JPS6249054A - Automatic transmission for vehicle - Google Patents

Abstract

PURPOSE:To enable increase of the number of stages as the length of a shaft is decreased, by a method wherein a planetary gear type transmission mechanism is situated in power transmission routes proportioned to plural gear trains, the gear ratio of at least one gear train is set for speed increase. CONSTITUTION:Through control of a clutch, torque of an input shaft is transmitted through a first gear train G1, a first shaft 2A, a planetary gear type transmission mechanism AT, and a second shaft 2B. Further, the torque is transmitted through a second gear train G2 and the transmission mechanism AT. The gear ratio of the second gear train G2 is set to a value higher than that of the first gear train G1, namely, is set so as to be increased in a speed. This enables increase of the number of stages through provision of overdrive as the whole length of a shaft is decreased.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an automatic transmission for a vehicle using a planetary gear type transmission mechanism.

(Prior art) Automatic transmissions for vehicles generally use a planetary gear type transmission mechanism connected to the engine output shaft via a torque converter.This M star gear type transmission a4
As for R, there are many three-speed transmissions such as Simpson type or Ravigneau type, which generally have two sets of planetary gears.
Two-speed gears are also used in light vehicles.

Incidentally, in recent years, automatic transmissions for vehicles have been increasingly equipped with multiple gears, particularly overdrive gears, from the viewpoint of fuel efficiency, noise reduction, and the like. Therefore, in order to increase the number of gears while still using the conventionally used planetary gear type transmission mechanism, the trapping planetary gear for configuring the overdrive gear is replaced with a conventional torque converter, for example, in three gears. Some devices have appeared that are further interposed between the main planetary gear type transmission mechanism and the main planetary gear type transmission mechanism.

On the other hand, in recent years, there have been an increase in the number of FF cars (front engine - front tri-life cars) and mid-engine cars that have horizontally mounted engines. It is required that the shaft length of automatic transmissions be made as short as possible.

From this point of view, it has been proposed that an auxiliary planetary gear for an overdrive gear is provided in parallel with, for example, a three-speed main planetary gear type transmission mechanism (Japanese Patent Laid-Open No. 59-133852). (see publication).

(Problems to be Solved by the Invention) However, as described in the above publication, if an auxiliary planetary gear is used in addition to the conventional main planetary gear type transmission mechanism, the structure of the planetary gear itself is quite large. Since this is complicated and unfavorable in terms of mechanical efficiency (power transmission efficiency), some kind of countermeasure is desired in this respect.

Therefore, an object of the present invention is to shorten the axial length of an automatic transmission as much as possible, while providing a simple structure and an advantage in terms of mechanical efficiency over the conventional planetary gear type transmission mechanism. It is an object of the present invention to provide an automatic transmission for a vehicle which is equipped with a gear mechanism and is capable of obtaining a gear position higher than that obtained by the planetary gear type transmission mechanism, that is, an overdrive.

(Means for Solving the Problems 1) In order to achieve the above-mentioned object, in order to shorten the shaft length of the automatic transmission, basically the input shaft connected to the engine output shaft is The output shaft connected to the axle shaft is arranged parallel to the shaft, and a planetary gear type transmission mechanism is interposed on either one of the shaft and the output shaft. In addition, in order to configure multiple power transmission lines from the engine output shaft to the axle shaft, multiple gear trains with different gear ratios are configured between the input and output shafts, and these multiple gear trains A switching means is provided for selecting any one of a plurality of power transmission paths configured correspondingly to each of the plurality of power transmission paths. The planetary gear type transmission mechanism is set to be located in each of the power transmission lines obtained by the gear trains, and the gear ratio of at least one gear train among the plurality of gear trains is set,
JF for speed increase so that overdrive can be obtained! It is fixed. Specifically, the configuration is as follows. That is, an input shaft connected to the engine output shaft, an output shaft arranged parallel to the input shaft and connected to the axle shaft, and a J!
! A power transmission system including a two-star gear type transmission mechanism, a plurality of gear trains configured between the input shaft and the output shaft and having different gear ratios from each other, and any one gear train among the plurality of gear trains. and the switching means to select.

each of the plurality of power transmission lines corresponding to the plurality of gear trains is set to pass through the planetary gear type transmission mechanism, and the gear ratio of at least one gear train is set for speed increasing. The configuration is as follows.

With such a configuration, for example, the gear train can be divided into two
If you install one set and set one of them for speed increase, when you select a power transmission path with one gear train that is not for speed increase,
The number of gear shifts depending on the gear stage of the planetary gear type transmission mechanism, for example, 1
On the other hand, when the gear train for increasing speed is selected, the fourth speed, that is, overdrive is obtained.

(Example) Embodiments of the present invention will be described below with reference to the accompanying drawings.

In FIG. 1 showing the first embodiment of the present invention, sentence 1. Interchange 2
) Sentence 3 is the first to third axes, and the intersection of these three axes is 1.22. ! Q3 are arranged in such a manner that they are located at the vertices of a triangle when viewed from the axial direction and parallel to the U. On this first axis line 1 is the input shaft 1.
However, an output shaft 2 is located on the second axis line 2, and a pair of left and right axle shafts 3A and 3B are located on the third track line 13.

An engine output shaft 5 is connected to one end of the input shaft 1 via a torque converter 4 , so that output (torque) from the engine is input to the input shaft 1 via the torque converter 4 . Further, a planetary gear type transmission mechanism AT, which will be described later, is interposed in the output shaft 2, and in the embodiment, this planetary gear type transmission mechanism AT is a Simpson type with three forward speeds. It has a two-part structure with a first shaft 2A and a second shaft 2B that are connected in series, and the first shaft 2A is used as an input shaft portion of the planetary gear type transmission mechanism AT, while the second shaft 2
B is the output shaft of a planetary gear transmission [AT].

A first gear train G1 and a second gear train G are connected between the input shaft 1 and the output shaft 2 at the end opposite to the torque converter 4.
2 are configured. This first gear train G1 requires 1 person
1 (first sleeve wire terminal 1-1=) and the drive gear 6 and 1. It meshes with the nuclear drive gear 6 and the output +b'
The driven gear 7 is fixed to the 1st i2A of 2, and its gear ratio is rlJ. In addition, the second gear train G2 is fixed to the first shaft 2A of the output shaft 2 by meshing with the drive gear 8 disposed on the human power 1 oil l (2nd @ Line 1 upper part). The gear ratio of the second gear train G2 is set higher than the gear ratio of the first gear train Gl, that is, the gear ratio is set to increase the speed.

Each drive gear 6.8 of both such gear trains G1 and G2
are rotatable with respect to the input shaft I, respectively, and the first
Is drive gear 6 of gear train GL a one-way clutch? 1
The input shaft 1 is coupled to the input shaft 1 so as to permit rotation transmission only from the input shaft 1 side, and is connected to and connected to the input @1 by a clutch 22 serving as a switching means. Further, the drive gear 8 of the second gear train G2 is connected to the input shaft 1 by the clutch lo as a switching means.
It is designed to be intermittent. An output gear 23 is fixed to the second shaft 2B of the output shaft 2, and the output (torque) from this output gear 23 is transmitted to the second shaft 2B of the output shaft 2.
The left and right axle shafts 3A are connected to the left and right axle shafts 3A through the final reduction gear 11 that is connected to
, 3B.

With the above configuration, when the clutch 10 serving as the switching means is disconnected and the clutch 22 is connected,
The rotation (torque) of the input shaft l is caused by the rotation of the gear train Gl (gear 6.
7), first shaft 2A of output shaft 2, 'M star-heavy dual transmission mechanism A
T, the second shaft 2B of the output shaft 2, and the output gear 23, and is finally transmitted to the axle shafts 3A, 3B.
A power transmission line from the gear train Gl to the output gear 23 via the planetary gear type transmission mechanism AT constitutes a first power transmission line construction. In this first power transmission system road construction,
A number of gear changes are performed according to the gear positions of the planetary gear type transmission mechanism AT (three forward gears in the embodiment).

-1 Meanwhile, the clutch 10 is connected and the clutch 22 is connected.
When the input shaft 1 is disconnected, the rotation of the input shaft 1 is caused by the first gear train G2.
8 and the planetary Y4 insect type transmission mechanism AT, the transmission is finally transmitted to the axle shafts 3A and 3B, and this first gear train G
A power transmission line passing through the planetary gear type transmission mechanism AT according to No. 1 constitutes a second power transmission line II. Then, in the case of the second power transmission line II, based on the relationship of the gear ratio of the second gear train G2, on the premise that the planetary gear type transmission #j1 structure AT is 3rd speed, the gear stage of the O-8 drive is In other words, 4th speed is obtained.

Now, next is the l! The J2 star gear type transmission mechanism AT will be explained, and this is a conventionally well-known Simpson type forward three-speed transmission with reverse. First of all, this planetary gear type transmission a structure AT has a first and a second gear in series with the gear.
It has two sets of planetary gears Y1 and Y2 (front and rear). Of these, planetary gear planet 111rY1. Both sun gears SG1 and SG2 in Y2 are integrated into a crab and rotatably arranged on the outer periphery of the second @2B of output @2, and the integrated product of both sun gears SGI and SG2 is connected to the first clutch (front clutch). , h) It is connected to the first leg 2A of the output shaft 2 via C1, and is intermittently (fixed, free) connected to the casing K of the M star gear type transmission mechanism AT by the first brake (seven cant brake) Bl. It is now possible to Further, a ring gear RGI having a tooth width Y1 is connected to and connected to the first shaft 2A of the output shaft 2 via a second clutch (rear clutch) C2.

Furthermore, the carrier PC2 holding the planetary gear PG2 of the second planetary gear Y2 is coupled to the casing K via the one-way clutch W, so that rotation in only one predetermined direction is permitted. With,
It is connected to the casing K via a second brake (low/high brake) B2. The carrier PCI holding the planetary gear PCI at the first planetary tooth east Yl and the ring gear RG2 at the first planetary tooth width Yl are integrated with the second shaft 2B of the output shaft 2.

Since the planetary tooth width AT itself as described above has been well known, each gear stage of this planetary tooth/F-type transmission mechanism AT, clutches C1, C2 as actuators, brakes B1, . The relationship between the operations of B2 is summarized in Table 1 below, and a detailed explanation beyond this point will be omitted.

In addition, when running in 4th speed with the second gear train G2 passing through, each actuator C1, C2 of the planetary gear type transmission mechanism AT
The operating conditions of B1 and B2 are the same as in the case of 3 speeds in Table 1. Further, the rotational difference when changing from the third speed to the fourth speed is absorbed by the one-way clutch W, and the shift to the fourth speed is smoothly performed.

Table 1 (0=activated, no mark=released) FIG. 2 shows a second embodiment of the present invention, in which the same reference numerals as in the previous embodiment are given to circuit components, and the explanation thereof will be omitted. The same applies to other examples below.)

In this embodiment, the planetary gear type transmission mechanism AT is arranged on the input @1 side, while the clutch 10.22 as a switching means is arranged on the output shaft 2 side. Note that the action itself is not substantially different from the case shown in Figure 1;
When the power transmission system step using the gear train G1 is selected, 1st, 2nd, or 3rd speeds are obtained, and when the power transmission system path using the second gear train G2 is selected, 4th speed is obtained.

FIG. 3 shows a third embodiment of the present invention.

In this embodiment, similarly to the previous embodiment, the first gear train L is selected and the planetary gear type transmission mechanism AT performs forward three-speed gear shifting, while the second gear train G2 is selected and the overdrive (4 gears) is performed.
This planetary tooth 11j type transmission mechanism AT is of the Ravigneau type described later.

Here, the planetary @tun type transmission mechanism AT, which has a Ravigneau type reverse transmission and 3 speeds, has a dual structure between the first shaft 2A and the second shaft 2B of the output shaft 2. 1st
, a second two-tree intermediate shaft portion 31,32. Such an M star gear type transmission mechanism AT also has two planetary gears Y1. The planet gears SGI and SG2 of the planetary gears Y1 and Y2 have different diameters and are separate bodies.
A sun gear SGI having a large diameter Yl is integrated with the first intermediate shaft portion 31, and a sun gear SG2 having a small diameter of the planetary gear Y2 is integrated with the second intermediate shaft portion 32. The second intermediate shaft portion 32 (small diameter sun gear 5
G2) is connected to and disconnected from the first shaft 2A of the output shaft 2 via the first clutch CI, and the first intermediate shaft portion 31 (large diameter sun gear 5G1) is connected to the first shaft 2A via the second clutch C2. It is connected to the first shaft 2A and connected to the casing K via the first brake B1. In addition, the inner planetary gear Y1.
The ring gears RGI and RG2 of Y2 are made common to each other (the structure is such that only the planetary gear Y2 has a ring gear), and the planetary gear PC of the i1th star port Y1
I is meshed with the large diameter sun gear SGI and the common ring gear RG2 (RGI), and the second
It is also meshed with planetary gear PG2 of M star gear Y2 (this meshing relationship is not shown in the drawing to clearly show the existence of planetary gears PCI and PG2). Note that planetary gear PG2 does not mesh with ring gear RG2. Furthermore, inner planetary gears Yl, Y2
Carrier PCI with both planetary gears PG1 and PG2
, PC2 are shared and connected to the casing K via the one-way clutch W, and the second brake B2
is connected to the casing K by. The ring gear RG, 2 (RGl), which has been made common as described above, is integrated with the second shaft 2B of the output shaft 2.

Note that the clutch 10.22 as a switching means and the one-way clutch 21 for reducing shock during 4-speed shifting are as follows:
Since the planetary gear type transmission mechanism AT is provided on the output shaft 2 side, it is provided on the input shaft 1 side.

Since the above-mentioned Ravigneau-type planetary gear 11jAT itself has been well known, the operational relationship between each gear stage of this planetary gear type transmission mechanism AT, the clutches C1 and C2 as actuators, and the brakes B1 and B2 will be explained below. , are summarized in Table 2 below, and further detailed explanation will be omitted. Of course, when selecting 4th speed by the second gear train G2, the flange C1, C2 and the brake B1, B2
The operating conditions are the same as in the case of 3rd speed in Table 2.

Table 2 (○=activated, no mark=released) FIG. 4 shows a fourth embodiment of the present invention, in which a Ravigneau two-speed forward speed mechanism is used as the planetary gear type transmission mechanism AT, and this planetary float type The transmission mechanism AT is provided on the output shaft 2 side. This Lavigneau style forward with reverse 2
The planetary float type transmission mechanism AT has a first gear and a second gear.
It has two planetary gears Yl and Y2, but this planetary gear Y1
, Y2's sun gears SGI and SG2 have different diameters and are made into very separate bodies.
The sun gear SG2, which has a large diameter, is connected to the first shaft 2A of the output shaft 2.
is integrated into. Further, the sun gear SGI, which has a small diameter of the planetary gear Y1, is connected to and connected to the first shaft 2A of the output shaft 2 through the first clutch C1, and connected to the casing K through the first brake B1. . In addition, the ring gears RGI and RG2 of the two-way planetary gears Y1 and Y2 are made common to each other (structurally, only the planetary gear Y1 has a ring gear), and are connected to the casing K via the second brake B2. Then, the planetary gear PCI of the first planetary gear Y1 is meshed with the small diameter sun gear SGI and the common ring gear RGI (RG2), and also with the planetary gear PG2 of the second planetary tooth east Y2. meshed (planetary gear P in the drawing)
G l (!1-PG2 This interlocking relationship is not shown to clearly show the existence of which). In addition, planetary gear P
G2 does not mesh with ring gear RGI (RG2). Furthermore, the two-way star gear Y1. Carrier PC1 and PO with both planetary gears PC1 and PG2 of Y2
2 are shared and integrated into the second shaft 2B of the output shaft 2.

-L Ravigneau planetary gear transmission mechanism AT as described above
Since the mechanism itself has been well known, the following Table 3 summarizes the operating relationships between each gear stage of this planetary gear type transmission mechanism AT and the clutch C1 as an actuator, and the brakes B1 and B2. , further detailed explanation will be omitted. Of course, the operating states of the actuators C1, Bl, and B2 in the third speed as an overdrive obtained by selecting the second gear train G2 are the same as in the case of the second speed in Table 3.

Table 3 (0=activated, no mark=released) FIG. 5 shows a fifth embodiment of the present invention. In this embodiment, in contrast to the one in FIG. The arrangement relationship with the clutch 1O122 as a means is reversed.

Although the embodiments have been described above, the present invention is not limited thereto, and includes, for example, the following cases.

(3) There may be three or more sets of gear trains having different gear ratios, as long as at least one gear train is set for increasing speed.

(2) Instead of using the torque converter 4, it is also possible to use an electromagnetic clutch whose intermittent control is performed electronically.

(Effects of the Invention) As is clear from the above description, the present invention makes it possible to obtain overdrive and increase the number of gears by using a conventional planetary gear transmission mechanism while shortening the overall shaft length. can.

In addition to the above-mentioned planetary gear type transmission mechanism, a plurality of gears with different gear ratios configured between the input shaft and the output shaft are used to provide at least an overdrive speed change mechanism without using planetary gears. Since it is multi-staged including a drive, a structure of 187 and better mechanical efficiency can be obtained compared to the case where this M-star center is used separately.

Of course, the gear train for multi-stage gearing requires only an extremely short shaft length, and the number of gears can be easily changed by increasing or decreasing the shaft length, so it is extremely effective as an automatic transmission of this type.

[Brief explanation of drawings]

Figure 7fS1 is a skeleton diagram showing the first embodiment of the present invention. FIG. 2 is a skeleton diagram showing a second embodiment of the present invention. FIG. 3 is a skeleton diagram showing a third embodiment of the present invention. FIG. 4 is a skeleton diagram showing a fourth embodiment of the present invention. FIG. 5 is a skeleton diagram showing a fifth embodiment of the present invention. AT: Planetary gear type transmission mechanism G1: 1st gear train G2: 2nd gear train Sentence 1, Sentence 2) Sentence 3: Axis line input shaft to 2: Output shaft 2A: First car 2B: 2nd axis 3A, 3B = Axle axis 4: Torque converter 5: Engine output shaft 10.22+clutch (switching means) 11: Final reduction gear Yl, Y2: Planetary gear SGI, SG2: Sangia RGI, RG2: Link gear PCI, PO2: Planetary gear PCI, PO2: Planetary carrier C1, C2: Clutch B1. B2: Brake

Claims (2)

[Claims] (1) An input shaft connected to the engine output shaft, an output shaft arranged parallel to the input shaft and connected to the axle shaft, and a planetary gear provided on either the input shaft or the output shaft. a transmission mechanism, a plurality of gear trains having different gear ratios between the input shaft and the output shaft, and selecting a power system delivery path using any one gear train among the plurality of gear trains. a switching means, wherein each of the plurality of power transmission lines corresponding to the plurality of gear trains is set to pass through the planetary gear type transmission mechanism, and the gear ratio of at least one gear train is set to pass through the planetary gear type transmission mechanism. An automatic transmission for a vehicle, characterized in that it is set to increase speed. (2) The device according to claim 1, wherein the input shaft is connected to the engine output shaft via a torque converter.