JPS6249052A - 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 placed to the one of power transmission routes responding to plural gear trains, and the single power transmission route is set so as to bypass a torque converter. CONSTITUTION:With a clutch 10 disengaged and a clutch 22 engaged, an output is transmitted through a torque converter 4, a first shaft 1A, and a planetary gear type transmission mechanism AT. With the clutch 10 engaged and the clutch 22 disengaged, the output is inputted to a third shaft 1C after bypassing the torque converter 4, and is transmitted through a second gear train G2. This enables increase of the number of stages as the whole length of a shaft is decreased, and permits reduction of incurring of a power loss caused by the torque converter.

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) A typical automatic transmission for a vehicle uses a planetary gear type transmission mechanism connected to an engine output shaft via a torque converter. This planetary gear type transmission mechanism is generally a three-speed transmission mechanism having two sets of planetary gears, such as a Simpson type or Ravigneau type, and a two-speed transmission mechanism is 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. For this reason, in order to increase the number of gears while using the conventionally used planetary gear type transmission mechanism as is, the auxiliary planetary gear for configuring the overdrive phase addition gear is replaced with the conventional torque converter and, for example, three There are now systems that are further interposed between the main planetary gear type transmission mechanism and the step-change 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 φ front drive cars) and mid-engine cars that have horizontally mounted engines. It is required to make the shaft length of the transmission as short as possible.

From this point of view, it has been proposed that an auxiliary planetary gear for an overdrive phase addition gear is provided in parallel with, for example, a three-speed main planetary gear type transmission mechanism (Japanese Patent Application Laid-Open No. 59-1999). (Refer to Publication No.-133852). Also,
In a planetary gear type transmission mechanism, it is generally connected to the engine output shaft via a torque converter.
From the viewpoint of fuel efficiency, etc., many vehicles are now configuring a power transmission line that bypasses the torque converter, that is, a power transmission system is equipped with a torque converter mechanism.

(Problems to be Solved by the Invention) However, as described in the publication, if an auxiliary planetary gear is used in addition to the conventional main planetary gear type transmission mechanism, the planetary gear itself has a very large structure. 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. A vehicular automatic that is equipped with a gear mechanism so as to be able to have more gears than those obtained by the planetary gear type transmission mechanism, and also to configure a power transmission path that bypasses a torque converter. Our goal is to provide transmissions.

(Means for Solving the Problems 1) In order to achieve the above-mentioned object, in the present invention, in order to shorten the shaft length of the automatic transmission, the engine is basically connected to the torque converter via the engine. The output shaft connected to the axle shaft is arranged parallel to the input shaft connected to the output shaft, and a planetary gear type transmission mechanism is interposed on either one of the filling 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 the plurality of power transmission lines configured correspondingly. The planetary gear type transmission mechanism is located in at least one power transmission path, and at least one power transmission path bypasses the torque converter. Specifically, the configuration is as follows. That is, an input shaft connected to the engine output shaft via a torque converter, an output shaft arranged parallel to the input shaft and connected to the axle shaft, and an input shaft provided on either one of the input shaft and the output shaft. and a planetary gear type transmission mechanism configured between the input shaft and the output shaft and geared to each other.

a plurality of gear trains with different gear ratios, and a switching means for selecting a power transmission system using any one gear train among the plurality of gear trains; In both cases, one power transmission line is configured to bypass the torque converter.

With such a configuration, for example, a planetary gear type transmission mechanism is located in a power transmission system obtained by one gear train, while the planetary gear type transmission mechanism is located in a power transmission system obtained by another gear train. If the relationship is such that the gear type transmission mechanism is not located, that is, the planetary gear type transmission mechanism is bi-sprung, then when the above-mentioned one gear train is selected for power transmission and thread path, the planetary gear type transmission mechanism While the number of gear shifts is performed according to the number of gears, a number of gear stages (for example, overdrive) corresponding to the number of other gear trains are added to the gear stages of this planetary gear type transmission mechanism to achieve multi-stages. It turns out.

Since one power transmission line obtained by at least one gear train bypasses the torque converter, for example, if this bypassing power transmission line is used for overdrive in 4th gear, etc., when running in 4th gear, , it is possible to run in a state where it is directly connected to the engine output shaft, similar to the conventional lock-up.

In addition, for example, if two sets of gear trains are provided and the M star gear type transmission mechanism is located in common in the power transmission system of both sets, the gear ratios of the gear trains can be different, i.e., high and low. Accordingly, obtain a high/low relationship for each gear stage of the planetary gear type transmission mechanism, that is, 1st gear low, 1st gear high, 2nd gear low, 2nd gear high, 3rd gear low, 3rd gear. It is possible to create multiple stages such as ``high''. In this case, the power transmission line of the gear train on the "high" side can be installed so as to bypass the torque comparator.

(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, vertical 1, vertical 2
．． 13 are the first and third axes, respectively, and these three axes 1, 2, 9, and 3 are arranged so that they are parallel to each other and located at the apex of the triangle when viewed from the axial direction. It is said to be related. This first axis line sentence IL has an input axis l
However, the output shaft 2 is also on the second axis line 2, and the third @
A pair of left and right axle shafts 3A and 3B are located at the line intersection 3-)-.

The above-mentioned input shaft portion has a first axis intersection 1] in order to form a power transmission line that passes the torque converter and to form a planetary gear type transmission mechanism AT with respect to the input shaft l. 2, the first axis IA, the second axis IB,
It has a three-division configuration with the third axis IC. This first axis I
A and the second shaft IB have a planetary gear type transmission mechanism A between them.
T (Simpson type forward three-speed transmission in the example), which are arranged in series with each other so as to be rotatable around the outer periphery of the third shaft 1G, and the first shaft IA is a planetary gear type transmission mechanism AT.
The second shaft IB is used as an output shaft of the planetary gear type transmission mechanism AT, and the third shaft IB is used as a bypass for bypassing the torque converter. That is, as is well known, the torque converter 4 is composed of a pump 4a, a turbine 4b, and a stator 4c coupled to a casing K via a one-way clutch W1, and the engine output shaft 5 is connected to the pump 4a of the torque converter 4. At the same time, the first shaft IA serves as a turbine shaft and is connected to the turbine 4b of the torque converter 4. And the third @J11C for bypass bypasses the torque converter 4, that is, the turbine 4b,
It is connected to the engine output shaft 5 via a damper D.

On the other hand, the output shaft 2 is divided into three parts: a first shaft 2A, a second shaft 2B, and a third shaft 2C, each located on a second axis line 2. Of these, the if car 2A and the second @2B each have a dual structure inside and outside, and constitute input shafts of different power transmission lines, respectively, and the third shaft 2c is connected to the first shaft 2A. , which is arranged in series with the second shaft 2B and serves as an output shaft portion. The output gear 23 fixed to the third shaft 2C as an output shaft portion is connected to the final reduction gear 11, and from this final reduction gear 11, the axle shaft 3A is connected via the differential box 12.
, 3B.

Between the input shaft 1 and the output shaft 2, a 1.5rJ2 gear train G1, G2 is constructed. This first gear train Gl is 1. Drive gear 6 fixed to the second shaft IH of the input shaft L
, and a driven gear 7 that meshes with the drive gear 6 and is fixed to the second shaft 2B of the output shaft 2, and the gear ratio of the first gear train G1 is set to "1". The second gear train G2 includes a drive gear 8 fixed to the third shaft 1c of the input shaft 1, and a driven gear 9 meshed with the drive gear 8 and fixed to the first shaft 2A of the output shaft 2. The gear ratio of the second gear train G2 is the same as that of the first gear train G.
The gear ratio is set higher than the gear ratio of 1 (set to increase speed).

The first shaft 2A of the output @2 to which the driven gear 9 of the second gear train G2 is fixed is the third shaft 2C having the output gear 23.
On the other hand, the clutch IO serving as a switching means connects and disconnects the power. Further, the second shaft 2B of the output shaft 2 to which the driven gear 7 of the first gear train G1 is fixed has a one-way clutch 21 that allows rotation transmission only from the second shaft 2A side to the third shaft 2C. The one-way clutch 21 and the one-way clutch 21 are connected to each other via a clutch 22 serving as a switching means.

With the above configuration, when the clutch 10 serving as the switching means is disconnected and the clutch 22 is connected,
Power from the engine output shaft 5 is transmitted via the torque converter 4 to the first @IA of the input shaft l to the planetary gear type transmission mechanism A.
T, the second gear train Gl (
gear 6.7), second shaft 2B of output shaft 2, third shaft of output shaft 2
Through the shaft 2C1 output gear 23, finally the axle shaft 3A
, 3B, and by using such a first gear train Gl, the torque converter 4 and the planetary gear type transmission mechanism A
The power transmission path from T to the output gear 23 is the first
Configure the power transmission system roadworks. In this first power transmission system road construction, the gear position (
In this embodiment, the number of gear changes is determined according to the number of forward gears (three forward speeds).

On the other hand, when the clutch 10 is connected and the clutch 22 is disengaged, the power from the engine output shaft 5 bypasses the torque converter 4 and is input to the third shaft 1c of the input shaft 1. Along with the input to the IC, it also bypasses the planetary gear type transmission mechanism AT, and is finally transmitted to the axle shafts 3A, 3B from the first shaft 2A and third shaft 2C of the second gear train G2) output shaft 2. transmitted to. This second
A power transmission line that bypasses the torque converter 4 and the planetary gear type transmission mechanism AT by the gear train G2 constitutes a second power transmission line (■), and when the second power transmission line II is used, the planetary gear type transmission mechanism In contrast to the 3-speed transmission of the mechanism AT, an overdrive gear, ie, 4th speed, is obtained. Note that when switching from the first gear train Gl to the second gear train G2 (when changing from 3rd gear to 4th gear), the one-way clutch 23 absorbs the rotational speed difference caused by this switching, and this switching is performed. It will be carried out smoothly.

Next, the above-mentioned planetary gear type transmission mechanism AT will be explained. This is a conventionally well-known Simpson type three-speed forward transmission with reverse. First, this planetary gear type transmission mechanism AT has two planetary gears Y1 and Y2, first and second (front and rear), which are in series with each other. Both sun gears SG1 and SG2 in these two-way star gear planetary gears Y1 and Y2 are integrated with each other and are rotatably arranged on the outer periphery of the second shaft IB of the input shaft 1.
The integrated body of GI and SG2 is connected to the first shaft IA of the input shaft 1 via the first clutch (front clutch) C1, and connected to the casing K by the first brake (second brake) BL (fixed, Free].

Further, the ring gear RGI of the first planetary gear Y1 is connected to the first @IIA of the input fdil via the second clutch (rear clutch) C2. Further, 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 W2, so that rotation in only one predetermined direction is permitted. At the same time, it is connected to the casing K via a second brake (low-reverse brake) B2. A carrier PCI holding the planetary gear PCI in the first planetary gear Yl, and a ring gear R in the second planetary gear Y2.
G2 is integrated with the second shaft IB of the input shaft I.

Since the planetary gear AT itself as described above has been well known, the relationship between each gear stage of this planetary gear type transmission mechanism AT and the operation of the clutches C1 and C2 as actuators and the brakes B1 and B2 is as follows. By showing them all in Table 1, further detailed explanation will be omitted.

In addition, when driving in 4th speed with :52 gear train G2 selected,
Each actuator C1, C2 of the planetary gear type transmission mechanism AT
) B1 and B2 are all canceled (neutral).

:? Table S1 (○=activated, no mark=released) FIG. 2 shows a second embodiment of the present invention, and the same components as those of the previous embodiment are given the same reference numerals and their explanations will be omitted.

In this embodiment, the planetary gear type transmission mechanism AT is of the Lavigneau type with two forward speeds with reverse, which will be described later. As a result, when the first gear train Gl, that is, the first power transmission path ■ is selected, the first speed by the planetary gear type transmission mechanism AT,
When a two-speed 2-speed shift is performed and the Em2 power transmission path ■, which bypasses the second gear train G2, that is, the planetary gear transmission mechanism AT, is selected, overdrive (3rd speed) is obtained. .

Here, a planetary gear type transmission mechanism AT, that is, a planetary gear type transmission mechanism AT having two forward speeds with a Ravigneau type reverse
has two planetary gears Y1 and Y2, the first and second, and both sun gears SGI and SG2 of the planetary gears Yl and Y2
The sun gears SG2, which have different diameters and are separate from each other, are integrated with the first shaft IA of the input shaft 1, and the large diameter sun gear SG2 of the planetary gear Y2. Also, planetary gear Y
The sun gear SGI, which has a small diameter of 1, is connected to the first clutch C1.
It is connected and disconnected to the first shaft IA of the input shaft 1 via the input shaft 1, and connected to the casing K via the first brake Bl. In addition, the ring gear RGI of the inner planetary gears Y1 and Y2,
RG2 is strongly standardized (the structure is similar to that of the planetary gear Yl).
(with only a ring gear) is connected to the casing K via the second brake B2. The planetary gear PCI of the first planetary gear Y1 is connected to the small diameter sun gear SGI and the common ring gear RGI.
(RG2), and is also meshed with planetary gear PG2 of first planetary gear Y1 (this meshing relationship is not shown in the drawing to clearly show the existence of planetary gears PCI and PO2). ). Note that planetary gear PG2 does not mesh with ring gear RGI (RG2). Furthermore, both 'M star gears Yl, Y
Carrier PC with both planetary gears PCI and PO2
I and PC2 are shared, and the second *b l of input shaft I
It is integrated into B.

Since the Ravigneau type planetary gear AT itself as described above has been well known, the operational relationship between each gear stage of this planetary tooth JII type transmission mechanism AT and the clutches C1, PLAY, t-Bl, and B2 as actuators will be explained below. are summarized in Table 2 below, and further detailed explanation will be omitted.

Table 2 (0=activation, no mark=cancellation) Although the embodiments have been described above, the present invention is not limited thereto, and includes, for example, the following cases.

(0) There may be three or more sets of gear trains with different gear ratios. In this case, for example, the gear train after summer is a torque converter 4 and a planetary gear type like the second gear train G2. It may be one that bypasses the transmission mechanism AT, or it may be one that passes through the torque converter 4 and the planetary gear type transmission mechanism AT, like the first gear train G1.In particular, the first gear train Gl may be one that bypasses the transmission mechanism AT. For example, by providing at least two sets of gear trains passing through the planetary gear type transmission mechanism AT, a high/low relationship can be established for each gear stage in the planetary gear type transmission mechanism AT.

(2) The planetary gear type transmission mechanism AT may be provided on the output shaft 2 side, and the switching means power transmission system pedal and the II selection clutch 10.22 may be provided on the input @1 side.

<3) The power transmission line passing through the planetary gear type transmission mechanism AT may bypass the torque converter 4.

(Effects of the Invention) As is clear from the above description, the present invention can use a conventional planetary gear type transmission mechanism to shorten the overall shaft length and increase the number of stages.

In addition to the above planetary gear type transmission mechanism, multi-stage transmission is achieved by using a plurality of gear trains with different gear ratios between the input shaft and the output shaft, without using planetary gears. Therefore, compared to the case where this planetary gear is used separately, it is possible to obtain a structure that is simpler and has better mechanical efficiency.

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.

In particular, in the present invention, at least one power transmission line bypasses the torque converter to obtain a so-called lockup, which is preferable in terms of reducing power loss due to the torque converter.

And a lock amplifier mechanism for long-up (E)
Since the clutch for switching the power transmission system using multiple gear trains can also be used as a clutch for switching the power transmission system, it is no longer necessary to separately provide a clutch for switching the power transmission system using multiple gear trains. is even more advantageous in terms of miniaturization.

[Brief explanation of drawings]

FIG. 1 is a skeleton diagram showing a first embodiment of the present invention. FIG. 2 is a skeleton diagram showing a second embodiment of the present invention. AT: Planetary gear type transmission mechanism GL: 1st gear train G2: 2nd gear train Father 1, Cross 2) Sentence 3: Axis line 1: Input shaft IA: 1st #? 1B: Second car IC = 3rd car 2 Output 1 2A: 1st axis 2B: 2nd axis 2C: Third car 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: Ring gear PCl, PO2: Planetary gear PCI, PO2: Blanetary carrier C1, C2: Clutch Bl, B2 Nibrake

Claims (2)

[Claims] (1) An input shaft connected to the engine output shaft via a torque converter, an output shaft arranged parallel to the input shaft and connected to the axle shaft, and one of the input shaft and the output shaft A power system is provided by a planetary gear type transmission mechanism provided, a plurality of gear trains having different gear ratios between the input shaft and the output shaft, and any one gear train among the plurality of gear trains. switching means for selecting a system, wherein the planetary gear type transmission mechanism is located in at least one of the plurality of power transmission paths corresponding to the plurality of gear trains, and the planetary gear type transmission mechanism is located in at least one of the plurality of power transmission paths corresponding to the plurality of gear trains. An automatic transmission for a vehicle, wherein at least one power transmission line is set to bypass the torque converter. (2) In claim 1, the gear train is
The power transmission system via one gear train bypasses the planetary gear type transmission mechanism and the torque converter.