JPS6088250A - Planetary gear transmission gear - Google Patents

Abstract

PURPOSE:To reduce the magnitude of the number of revolutions produced at some member, by a method wherein, in a device which is provided between an input and an output shaft with 2 planetary gear mechanisms, an arranging method, such as disconnecting means, for a plurality of clutches and brakes is devised. CONSTITUTION:In a planetary gear transmission gear which is sonstituted such that first and second planetaly gear mechanism, having sun gears S1 and S2, carriers PC1 and PC2, and ring gears R1 and R2, respectively, are located between an input shaft I and an output shaft O, the input shaft I is coupled to the sun gear S1 through a clutch C1. The carrier PC1 and the ring gear R2 are coupled integrally with the output shaft O, the input shaft I is coupled to the sun gear S2 and the carrier PC2 through clutches C2 and C3, respectively, and the ring gear R1 and the carrier PC2 are intercoupled through a clutch C4. Further, a case H is coupled to the sun gear S2 and the carrier PC2 through brakes B1 and B2, respectively.

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 and the like.

(Prior Art) A conventional planetary gear transmission is shown in FIG. 1 (US Pat. No. 4,237,749).

A so-called collinear chart showing the number of revolutions of each gear, carrier, etc. in such a gear train is shown in FIG. 2. ■ to ■ in the same figure indicate 1st to 4th forward speeds.
Corresponding to the speed and reverse ranges, these straight lines are Sl (
1st sun gear), S2 (2nd sun gear), PC, (1st
Each intersection point that intersects with the vertical axis of carrier), PC2 (second carrier), R1 (first ring gear), R2 (second ring gear), etc. represents the rotation speed of each member in each range. In particular, the intersection of PC, and R2 with the vertical axis represents the output rotational speed (N l - N'4, NR) in each range (reference specification for collinear chart, Japanese Patent Application No. 1983). -173
No. 603).

However, as can be seen from the figure, the straight line
S, (the first Zang gear) exhibits a very high rotational speed Nma, which is a source of noise and reduces the durability of the gear bearing.

(Purpose of the invention) Therefore, the present invention provides the following advantages:
The purpose is to reduce the maximum rotational speed that occurs in any member of the device.

(Structure of the Invention) A planetary gear transmission according to the present invention includes a first planetary gear mechanism provided in a case between an input shaft and an output shaft, and having a first sun gear, a first carrier, and a first ring gear; a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear; A first carrier, a second ring gear, and an output shaft are integrally connected, the input shaft and a second sun gear are connected via a second disconnection means, and the input shaft and the second carrier are connected via a third disconnection means. the first ring gear and the second carrier are connected through a fourth connection means, the case and the second gear are connected through a fourth connection means, and the case and the second carrier are connected through a fourth connection means. are connected via the sixth disconnection means.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. Third
The figure shows a first embodiment of the present invention.

In the figure, I is an input shaft connected to an engine output shaft (not shown), and this input shaft I is connected to the first clutch C,
1g is connected to the first Zangya S via an intermittent means (disconnection means). 1st sun gear S, 1st carrier PC8
The first planetary gear P is externally meshed with a first planetary gear P supported by the ring gear R8, and the first planetary gear P is internally meshed with a ring gear R8. Therefore, the first sun gear S8, the first carrier p
c., first planetary gear P.

and the first ring gear R8 constitute a first planetary gear mechanism as a whole. The first carrier 1>C3 is integrally connected to the second ring gear R3 and the output shaft 0. Second
Ring gear R2 is internally meshed with a second planetary gear P2 supported by second carrier PC2, and this second planetary gear P2 is externally meshed with second sun gear S2. Therefore, the second sun gear S2, the second carrier 1)C2, the second
The planetary gear set P2 and the second ring gear R7 constitute a second planetary float mechanism as a whole. The input shaft I and the second Zang gear S2 are connected to the second clutch C2 (second disconnecting means)
It is connected intermittently via the input shaft! and the second carrier PC2 are intermittably connected via a third clutch C1 (third disconnection means).

The first ring gear R1 and the second carrier pc, .
They are connected in an intermittent manner via a clutch C'4 (fourth disconnecting means), and are also connected via a first one-way clutch OC1 in parallel with the fourth clutch C4. The second sun gear S2 is intermittably connected to the case H via the first brake B (fifth disconnection means). Second
The carrier PC2 and the case H are connected in an intermittent manner via a second brake B2 (sixth disconnection means), and a second one-way clutch OC2 is also connected in parallel with the second brake B2.

A collinear chart for such a gear train is shown in FIG. 4. In the same figure, the straight line Φ~■ indicates the forward speed 1st~4th
It corresponds to the speed and reverse ranges, and each clutch C8, C2, C3, C'4, each brake B, , B2, and one-way clutch OC, 0 in each range.
The operating status of C2 is shown in the attached table. In addition, in the attached table, the O mark indicates that the product is in operation, and the no mark indicates that it is released. In addition, in the attached table, ρ1-(number of teeth of first sun gear S)/(number of teeth of first ring gear R8), ρ2=(number of teeth of second sun gear S2)/(number of teeth of second ring gear R2). be.

In the 4th forward speed range, the first brake B is connected and activated to bring the rotational speed of the second sun gear S2 to zero, and the third clutch C3 is connected and activated to rotate the second carrier PC2 at the same time as the input shaft ■. , an output rotational speed N-4 is obtained from the second ring gear R7, that is, the output shaft 0. At this time, in the first planetary gear, the first carrier PC4 rotates at the same rotation speed as the output shaft O, and the first sun gear S and the first clutch C1
Since it is connected and operating, it rotates at the same rotation speed as human power shaft I. The first ring gear R is released from the fourth clutch C4 and the first one-way clutch OC, and due to the rotation of the first sun gear S and first carrier PC, the first ring gear R is aligned with the vertical axis of R8 shown in FIG. It rotates at the rotation speed N max indicated by the intersection with the gear train, which is the maximum rotation speed in this gear train. In this way, the maximum rotation that can be achieved by the device is achieved by releasing the first ring gear R1 from the fourth clutch notch C4 and the first one-way clutch OC1 and connecting the first sun gear S to the input shaft I by the first clutch CI. Number N
may be the fourth clutch C-4 and the first clutch C-4.
Maximum rotation speed NL in the device that occurs in the first sun gear S when 1 is released.
much smaller than

FIG. 5 shows a second embodiment. In this example,
Although the external structure appears to be different from the first embodiment, the positions of the first planetary gear mechanism and the second planetary gear mechanism are simply swapped left and right in the figure to adjust the positional relationship of the clutch, brake, etc. The substantial configuration is exactly the same as the first one, and the operation status of each part in the attached table and the collinear chart shown in FIG. 4 can be used as they are.

FIG. 6 shows a third embodiment. In this embodiment, in the first and second embodiments, the input shaft ■ and the sun gear S
, a dog clutch D is used between the human power shaft (2) and the sun gear S1 or S2, unlike the case where a friction clutch G is used between the bsc and S2. Therefore, it is possible to improve the rotation (torque) transmission efficiency when the vehicle moves forward.

It should be noted that each one-way clutch used in the first to third embodiments is to restrict unnecessary reversal of each gear, and is not necessarily necessary to achieve the IN objective of the present invention. It may be one without a one-way clutch.

(Effects of the Invention) As described above, according to the present invention, by changing the arrangement of each disconnection means, etc., without impairing the function of the device, the maximum rotational speed generated in any member of the device can be achieved. can be reduced in size. This makes it possible to eliminate noise sources caused by high-speed rotation of gears in a vehicle and improve the durability of gear bearings.

In addition, in the second embodiment, the device layout"
The second degree of freedom can be increased.

Further, in the third embodiment, it is possible to improve the J ratio of rotation (torque) transmission when the vehicle moves forward.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram showing a conventional planetary gear transmission, FIG. 2 is a collinear chart for the planetary gear transmission shown in FIG. 1, and FIG. 3 is a planetary gear transmission according to the present invention. FIG. 4 is a diagram showing a collinear diagram of the planetary gear transmission shown in FIG. 3, and FIG.
FIG. 6 is a partial schematic diagram showing the third embodiment. 1--One-person power shaft, 0--1-Output shaft, H---1--Case, S, ----1 first sun gear, S2---1 second sun gear, pc, ----1 First carrier, PC2-----second carrier, R,------first ring gear, R2-----second ring gear, C,-=-first clutch (first disconnecting means), C2 ---
- Second clutch (second engagement means), C3 - Third clutch (third engagement means), C-4 - - Fourth clutch (fourth engagement means), B, ---- One 1st brake (5th
B2--second brake (sixth intermittent means). Patent Applicant Nissan Motor Co., Ltd. Patent Attorney Patent Attorney Agagun Part I - Figures in parentheses are power chairs j1-, familiar East Fig. 1 l Fig. 3 Fig. 2 SL Fig. 4 I N, - Figure 5, Figure 6, Figure 6

Claims (1)

[Claims] A first gear provided in the case between the input shaft and the output shaft, and having a first sun gear, a first carrier, and a first ring gear.
In a planetary gear transmission including a planetary gear mechanism and a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring, a first disconnecting means connects the input shaft and the first sun gear. the first carrier, the second ring gear, and the output shaft are integrally connected, the input shaft and the second sun gear are connected via the 211i connection means, and the input shaft and the second ．． The first ring gear and the second carrier are connected to each other via a third disconnecting means, and the first ring gear and the second carrier are connected to each other through a fourth disconnecting means.
A planetary gear, characterized in that the case and the second sun gear are connected through a fifth disconnection means, and the case and the second carrier are connected through a sixth disconnection means. gearbox.