JP2956172B2 - Planetary gear train of automatic transmission - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear train of an automatic transmission, and more particularly, to an automatic transmission having an input shaft and an output shaft arranged in parallel and having two planetary gear sets. Planetary gear train.

2. Description of the Related Art As a conventional planetary gear train of an automatic transmission, there is one described in, for example, Japanese Patent Application Laid-Open No. 60-188646. This conventional example includes two planetary gear sets, five clutches, two brakes, three one-way clutches, two gear sets, and one countershaft to obtain a forward five-speed gear ratio. Things.

[Problems to be solved by the invention]

However, according to the prior art, since each component is arranged on one axis, there is a problem that the length of the planetary gear train in the axial direction becomes large. There is a problem that it is difficult to apply to an automatic transmission.

The present invention has been made in view of the problems of the prior art, and arranges an input shaft and an output shaft of a planetary gear train in parallel and arranges components on an input shaft and an output shaft. The purpose of the present invention is to reduce the length of the planetary gear train by disposing them separately.

[Means for solving the problem]

The planetary gear train of the automatic transmission according to the present invention has an input shaft and an output shaft arranged in parallel, a first planetary gear set including a first sun gear, a first ring gear and a first pinion carrier, a second sun gear, and a second sun gear. A second planetary gear set including a two-ring gear and a second pinion carrier is provided on the input shaft, and has two gear sets provided on the input shaft and the output shaft by meshing with each other.

Further, the input shaft is connected to the first ring gear, and the first sun gear is connected to the second sun gear via the parallel first clutch and first one-way clutch.

A first pinion carrier, a first gear set, a second one-way clutch and a second clutch arranged on the output shaft in series with each other and in series with each other, and the second one-way clutch in series with the first gear set. And a third clutch arranged in parallel with the second clutch and disposed on the output shaft and connected to the output shaft.

Further, a fourth clutch integrating the first planetary gear set is disposed on the first planetary gear set, the second sun gear can be fixed to the case via the first brake, and the second pinion carrier is connected to a second parallel pinion carrier. It can be fixed to the case via a brake and a third one-way clutch, and is connected to a first sun gear or a first pinion carrier via a fifth clutch, and the second ring gear is connected to the output shaft via a second gear set. Connected.

[Action]

The planetary gear train of the automatic transmission according to the present invention includes first to fifth clutches (C1 to 5), first and second brakes (B1, B2),
By selectively operating the first to third one-way clutches (OWC1 to 3) as indicated by a circle in FIG. 2 to be described later, five forward speeds in the D range and four forward speeds in the L range are achieved. , R range.

Here, by operating the circles described in the "3 '" column at the bottom of FIG. 2, six forward speeds can be changed.

Further, in the present invention, since the second and third clutches and the second one-way clutch are disposed on the output shaft, no space is required for these elements on the input shaft.

〔Example〕

 Next, an embodiment of the present invention will be described.

First Embodiment FIGS. 1 to 3 show a first embodiment. The planetary gear train of this automatic transmission includes a first planetary gear set G1 and a second planetary gear set G.
2, input shaft I, output shaft O, first to fifth clutches C1 to C5,
It has first and second brakes B1, B2, first to third one-way clutches OWC to OWC3, first and second gear sets i1, i2, and the input shaft I and the output shaft O are arranged in parallel. Have been.

The first planetary gear set G1 has a first sun gear S1, a first ring gear R1, and a first pinion carrier PC1 that supports a first pinion P1 that meshes with them at the same time. Further, the second planetary gear set G2 also includes a second sun gear S2, a second ring gear R2.
And a second pinion carrier PC2 that supports a second pinion P2 that meshes with them at the same time. Both planetary gear sets G1 and G2 are arranged on the input shaft I.

Each of the first and second gear sets i1 and i2 is configured such that gears rotatably arranged on the input shaft I and the output shaft O are meshed with each other.

The input shaft I is directly connected to the first ring gear R1, and the first sun gear S1 is connected to the second sun gear S2 via the parallel first clutch C1 and first one-way clutch OWC1.

The first pinion carrier PC1 is arranged on the output shaft O in series with the first gear set i1 and connected to the output shaft O via the second one-way clutch OWC2 and the second clutch C2 which are serially connected to each other. . The second one-way clutch in series
A third clutch C3 arranged on the output shaft O is arranged in parallel with the OWC2 and the second clutch C2.

The first planetary gear set has a fourth clutch integrated with it.
C4 is interposed between the first sun gear S1 and the first ring gear R1, while the second sun gear S2 is fixed to the case via the first brake B1, and the second pinion carrier PC2 is also And a second brake B2 and a third one-way clutch OWC3 arranged in parallel with each other. The second pinion carrier PC2 is connected to the first pinion carrier PC1 via a fifth clutch C5.

The second ring gear R2 is connected to the output shaft O via a second gear set i2.
It is connected to.

In the planetary gear train of the automatic transmission having the above configuration, each clutch, brake, and one-way clutch are operated in a combination as shown in FIG. It is possible to obtain the speed ratios of the four forward speeds in the range and the R range. The circles in the figure are operating components, of which [○]
The mark is an element that transmits power only during engine braking, and the mark (（) is an element that is not related to power transmission.

In addition, by operating the circle marked in the lowermost column indicated by “3 ′” in FIG. 2, six forward speeds can be shifted in the D range.

The gear ratios in the D range and the R range are as shown in FIG. Where α1 is the first sun gear S1
Α2 is the ratio of the number of teeth between the second sun gear S2 and the second ring gear R2, and i1 is the first number of teeth between the second ring gear R2 and the first ring gear R1.
This is the gear ratio of the gear set i1, and i2 is the gear ratio of the second gear set i2. When these gear ratios are combined with the three modes shown in FIG. 3, the gear ratio shown in FIG. 3 can be obtained.

The gear ratio in the case of the "3 '" column in FIG. 2 is also shown in the "3'" column in FIG. When the forward range is set to six speeds in the D range using this speed ratio, the speed ratio in the "3 '" column is the fourth speed, and the fourth and fifth speeds in FIG. Becomes In this case, the α1,
It can be seen that even when the numerical values of α2, i1 and i2 are changed, the ratio (interstage ratio) between adjacent speed ratios in the first to sixth speeds is appropriately matched. Therefore, it can be understood that the degree of freedom in setting each speed ratio is large.

Here, in the D range, the first and third clutches C
1 and C3, the second brake B2 remains released, and the second clutch C2 remains engaged, so that there are few switching elements that operate when switching between each gear in the D range, and Adjustment is easy.

Further, since the second and third clutches C2 and C3 and the second one-way clutch OWC2 are arranged on the output shaft O, the number of components on the input shaft I is reduced by the amount of these components. For this reason, the distance on the input axis I where each element is arranged is reduced,
As a result, the length of the planetary gear train is reduced, which makes it suitable as a transmission for a transverse engine.

(Second Embodiment) FIG. 4 shows a second embodiment. In this embodiment, a first planetary gear set G1 is arranged on the side of a rotary drive source (not shown), and this and a second planetary gear set G2. Between the first gear set i1
This is an example in which a second gear set i2 and a second gear set i2 are arranged. In the first embodiment, the second pinion carrier PC2 is connected to the first pinion carrier PC1 via the fifth clutch. However, the second pinion carrier PC2 of this embodiment is connected to the first pinion carrier PC2 via the fifth clutch. It is connected to sun gear S1. The other structure is the same as that of the first embodiment, and the operation is the same as that of the first embodiment described above with reference to FIGS.

(Third Embodiment) FIG. 5 shows a third embodiment. In this embodiment, the relative position of each element is the same as that of the second embodiment (FIG. 4), while the connection of each element is This is an example similar to the first embodiment (FIG. 1). Therefore, the operation is the same as that of the first embodiment described above with reference to FIGS.

(Fourth Embodiment) FIG. 6 shows a fourth embodiment. In this embodiment, the relative position of each element and the connection of each element are described in the second embodiment (fourth embodiment).
This is an example in which the first planetary gear set G1 and the fourth clutch C4 are incorporated in the torque converter TC in addition to the configuration shown in FIG.

That is, the first ring gear R1 of the second embodiment is connected to the turbine runner T of the torque converter TC, the input shaft is connected to the pump impeller PO, and a lock is provided between the turbine runner T and the pump impeller PO. This is with an up clutch LC interposed. Thus, in this embodiment, the trick converter TC is interposed between the input shaft I and the first ring gear.

Therefore, in this embodiment, the input from the input shaft I is transmitted to the first ring gear R1 via the torque converter TC, and other configurations are the same as those of the second embodiment.
The operation is the same as that of the first embodiment described above with reference to FIGS.

〔The invention's effect〕

As described above, in the present invention, up to six forward gears can be obtained by the two planetary gear sets, and the input shaft and the output shaft of the planetary gear train are arranged in parallel. Since the components are separately arranged on the input shaft and the output shaft, the total length of the planetary gear train can be shortened. The effect is that it can be applied.

[Brief description of the drawings]

1 is an explanatory view showing a planetary gear train of a first embodiment, FIG. 2 is an explanatory view showing a combination of members that operate at each shift speed of the planetary gear train of FIG. 1, and FIG. 3 is FIG. FIG. 4 is an explanatory diagram showing a planetary gear train of the second embodiment, FIG. 5 is an explanatory diagram showing a planetary gear train of the third embodiment, and FIG. It is explanatory drawing which shows the planetary gear train of 4th Example. I: input shaft, O: output shaft, G1: first planetary gear set,
G2 second planetary gear set, S1 first sun gear, S2 second sun gear, R1 first ring gear, R2 second ring gear, PC1 first pinion carrier, PC2 second Pinion carrier, C1 to C5 ... first to fifth clutches, B1, B2
...... First and second brakes, OWC1 to OWC3 ... First to third one-way clutches, i1, i2 ... First and second gear sets.

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-57-173639 (JP, A) JP-A-62-249054 (JP, A) JP-A-62-177337 (JP, A) JP-A-60-1985 23657 (JP, A) JP-A-59-113346 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 3/44-3/78

Claims (1)

(57) [Claims] An input shaft and an output shaft are arranged in parallel, a first planetary gear set including a first sun gear, a first ring gear and a first pinion carrier, and a second sun gear, a second ring gear and a second pinion carrier. A planetary gear train having two gear sets provided on the input shaft and on the output shaft, respectively, provided on the input shaft and a second planetary gear set comprising The first sun gear is connected to the second sun gear through a parallel first clutch and a first one-way clutch, and the first pinion carrier is connected to the first ring gear.
A gear set, a second one-way clutch and a second clutch arranged on the output shaft in series with each other and in series with each other, and in parallel with the second one-way clutch and the second clutch in series with the first gear set. And a fourth clutch integrated with the output shaft, which is connected to the output shaft via a third clutch disposed on the output shaft, and the first planetary gear set, and a second sun gear is connected via the first brake. Can be fixed to the case,
The second pinion carrier can be fixed to the case via a mutually parallel second brake and a third one-way clutch. The second pinion carrier can be connected to the first sun gear or the first pinion carrier via a fifth clutch. Is connected to the output shaft via a second gear set.