JPS60188646A - Planetary gear transmission - Google Patents

Abstract

PURPOSE:To reduce a planetary gear transmission to a compact size and to increase the number of transmission steps by inserting speed change means between a planetary gear mechanism and an output shaft. CONSTITUTION:A transmission mechanism H forming speed change means comprises the first gear G1 integrally coupled to the first pinion carrier PC1, the second free gear F2 integral with the first free gear F1 engaged with the first gear G1, and the second gear G2 engaged with the second free gear F2 and integrally coupled to an output shaft O. The first and second free gears F1, F2 are integrally formed on an auxiliary shaft A disposed parallel to an input shaft 1 and the output shaft O. The second sun gear S2 can be fixed to a stationary portion K by the first brake B1, and the second pinion carrier PC2 can be fixed to the stationary portion K by the second brake B2. The stationary portion K and the second pinion carrier PC3 are coupled to each other through a one-way clutch OC.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a planetary gear transmission used in automatic transmissions of automobiles, etc., and particularly to a device using two sets of planetary gear mechanisms.

[Prior art]

As a conventional planetary gear transmission using two sets of planetary gear mechanisms, there is, for example, a four-speed planetary gear transmission described in U.S. Pat. No. 4,237,749, a diagram of which is shown in FIG. show.

[Problems with conventional technology]

However, such conventional planetary gear transmissions have a structure that can only provide 4 gears, so from the standpoint of fuel efficiency and rotational transmission efficiency, it is difficult to respond to continuous speed changes of the vehicle. However, there was a problem in that a gear ratio more suitable than that of the previous model could not be obtained, and the number of gears in 4th gear was small.

[Purpose of the invention]

This invention was made by focusing on such conventional problems, and by inserting a speed change means such as a speed change gear between the planetary gear mechanism and the output shaft, it is possible to change gears with a simple and compact structure. The purpose of this system is to increase the number of gears in the train compared to the number of gears obtained with a planetary gear mechanism to obtain a gear ratio more suitable for responding to continuous speed changes of the vehicle.

[Structure of the invention]

Accordingly, the present invention includes a first planetary gear mechanism and a second planetary gear mechanism provided between an input shaft and an output shaft, and the first planetary gear mechanism includes a first sun gear and a first interface. The second planetary gear mechanism has a null gear and a first pinion carrier, and the second planetary gear mechanism has a second sun gear, a second internal gear, and a second pinion carrier, and combines these elements to obtain a plurality of speed ratios, The pinion carrier of one of the first and second planetary gear mechanisms can be connected to the output shaft, and the internal gear of the other planetary gear mechanism can be connected to the output shaft, and The pinion carrier and the output shaft of one planetary gear mechanism are related to a planetary gear transmission that can be connected via a transmission means.

〔Example〕

The present invention will be explained below based on illustrated embodiments.

FIG. 2 is a diagram showing a first embodiment of a planetary gear transmission according to the present invention.

First, to explain the configuration, ■ in the figure is an input shaft connected to the output shaft of an engine (not shown), and this input shaft ■ is connected to the first clutch CI and the first one-way clutch OCI.
The first internal gear R1 is connected in series with the first internal gear R1, and the first internal gear It is intermittently connected to R1. Furthermore, the input shaft I is intermittably connected to the first sun gear Sl via a third clutch C3.

The first sun gear 31 externally meshes with a first planetary gear PI rotatably supported by a first pinion carrier PCI, and the first planetary gear PI internally meshes with a first internal gear R1.

Therefore, the first sun gear 31 and the first planetary gear PI
, the first pinion carrier Pcl, and the first internal gear R1 constitute a first planetary gear mechanism X as a whole.

Further, the first sun gear Sl is intermittently connected to the second pinion carrier PC2 via the fourth clutch c4, and therefore the input shaft 1 and the second pinion carrier PC2 are
The third clutch c3 and the fourth clutch C4 are intermittably connected to each other. Furthermore, the first sun gear Sl is intermittently connected to the second sun gear S2 via a fifth clutch C5, and also via a second one-way clutch OC2 provided in parallel with the fifth clutch C5. It is connected to second sun gear S2. Therefore, the input shaft I and the second sun gear s2 are intermittably connected via the third clutch c3, the fourth clutch C4, and the fifth clutch c5.

The second sun gear S2 externally meshes with a second planetary gear P2 rotatably supported by a second pinion carrier PC2, and the second planetary gear P2 internally meshes with a second internal gear R2. Therefore, the second sun gear S
2, the second planetary gear P2, the second pinion carrier PC2, and the second internal gear R2 constitute a second planetary gear mechanism Y as a whole.

The second internal gear R2 is integrally connected to the output shaft 0. Further, the output shaft 0 is connected to a first pinion carrier P via a gear transmission mechanism H, which is a specific example of a transmission means.
Always connected to CI.

The gear transmission mechanism H includes a first gear Gl integrally connected to a first pinion carrier Pcl, and a first gear Gl.
A first free gear Fl that meshes with the first free gear Fl, a second free gear F2 that is integral with the first free gear Fl, and a second free gear F2 that meshes with the second free gear F2 and is integrally connected to the output shaft O.
It consists of gear G2. The first and second free gears FitF2 are integrally formed on a sub-shaft A that is provided parallel to the input shaft I and the output shaft 0.

The second sun gear S2 can be fixed to a stationary part K such as a casing by a first brake Bl, and the second pinion carrier PC2 can also be fixed to a stationary part K by a second brake B2, This stationary part is also connected to the second pinion carrier PC2 via a third one-way clutch OC3, which is provided in parallel with the second brake B2.

Each clutch CI of the planetary gear transmission having the above configuration
, C2, C3, C4, Cs, each brake Bl, B2, and each one-way clutch OCt.

By selectively operating OC2 and OC3 in combination as shown in FIG. 3, five forward speeds and one reverse speed can be obtained as shown in the same figure.

In FIG. 3, O marks indicate operating states, and no marks indicate non-operating (released) states. Also, in the same figure,
ρl is the reduction ratio of the first planetary gear mechanism X, ρ2 is the reduction ratio of the second planetary gear mechanism Y, i is the reduction ratio of the gear transmission mechanism H, and these reduction ratios ρl, ρ2, and i are as follows. It's looked like this.

ρ1=(Number of teeth of first sun gear 31)/(Number of teeth of first internal gear R1) ρ2=(Number of teeth of second sun gear S2)/(Number of teeth of second internal gear R2) i=(Number of teeth of second internal gear R2) Number of teeth of 1st free gear Fl) x (Number of teeth of 2nd gear G2)/(Number of teeth of 1st gear Gl) x (2nd free gear F
As is clear from Fig. 3, by adding and combining two sets (four gears) of the two sets of planetary gear mechanisms, the number of gears can be set to five. I can do it. Moreover, since two sets of planetary gear mechanisms are required, the length between the input shaft (■) and the output shaft (O) can be made shorter than that of conventional systems. This is convenient for transaxles.

FIG. 4 shows a second embodiment of the invention.

In this embodiment, the sub-shaft A in the first embodiment is replaced by the output shaft O.

Each clutch C1, Cz, C3, C4, C5, each brake B1 . of the planetary gear transmission according to the second embodiment. B2
and each one-way clutch OCI.

The operations of OC2 and OCa are similar to those in the embodiment shown in FIG. 3, and by selectively operating them in such a combination, a gear ratio as shown in FIG. 5 can be obtained. In FIG. 5, the reduction ratio 11+'2 is determined as follows.

il - (number of teeth of first gear Q7)/ (Number of teeth of first free gear Fl) 12=(number of teeth of second free gear F2/ (Number of teeth of second gear G2) Incidentally, the reduction ratios ρl and ρ2 are the same as those in the above embodiment.

In this embodiment, the subshaft provided parallel to the output shaft (■) was used as the output shaft O, so that the length of the input shaft of this planetary gear transmission in the axial direction was equal to that of the three sets of conventional planetary gear mechanisms. It can be significantly shorter than the conventional one, and therefore, there is a great advantage especially when the present planetary gear transmission is used in a transversely mounted engine of a front-wheel drive vehicle.

FIG. 6 shows a third embodiment of the invention.

In this embodiment, the second clutch C2 of the first embodiment shown in FIG. 2 is connected to the first pinion carrier PCI and the output shaft O.
A second one-way clutch OC2 is provided in parallel with the second clutch C2. The other configurations and operations are similar to those of the same embodiment, and similar effects can be obtained by configuring in this way.

Note that the positions of the planetary gear mechanisms in the first, second, and third embodiments are not necessarily the same as those of the first, second, and third planetary gear mechanisms.
It is not necessary to arrange them in the order of Y, and the coupling relationship of each clutch or brake may be adjusted and arranged on the opposite side. In addition, each one-way clutch in the first, second, and third embodiments is for restricting unnecessary reversal of each gear, and is not necessarily necessary for achieving the object of the present invention. It may be one without a one-way clutch. Further, as the speed change means, various speed change transmission mechanisms such as a chain transmission mechanism and a V-belt transmission mechanism can be employed.

〔Effect of the invention〕

As explained above, in this invention, the structure is such that a speed change means such as a gear transmission mechanism is inserted between the planetary gear mechanism and the output shaft, so it is possible to use a simple structure while using two conventional planetary gear mechanisms. The number of gear stages of the gear train can be increased compared to the number of gear stages obtained with the two sets of planetary gear mechanisms.

Therefore, it is possible to obtain a more suitable transmission ratio (M) corresponding to continuous speed changes of the vehicle.

Moreover, since only two sets of planetary gear mechanisms are required,
The axial length of the input shaft and output shaft can be shortened,
Another effect is that the degree of freedom in layout of this planetary gear transmission and other devices can be increased.

In addition, in an embodiment in which the output shaft is used as a sub-shaft of the transmission means, the layout is suitable for use in a horizontal automatic transaxle.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram showing a gear train of a conventional planetary gear transmission, FIG. 2 is a schematic diagram showing a gear train according to an embodiment of the present invention, and FIG. 3 is a diagram of the planetary gear shown in FIG. 2. A diagram showing combinations of operating elements of the transmission and their gear ratios; FIG. 4 is a schematic diagram showing a gear train according to a second embodiment of the present invention;
FIG. 5 is a chart showing the gear ratio of the planetary gear transmission shown in FIG. 4, and FIG. 6 is a schematic diagram showing a gear train according to a third embodiment of the present invention. ■・・・Input axis, 0・・・Output axis, X...
...First planetary gear mechanism, Y...Second planetary gear mechanism, 31...First sun gear, S2...
...Second sun gear, PCI...First pinion carrier, PC2...Second pinion carrier, R
1...First internal gear 4..., R2...
...Second internal gear, C1...First clutch, C2...Second clutch, C3...
・Third clutch, C4...Fourth clutch, C5
...5th clutch, B, ...1st brake, B2...2nd brake, H...
Gear transmission mechanism (transmission means), Gl...first gear, G2...second gear, Fl...first free gear, F2...second Free gear, A...
...Secondary shaft, K...Stationary part Fig. 4 Fig. 5 Fig. 6

Claims (1)

[Scope of Claims] (11) A first planetary gear mechanism and a first planetary gear mechanism are provided between a human power shaft and an output shaft, and the first planetary gear mechanism includes a first sun gear, a first planetary gear mechanism, and a first planetary gear mechanism. the second planetary gear mechanism has a null gear and a first pinion carrier;
It has a sun gear, a second internal gear, and a second binion carrier, and these elements are combined to obtain a plurality of transmission ratios, and the binion carrier of one of the planetary gear mechanisms of the first and second planetary gear mechanisms is The output shaft can be connected to the output shaft, and the internal gear of the other planetary gear mechanism can be connected to the output shaft, and the binion carrier of the one planetary gear mechanism and the output shaft can be connected via a transmission means. A planetary gear transmission characterized by: (2) The planetary gear transmission according to claim 1, wherein the output shaft is a subshaft of the transmission means provided parallel to the input shaft.