JPS6088251A - Planetary gear transmission gear - Google Patents

Abstract

PURPOSE:To always provide a proper speed ratio and to improve the degree of freedom of a layout, by a method wherein, in a device which is provided between an input and an output shaft with 3 planetary gear mechanisms, a method of intercoupling the constituting element of each planetary gear mechanism is devised and a speed shifting step is set to 5-step. CONSTITUTION:In a planetary gear transmission gear which is constituted such that first-third planetary gear mechanism having sun gears S1-S3, carriers PC1-PC3, and ring gears R1-R3, respectively, are mounted between an input shaft I and an output shaft O, the inputs shaft I is coupled to the sun gear S1 and the ring gear R1 through clutches C1 and C2, respectively. The carrier PC1 and the ring gears R2, R3, and the ring gear R1 and the carrier PC2 are respectively integrally intercoupled, and the carrier PC2 and the sun gear C3, and the input shaft I and the sun gear S2 are intercoupled through clutches C3 and C4, respectively. Further, the carrier PC3 and the output shaft O are integrally intercoupled, and a case H is coupled to the sun gears S2 and S3 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) 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 are insufficient in order to respond to continuous speed changes of the vehicle and to obtain a gear ratio that is more appropriate from the standpoint 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 planetary gear east mechanism that is provided in a case between an input shaft and an output shaft, and has a first sun gear, a first carrier, and a first ring gear, a second sun gear, and a first planetary tooth gear mechanism. a second planetary gear mechanism having two carriers and a second ring gear;
a third planetary gear mechanism including a third Zang gear, a third carrier, and a third ring gear; The shaft and the first ring gear are connected via a second continuation means, the first carrier, the second ring gear and the third ring gear are integrally connected, and the first ring gear and the second carrier are integrally connected. the second carrier and the third sun gear are connected via a disconnection means, the input shaft and the 24th ton gear are connected via a fourth disconnection means, and the third carrier and the output shaft are integrally connected, the second sun gear and the case are connected through a fifth continuation means, and the third sun gear and the case are connected through a sixth disconnection means.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. Second
The figure shows a first embodiment of a planetary gear transmission according to the present invention.

In the figure, ■ is an input shaft connected to an engine output shaft (not shown), and this input shaft r is connected to the first Zang gear SL in an intermittent manner via the first clutch C (first disconnection means). It is also connected to the first sangee-1-S via a disengageable friction clutch M and a first one-way clutch OC, which are arranged in series. The first gear 1-S externally meshes with the first planetary gear P1 supported by the first carrier PC, and the first planetary gear P internally meshes with the first ring gear 16. Therefore, the first Zang gear S1, the first carrier pc, ,
Planetary 4! YaP, and first ring gear R8 are
The first planetary gear mechanism A is configured as a whole. The input shaft I is also disconnectably connected to the first ring gear R1 via a second clutch C2 (second disconnecting means). The first carrier PCI is integrally connected to the second ring gear R2 and the third ring gear R3. The second ring gear R2 is the second planetary gear 1 supported by the second carrier PC2.
12, and this second planetary gear P2
is in external meshing with the second sun gear S2, so the second sun gear S2, the second carrier I) C2, the second planar gear P2, and the first ring gear R2 constitute the second planetary gear mechanism B as a whole. . 2nd carrier PC
2 integrally continues with the first ring gear R2, and is intermittently connected to the third sun gear S3 via a third clutch C3<31st connection means). Further, the second carrier PC2 and the third to eleventh gear S3 are also connected via a second one-way clutch OC2 provided in parallel with the third clutch C3.

The third sun gear S3 is externally meshed with a third planetary gear P3 supported by a third carrier PC3, and this third planetary gear P3 is internally meshed with a third ring gear R3. Therefore, the third Zang gear s3, the third gear (-
PC3, third planetary gear P3, and third ring gear R3 constitute a third planetary gear mechanism C as a whole.

The human power shaft I and the first gear S2 are connected to each other via a fourth clutch (fourth disconnection means), and
The third middle rear PC3 and the output shaft O are integrally connected. The second sun gear S2 and case H are intermittably connected to each other via a first brake B (fifth disconnecting means), and the third sun gear S3 and case 11 are connected to each other via a second brake B2 (sixth disconnecting means). ) are intermittently connected via. In addition, the third Zangear S3 and case l (
It is also connected via a third one-way clutch OC3 installed in parallel with the second brake B2.

Attached Table 1 shows the operating conditions of each clutch Cl-Ca, M, each brake B1, B2, and each one-way clutch oc, to OC3 in the planetary gear transmission having the above configuration. In this Attached Table 1, the O mark indicates an operating state, and the no mark indicates a released state. In addition, R1, R2, and R3 in Attached Table 1 are expressed as follows.

ρ, = (number of teeth of first sun gear S1)/' (number of 11A of first ring gear R2) R2-(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 S3)/(Number of teeth of third ring gear R3) FIG. 3 shows a second embodiment. In the first embodiment, a first one-way clutch OC8 force<G is installed between the input shaft I and the first gear Sl, and the first one-way clutch is disposed in series with a friction clutch M that can be engaged and disconnected. In this case, the first one-way clutch OC3 is connected to the input shaft I and the second one-way clutch OC3.
4 clutches C, I and 1 (interposed in one row, in the planetary gear transmission according to this second embodiment) are connected to the gear S2. The operating status is shown in Attached Table 2.

In addition, the positions of each planetary gear mechanism in the first and second embodiments are necessarily the first, second, and third planetary gear mechanisms A, B,
It is not necessary to arrange them in the order of C, and they may be arranged in any order by adjusting the coupling relationship of each clutch or brake. In addition, each one-way clutch in the first and second embodiments is to prevent unnecessary reversal of each gear, and is not necessarily necessary to achieve the object of the present invention, so each one-way clutch is It may be something that does not exist.

In addition, in order to improve the rotation (torque) transmission efficiency when the vehicle moves forward, a friction clutch (first clutch C,) interposed between the input shaft I and the first sun gear S is replaced. Alternatively, a tongue clutch may be used.

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

Further, in the second embodiment, in addition to the first embodiment, the degree of freedom in layout of the device can be increased.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing a conventional planetary gear transmission, FIG. 2 is a schematic diagram showing a first embodiment of a planetary gear transmission according to the present invention, and FIG. 3 is a schematic diagram showing a second embodiment. It is a skeleton diagram. 1---One-person power shaft, O----1 output shaft, H----1 case, S, ---1st sun gear, S2----1 2nd sun gear, 53--1 3rd sun gear sun gear, pc, ---first carrier, PO2--second carrier, PO2--first third carrier, R8--first ring gear, R2--second ring gear, R3-- ,, - third ring gear, C, - - first clutch (first disconnecting means), C, -
Second clutch (second disconnecting means), C,-----Third clutch (third disconnecting means), C4-----Fourth clutch (fourth disconnecting means), B,---- 1st brake (5th
B2----1 second brake (sixth disconnection means), A~-1---1st planetary gear mechanism, B---2nd planetary gear mechanism, C---1st 3 planetary gear mechanism. Patent applicant: Patent attorney representing Nissan Motor Co., Ltd. Ugagun Partial Attached Table 2 Figure 1

Claims (1)

[Claims] A first ring gear provided in the case between the input shaft and the output shaft, and having a first ring gear, a first carrier, and a first ring gear.
A planetary gear comprising: a planetary gear mechanism; a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear; and a third planetary gear mechanism having a third sun gear, a third carrier, and a third ring gear. In the transmission, the input shaft and a first sun gear are connected via a first disconnecting means, the input shaft and an 11th ring gear are connected via a second connecting means, and the first carrier and a second ring gear are connected via a second connecting means. and a third ring gear, and the first ring gear 4 is integrally connected to the third ring gear.
・The input shaft and the second sun gear are connected integrally with the stopping second carrier, the second carrier and the third sun gear are connected via the 311i connecting means, and the input shaft and the second sun gear are connected via the fourth disconnecting means. The third gear middle rear and the output shaft are integrally connected, the second sun gear and the case are connected via a fifth continuation means, and the third sun gear and the case are connected by a sixth disconnecting means. A planetary gear transmission characterized in that the gears are connected via a planetary gear.