JPS6088252A - Planetary gear transmission gear - Google Patents

Abstract

PURPOSE:To provide a further proper transmission ratio responding to the continuous change in speed of a vehicle, by a method wherein, in a device which is provided between an input and an output shaft with a planetary gear mechanism, a method of intercoupling constituting elements of each planetary gear mechanism is devised, and the number of speed shifting steps is set to 5 steps. CONSTITUTION:In a planetary gear transmission gear which is formed such that first-third planetary gear mechanism having sun gears S1-S3, carriers PC1- PC3, and ring gears R1-R3 are located between an input shaft I and an output shaft O, the sun gears S1, S2 and the carrier PC2 are coupled to the input shaft I through clutches C1-C3, respectively. The ring gear R1 is coupled to the carrier PC2 through a clutch C4, the carrier PC1, and the ring gears R2 and R3 are integrally intercoupled, and the carrier PC2 is coupled to the sun gear S3 through a clutch C5. Further, the sun gears S2 and S3 are coupled to a case H through brakes B1 and B2, respectively, and the carrier PC3 is coupled integrally to the output shaft O.

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) As a conventional planetary gear transmission, in addition to the 2nd and 3rd speeds, there was a 4-speed planetary gear transmission as shown in FIG. 1 (US Pat. No. 4,237,749). ).

However, there is a problem in that four speeds is insufficient in order to respond to continuous speed changes of the vehicle and to obtain a gear ratio that is more appropriate from the standpoints of fuel efficiency, rotational transmission efficiency, and the like.

(Objective of the Invention) Therefore, an object of the present invention is to increase the number of gears of the gear train to 5 speeds to obtain a more suitable gear ratio corresponding to continuous speed changes of the vehicle.

(Structure of the Invention) The present invention provides a first M star gear mechanism that is provided in a case between an input shaft and an output shaft and has a first sun gear, a first carry, and a first ring gear, a second sun gear, a second An 11-gear transmission device comprising: a second planetary gear mechanism having a carrier and a second ring gear; and a third M star gear mechanism having a third scene gear, a third carrier, and a third ring gear; 1 Sangeet and 1st
The input shaft and the second sun gear are connected via a disconnection means, and the input shaft and the second sun gear are connected through the second disconnection means, and the input shaft and the second sun gear are connected through a second disconnection means.
the first ring gear and the second carrier are connected via a fourth intermittent means U1, and the first carrier, the second ring gear and the third ring gear are integrally connected to each other via a third intermittent means. the second carrier and the third sun gear are connected through a fifth connecting means, the second sun gear and the case are connected through a fifth connecting means, and the third sun gear and the case are connected through a fifth connecting means. The third carrier and the output shaft are integrally connected through seven disconnecting means.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. Second
F+ is a diagram showing a first embodiment of a planetary 1'# vehicle transmission according to the present invention.

In the figure, ■ is an input shaft connected to the engine output shaft of diagram I, and this human power shaft l is connected to the first clutch C, (
It is intermittably connected to the first Sankya S via a first disconnecting means (first disconnecting means). The first sun gear S1 is the first carrier r)
The first planetary gear P is externally meshed with the first planetary gear P1 supported by the first ring gear P, which is supported by the first ring gear P1.
? , interlocks internally with . Therefore, the first Zangia S8,
The first carry 1-PC, the first planetary gear l)l, and the first ring gear R1 constitute a first planetary gear mechanism A as a whole. The input shaft I is disconnectably connected to the second sun gear S2 via a second clutch C2 (second disconnecting means), and a tongue clutch is used as the second clutch C2. In addition, the input shaft I is connected to the second middle rear PC2 in an intermittent manner via a third clasp C3 (third disconnection means). The second sun gear S2 is the second carrier PC2
The second planetary gear P2 is externally meshed with a second planetary gear P2 supported by the second ring gear R2, and the second planetary gear P2 is internally meshed with a second ring gear R2. Therefore, the second sun gear s2, the second carrier PC2, the second planetary gear P, and the second ring gear R2 constitute the second idler gear mechanism B as a whole.

The first ring gear 1 is connected to the second carrier Pc2 in an intermittent manner through a fourth clutch C4 (fourth disconnection means), and is connected to the second carrier Pc2 in a parallel manner with the fourth clutch C%.
: Also connected via the first one-way clutch OC1.

The ml carry 1-PC is integrally connected to the second ring gear 4.R2 and the third ring gear R7.

The third ring gear R3 is internally engaged with a third planetary gear P supported by the third carrier 1)c3, and this third planetary gear P3 is externally engaged with a third Zang gear S3. Therefore, the third sun gear S3, the third carrier PC3, the third planetary gear P3, and the third ring gear R1 constitute the third M star gear mechanism C as a whole. The second middle rear PC2 is intermittably connected to the third sangeet S3 via a fifth clutch CS (fifth disconnecting means), and
A second one-way clutch O is connected in parallel with the fifth clutch C9.
It is also connected via c2. The second sun gear s2 is the first
The brake B is intermittably connected to the case H via the brake B (sixth disconnection means). The third sun gear S is intermittably connected to the case H via a second brake B2 (disconnection means), and is also connected in parallel with the second brake B2 via a third one-way clutch OC3. There is. The third middle rear PC3 is integrally connected to the output shaft 0.

The operating status of each of the clutches C0 to C9, each of the brakes B1 and B2, and each of the one-way clutches OC8 to QC in the planetary gear transmission having the above configuration is shown in the attached table. In this attached table, the mark "ζ, 0" indicates the operating state, and no mark indicates the released state.
1.R2 and R3 are expressed as follows.

ρ, = (number of teeth of first sun gear S)/(number of teeth of first ring gear R) ρ2=(number of teeth of second sun gear S2)/(number of teeth of second ring gear R2) R3-(number of teeth of second ring gear R2) (number of teeth of sun gear S)/(number of teeth of third ring gear R3)
As shown in the figure (for collinear charts, please refer to the patent application filed in 1984-17).
(See No. 3603) 1. In the same figure, N, ~N, is the first
NR is the output rotation speed at speed to 5th gear, and NR is the output rotation speed at reverse.

It should be noted that each non-way clutch used in this example is to prevent unnecessary reversal of each gear, and is not necessarily necessary to achieve the purpose of the present invention.
Therefore, there is no one-way clutch.
Good too.

(Effects of the Invention) As explained above, according to the present invention, it is possible to set the number of gears of the gear train to 5 to obtain a more appropriate gear ratio that corresponds to continuous speed changes of the vehicle. .

[Brief explanation of drawings]

Fig. 1 is a schematic diagram showing a conventional planetary gear transmission, Fig. 2 is a schematic diagram showing an embodiment of the planetary gear transmission according to the present invention, and Fig. 3 is a schematic diagram showing a planetary gear according to this embodiment. It is a figure which shows the collinear chart table in the gear train of a transmission. 1--Single power shaft, o----One output shaft, H----Case, S,----1st sun gear, S,----2nd sun gear, s, ----1 Third sun gear, PC, ---1 first carry, pc, ---1 second carrier, pc, ---1 third carrier, R, ----1st ring gear, R2, --- - 2nd ring gear, R, -, , - 3rd ring gear, c, - 1. - 1st clutch (1st intermittent stage), C2 -.
-Second clutch (second disconnection means), C3--13rd clutch (3rd Liyi continuous 1st stage), c-4--14th
Clutch (fourth disconnection means), C5-1 fifth clutch (fifth disconnection means), B, --1.-first brake (61st #
i connection means), B2-----1 second brake (seventh intermittent means), A-----1 first planetary gear mechanism, B--m-2nd M, star gear mechanism, c--m -Third planetary gear mechanism. Patent Applicant Nissan Motor Co., Ltd. Representative Patent Attorney Agagun Part Figure 1 Figure 2 Figure 3 NIz Input Shaft @Koku 4 Mystery

Claims (1)

[Claims] The first
a first planetary gear mechanism having a sun gear, a first carrier and a first +J song; a second planetary gear mechanism having a second sun gear, a second carrier and a second ring gear; a third sun gear, a third carrier and a third ring gear; A planetary gear transmission comprising: a third planetary gear mechanism with a zero connection; and a third planetary gear mechanism with a zero connection, wherein the input shaft and the first sun gear are connected via a first disconnection means, and the input shaft and the second sun gear are connected with a second disconnection means. connecting the input shaft and the second carrier via a third disconnection means; n; 1 connecting the first ring gear and the second carrier via a fourth disconnection means; The first carrier, the second ring gear, and the third ring gear are integrally connected, and the second carrier and the third sun gear are connected to the fifth ring gear.
the second sun gear and the case are connected via a sixth disconnection means, the third sun gear and the case are connected via a seventh disconnection means, and the third sun gear and the case are connected via a seventh disconnection means; A planetary gear transmission characterized by integrally connecting an output shaft.