JPS6088249A - Planetary gear transmission gear - Google Patents

Abstract

PURPOSE:To provide a proper transmission ratio responding to the speed change of a vehicle, by a method wherein, in a device having 3 planetary gear mechanisms between an input and an output shaft, a method of intercoupling the constituting elements of each planetary gear mechanism is devised, and the number of speed shifting steps of a gear row is set to 5 steps. CONSTITUTION:In a planetary gear transmission gear which is constituted such that first-third planetary gear having sun gears S1-S3, carriers PC1-PC3, and ring gears R1-R3, respectively, are situated between an input shaft I and an output shaft O, the input shaft I is coupled to the sun gear S1 and the carrier PC1 through clutches C1 and C2, respectively. The sun gear S2 is located integrally to the input shaft I, and the ring gears R1, R3 and the carriers C2, C3 are situated integrally with the output shaft O. Further, the ring gear R2 and the carrier PC1, the carrier PC1 and the sun gear S3, a case H and the sun gear S1, and the case H and the sun gear S3 are intercoupled through clutches C3, C4, brakes B1, 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) As for the conventional planetary gear transmission, in addition to the 2nd and 3rd speeds, there was also a 4-speed JT planetary gear transmission as shown in 1ryI (U.S. Patent Specification No. 4237749).

However, there is a problem in that 4-speed gears are insufficient in order to respond to continuous changes in vehicle speed and to obtain a gear ratio that is more appropriate from the standpoint of fuel efficiency, rotational transmission efficiency, etc.

(Objective of the Invention) Therefore, an object of the present invention is to increase the number of gears in the gear train to five, and to obtain a gear ratio more suitable for L7 that corresponds to the continuous gear change of the vehicle.

(Structure of the Invention) A planetary gear transmission according to the present invention includes a first planetary gear mechanism provided in a case between a human power shaft and an output shaft, and having a first Zang gear, a first carrier, and a first ring gear; 2'M: planetary gear transmission having a second Zangito, a second carrier, and a second ring gear; a third planetary gear mechanism having a third sun gear, a third carrier, and a third ring gear; In the apparatus, 7, the input shaft and the first sun gear are connected via a first disconnection means, the input shaft and the first carrier are connected via a second disconnection means, and the input shaft and the second sun gear are connected through a second disconnection means. are integrally connected, and the first
A ring gear, a second carrier, and a third ring gear are integrally connected, and the second ring gear and the first carrier are connected to a third ring gear.
the first carrier and the third sun gear are connected via a disconnection means, the third carrier and the output shaft are integrally connected, and the case and the first sun gear are connected via a fourth disconnection means; are connected via a fifth disconnection means, and the case and the third sun gear are connected via a 61i1i connection means.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. Second
Figure a is a diagram showing a first embodiment of a planetary gear transmission according to the present invention.

In the figure, ■ is an input shaft connected to the output shaft of an engine (not shown), and this input shaft I is connected to the first Zangya S in an intermittent manner via the first clutch C (first disconnection means). In addition to being connected, the first Kuratsuji CI
It is also connected via a one-way clutch OC4.

The first sun gear Sl is in external meshing with a first planetary gear P supported by a first ring gear 1-1''C, and this planetary gear Pl is in contact with a first ring gear 1=R.

interlocks internally with Therefore, the first Zang gear S1, the first
The carrier PCI, the first planetary gear P, and the first ring gear R collectively constitute a first planetary gear mechanism. The input shaft I L is connected to the first carrier PCI in a disconnectable manner via a second clutch C2 (second disconnecting means), and is also integrally connected to the second Zang gear S2. The second sun gear S2 externally meshes with a second planetary gear P2 supported by the second carrier P02, and this second planetary gear P2 internally meshes with the second ring gear R2.Therefore, the second sun gear S2, the second carrier pc, , the second planetary gear P2 and the second ring gear R2 constitute a second M star gear mechanism as a whole.
Ring gear R8 is integrally connected to second carrier PC2 and 39th ring gear R3. 3rd ring gear R3
is internally meshed with the third planetary gear P3 supported by the third carrier PC3, and this third planetary gear P is in internal mesh with the third planetary gear P3 supported by the third carrier PC3.
Sun gear S.

externally engages with. Therefore, the third sun gear S1, the third
The carrier PC3, the third planetary gear P3, and the third ring gear R1 constitute a third planetary gear mechanism as a whole. The second ring gear R2 is disconnectably connected to the first carrier PCI via a third clutch C3 (third disconnecting means). Furthermore, the first carrier PCI is connected to the fourth clutch C.
-4 (fourth disconnection means), it is intermittably connected to the third sun gear S3, and also connected in parallel to the fourth clutch C- through the second one-way clutch 7CH OC2. . The first sun gear S is intermittably connected to the case [I] via the first brake B (fifth disconnection means).

The third sun gear S and the case H are the second brake B2.
(sixth disconnection means), and is connected in parallel with the second brake B2 via a third one-way clutch QC. The third carrier 1)C1 and the output shaft 0 are integrally connected.

Each clutch C in the planetary transmission having the above configuration
8 to C'4, each brake B, , B2, and each one-way flange OC1 to OC1 are shown in Attached Table 1. In this Attached Table 1, the 0 mark indicates the operating state, and the no mark indicates the released state. Further, R5, R2, and R3 in Attached Table 1 are expressed as follows.

ρ, - (number of teeth of first sun gear S) 7/(number of teeth of first ring gear R1) R2 - (number of teeth of second sun gear S2) 7/(number of teeth of second ring gear R2) R3 - (number of teeth of second ring gear R2) (Number of teeth of third ring gear R3) / (Number of teeth of third ring gear R3) FIG. A second embodiment is shown, and FIG. 4 shows a third embodiment in which the arrangement and number of clutches and clutches are different from those of the first embodiment. In addition, Attached Table 2 shows the operating status of each clutch, etc. in the third embodiment, and the operation of the third clutch C3 in the fifth gear is unrelated to power transmission, and is intended to restrict unnecessary high-speed rotation of the gear. belongs to.

Although the one-way clutches in the first to third embodiments described above are intended to prevent unnecessary reversal of each gear, they are not necessarily necessary to achieve the object of the present invention, and therefore each one-way clutch is not provided. It may be.

FIG. 5 shows a fourth embodiment. In this fourth embodiment, unlike the first to third embodiments in which a friction clutch was used between the input shaft I and the first sangeet S, a dog clutch D is used instead of the friction clutch. It was there. For this reason, the rotation (torque) when the vehicle moves forward
Transmission efficiency can be improved by 11 degrees.

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

Furthermore, in the second and third embodiments, the degree of freedom in the layout of the device can be increased.

Furthermore, in the fourth embodiment, the rotation (torque) transmission efficiency when the vehicle moves forward can be improved compared to the third embodiment.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing a conventional planetary gear device, FIG. 2 is a schematic diagram showing a first embodiment of a planetary gear device according to the present invention, and FIG. 3 is a schematic diagram showing a second embodiment. 4 is a schematic diagram showing the third embodiment, and FIG. 5 is a partial schematic diagram showing the fourth embodiment. I----1・Input shaft, o-'----Output shaft, H----Case, S, ・---1-・1st sun gear, sz-"'-~2nd sun gear, S , ---1 third sun gear, pc, ---1 first carrier, pc2.-, ,,-2nd carry, pc, ---1 third carrier, R, ---1st ring gear, R2--1 2nd ring gear, R3-- 3rd ring gear, c, --- 1st clutch (first disconnecting means), C2--
-1 second clutch (second disconnection means), c, ---1 third
Clutch (third disconnection means), c-:-----14th clutch (4th disconnection means), Bl---1st brake (5th disconnection means)
tlji connection means), B2--second brake (sixth disconnection means). Patent Applicant Nissan Motor Co., Ltd. Agent J1 Physician Ugagun Part Figure 3 Figure 4 Figure 5

Claims (1)

[Claims] A first planetary gear mechanism is installed in the case between the input shaft and the output shaft, and has a first sun gear, a first carrier, and a first ring gear, and a second planetary gear mechanism has a second sun gear, a second carrier, and a second ring gear. 2312 star gear mechanism and the third
9. In a planetary gear transmission comprising a third planetary gear mechanism having a third carrier and a third ring gear, the input shaft and the first gear are connected via a first disconnecting means. , n; 1 input shaft and a first carrier are connected via a 2111i connection means, the input shaft and a second sun gear are integrally connected, and the first ring gear and the second
A carrier and a third ring gear are integrally connected, the second ring gear and the first carrier are connected via a third connecting means, and the first carrier and the third sun gear are connected through a fourth connecting means. The third carrier and the output shaft are integrally connected, and the case and the first Zang gear are connected to each other by a fifth L.
A planetary float transmission, characterized in that the case and the third sun gear are connected through a fi connection means, and the case and the third sun gear are connected through a sixth disconnection means.