed on the outer periphery of the planetary gear transmission mechanism, thereby increasing the axial dimension of the transmission. The gear stage can be increased by one without having to change the gear position.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing the first embodiment, FIG. 2 is a diagram showing the combination of elements operating at each gear stage of the first embodiment, and FIG.
FIG. 4 is a diagram showing a third embodiment. DESCRIPTION OF SYMBOLS 10... First shaft, 12... Second shaft, 14. Planetary gear transmission mechanism, 16... First gear. 18...Second gear, 20...First gear set, 22...
- Third gear, 24... Fourth gear, 26... Second gear set, ■... Input shaft, 0... Output shaft.

Claims (1)

[Claims] 1. A rotatably provided first shaft; a rotatable second shaft disposed parallel to the first shaft; It has an input shaft connected to the input shaft, an output shaft located concentrically with the input shaft at one end thereof, a planetary gear set, a clutch, and a brake, and controls the rotation ratio between the input shaft and the output shaft in multiple stages. a possible planetary gear transmission mechanism; a first gear and a second gear meshing with each other provided on an output shaft and a second shaft of the planetary gear transmission mechanism, respectively;
A first gear set consisting of gears enables transmission of rotational force between the output shaft and the second shaft of the planetary gear transmission mechanism through the first gear set when engaged, and transmits torque through the first gear set when released. a first clutch that releases the rotational force transmission state between the output shaft and the second shaft of the planetary gear transmission mechanism; A second gear set consisting of a third gear and a fourth gear provided on the second shaft so as to mesh with the third gear, and a third gear of a planetary gear transmission mechanism provided through the second gear set when engaged. a second clutch that enables the transmission of rotational force between the member and the second shaft, and when released, releases the state of transmission of the rotational force between the member and the second shaft via the second gear set; Multi-speed transmission. 2. The third gear is fixed to the above-mentioned member of the planetary gear transmission mechanism, the fourth gear is rotatably supported by the second shaft, and the second clutch connects or connects the fourth gear and the second shaft. 2. The multi-stage transmission according to claim 1, wherein a releasable brake for fixing said member of the planetary gear transmission mechanism is provided on the second shaft side so as to enable fixation of the fourth gear to the stationary part. 3. A rotatably provided first shaft, a rotatable second shaft arranged parallel to the first shaft, and an output shaft that is integral with the second shaft or connected to rotate integrally therewith. , a planetary gear transmission mechanism that has an input shaft, a planetary gear set, a clutch, and a brake arranged concentrically with the output shaft at one end thereof, and is capable of controlling the rotation ratio between the input shaft and the output shaft in multiple stages. and a first gear and a second gear that mesh with each other and are provided on the first shaft and the input shaft of the planetary gear transmission mechanism, respectively.
A first gear set consisting of gears enables transmission of rotational force between the first shaft and the input shaft of the planetary gear transmission mechanism through the first gear set when engaged, and transmits torque through the first gear set when released. a first clutch that releases the rotational force transmission state between the first shaft of the planetary gear transmission mechanism and the input shaft of the planetary gear transmission mechanism; A second gear set consisting of a third gear and a fourth gear provided on the first shaft so as to mesh with the third gear; a second clutch that enables rotational force to be transmitted between the third gear and the member provided thereon, and that releases the rotational force transmission state between the first shaft and the member via the second gear set when released; Multi-speed transmission.