JPH08184352A - Four-speed shift mechanism - Google Patents

Abstract

PURPOSE: To provide a four-speed shift mechanism with under drive constituted in such a manner that the carrier of a pinion produces the output of a shift mechanism by providing a double planetary gear set, the single planetary gear set, and only six frictional engagement and fixing elements. CONSTITUTION: During extra low running, an input shaft 3 and a sun gear s2 are intercoupled through a clutch c0 and a ring gear r1 is fixed to a case 5 by a brake b1. Thus, torque inputted to a sun gear s1 is decelerated and outputted from a carrier 1c. Further, during first speed running, an input shaft 3 and a sun gear s1 are intercoupled through a clutch c2 and a carrier c2 is fixed to the case 5 by the brake b1. Thus, torque inputted to the sun gear s1 is decelerated and outputted from the carrier 1c. Further, during reversing, the input shaft 3 and the sun gear s1 are intercoupled through the clutch c2 and the ring gear r1 is fixed to the case 5 by a brake b2. This constitution outputs reversing and deceleration from the ring gear r2.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a four-speed transmission mechanism having an underdrive or overdrive gear ratio,
Used for FR (front engine / rear drive) type automatic transmission.

[0002]

2. Description of the Related Art Japanese Unexamined Patent Publication No. 3-4059 has a double planetary gear set I in the first row and a simple planetary gear set II in the second row in the opposite direction from the input shaft side.
A five-speed transmission mechanism has been proposed in which one of the double pinions in the row is extended to become a pinion P common to the first and second rows. FIG. 4 is a gear train diagram for explaining the conventional five-speed transmission mechanism.

With reference to FIG. 4, this transmission mechanism includes a clutch (C0-3) for connecting the torque input / output shaft and a rotating member in a disconnectable and connectable manner, and the rotating members to the transmission. Brake (B
0 to 2) in total, and a carrier 11c (connected to 10c) serving as an output of this transmission mechanism, which pivotally supports all pinions including a pinion common to the first row and the second row. 11C is an FF (front engine) that extends to the outside of the speed change mechanism further to the input shaft side of the second-row planetary gear set II and is connected via a gear to a counter mechanism 18 provided parallel to the input / output shaft.・ A front gear shift mechanism.

Japanese Unexamined Patent Publication No. 3-249453 discloses the above-mentioned Japanese Unexamined Patent Publication No. 3-249453.
A 5-speed transmission mechanism has been proposed for making the transmission mechanism described in JP-A-4059 FR (front drier / rear dlife). Figure 5
[Fig. 6] is a gear train diagram for explaining the conventional 5-speed transmission mechanism.

Referring to FIG. 5, in this transmission mechanism, the total number of clutches and brakes is 7 elements (C1-5, B1).
2), the planetary gear set (I, II) is configured such that, from the input side, the double planetary gear set I in the first row and then the simple planetary gear set II in the second row.
The above-mentioned publication is different from the above-mentioned publication only in the point of disposing, and a carrier 11C 'which is an output by pivotally supporting all pinions including a common pinion in the first row and the second row is provided. It is an FR dedicated transmission mechanism that is connected to the output shaft 15 from the rear side (transmission mechanism output side) of the second-row planetary gear set II via a clutch C4. The clutch C4 and the clutch C5 for switching the output in parallel with the clutch C4 are the second-row planetary gear set II.
It is provided on the rear side of.

These five-speed transmission mechanisms are used in high-priced vehicles equipped with relatively high-power engines.

[0007]

However, the five-speed transmission mechanism proposed in Japanese Patent Laid-Open No. 3-4059 has a FF
The speed change mechanism, which is a dedicated speed change mechanism and is proposed in Japanese Patent Laid-Open No. 3-249453, is FR-ized,
It has a total of seven clutches and brakes, like the transmission mechanism described in the 4059 publication. Engagement / disengagement fixing elements such as clutches and brakes have a complicated mechanism, and the transmission case for accommodating the transmission mechanism is enormous in order to secure the location of these elements in the transmission, and the manufacturing cost is increased. Have the problem of

Further, the speed change mechanism proposed in Japanese Patent Laid-Open No. 3-249453 has clutches C4 and C5 on the rear side of the second-row planetary gear set II in order to realize the fifth speed.
Due to the juxtaposition, the transmission mechanism is expanded in the axial direction.

Further, in an automatic transmission type light vehicle equipped with an engine of relatively low output, which requires a low price, 5
Fast shifts are not necessary and may result in excess quality.

Therefore, it is a basic object of the present invention to provide a four-speed transmission mechanism that solves the above-mentioned problems, has a compact structure with few clutches or braking elements, and achieves a significant cost reduction. Another object of the present invention is to provide a basic speed change mechanism that can easily create a different speed change mechanism.

[0011]

In order to achieve the above-mentioned basic object, a four-speed transmission mechanism according to a first aspect of the present invention is provided with a sun gear s1 and a pinion in order between a power shaft 3 and an output shaft 4. a first row double planetary gear set including a p1, a pinion p2, and a ring gear r1, a sun gear s2, and the first gear
A second row simple planetary gear set consisting of the pinion p1 and the ring gear r2 of the row, and the first row and the second row planetary gear set are juxtaposed between the input shaft 3 and the output shaft 4, The torque from the input shaft is a four-speed transmission mechanism in which the torque is changed through these planetary gear sets and transmitted in series to the output shaft, and three clutches (c0, c1, c2) for connecting and disconnecting the torque and Two brakes (b1, b2) for fixing the rotating member in a non-rotatable manner,
A pinion p1 and a carrier 1c which supports the pinion p2 in common, and the pinion of the second row extends the pinion p1 of the first row in the second row direction,
The input shaft 3 is releasably connected to the sun gear s2 via the clutch c0, is releasably connected to the ring gear r1 via the clutch c1, and is connected to the sun gear s2 via the clutch c2. The sun gear s1 is detachably connected to the ring gear r1 and the brake b2.
The ring gear r2 can be fixed by the brake b1, and the carrier 1c is connected to the output shaft 4.

In the first aspect, the carrier 1
It is preferable that c is connected to the output shaft 4 through between the second row sun gear s1 and the ring gear r2.

In a second aspect, the present invention also includes a first-row double planetary gear set consisting of a sun gear s1, a pinion p1, a pinion p2, and a ring gear r1 in this order between the input shaft 3 and the output shaft 4. Sun Gear s2, the first
A second row simple planetary gear set consisting of the pinion p1 and the ring gear r2 of the row, and the first row and the second row planetary gear set are juxtaposed between the input shaft 3 and the output shaft 4, A four-speed transmission mechanism in which torque from the input shaft is shifted through these planetary gear sets and transmitted in series to the output shaft, and includes two clutches (c1, c2) and a rotating member that connect and disconnect the torque. The two brakes (b0, b1, b2) that fix the wheel in a non-rotatable manner,
A pinion p1 and a carrier 1c which supports the pinion p2 in common, and the pinion of the second row is formed by extending the pinion p1 of the first row in the second row direction, and the input shaft 3 is , The gear c1 is detachably connected to the ring gear r1 via the clutch c1 and the sun gear s1 is detachably connected to the ring gear r1 via the clutch c2. The ring gear r1 can be fixed by the brake b2. The ring gear r2 can be fixed by the brake b1, and the sun gear s1 is fixed by the brake b1.
The carrier 1c is connected to the output shaft 4 by means of the above.

In the second aspect, it is preferable that the carrier 1c is connected to the output shaft 4 passing between the second row sun gear s1 and the ring gear r2.

[0015]

Under the above structure, in common with the first and second aspects of the present invention, only six friction engagement / fixing elements are provided to provide an underdrive (UD) (first aspect) or an overdrive. The drive mechanism (OD) (second viewpoint), the forward four-speed reverse and first-reverse speed change mechanism, is particularly compact in the input / output axis direction. Moreover, in the underdrive or overdrive four-speed transmission mechanism, the planetary gear set portion, the two clutches and the two brakes are common constituent elements, so that the parts are made common, and the assembly line and the apparatus are Will be standardized, and a significant cost reduction will be realized. In addition, it is possible to use a common mechanism for both UD and OD as a 3rd speed transmission mechanism, and ultimately, a total of 3 different transmission mechanisms are provided based on one basic transmission mechanism. This achieves the object according to the other aspect of the present invention.

Further, in an automatic transmission vehicle of the same size (the input level from the engine is the same), there is no example in which there is a difference in the number of shift steps of two, such as the third speed or the fifth speed. That is, for a certain level of engine output (torque input to the transmission), there are transmissions of the third and fourth speeds, or the fourth and fifth speeds, but there is no example such as the third and fifth speeds. . Therefore, in the four-speed transmission mechanism of the present invention, the clutch 1
It is practically sufficient because by selecting and installing one and / or one brake, it is possible to achieve 3 speeds with a difference of 1 speed, 4 speeds with UD or 4 speeds with OD. It is possible to adjust the overall gear ratio by final deceleration (typically a differential mechanism).

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below with reference to the accompanying drawings. First, the structure of a four-speed transmission mechanism with an underdrive (UD) as the first embodiment and an overdrive (OD) as the second embodiment will be described. Next, in these embodiments, operating elements for the first to third speeds will be described. And the gear ratio is common, and these gear shifting operations will be described together.

<Embodiment 1> First, the structure of a 4-speed transmission mechanism with a UD according to an embodiment of the present invention will be described. FIG. 1 is a gear train diagram of a 4-speed transmission mechanism with UD according to an embodiment of the present invention.

With reference to FIG. 1, this four-speed transmission mechanism has a sun gear s1, a pinion p1, a pinion p2, and a ring gear r1 that mesh with each other between an input shaft 3 and an output shaft 4 in order.
1st row double planetary gear set I consisting of, sun gear s2 meshing with each other in order, said pinion p of 1st row
1, a second-row simple planetary gear set II including a ring gear r2.

The double pinion p1 in the first row has three clutches (c0, c1, c2) for connecting and disconnecting the driving torque and two brakes (b1, b2) for non-rotatably fixing the rotating member. and a carrier 1c which supports p2 in common, and the pinion in the second row is the pinion p in the first row.
1 is extended in the second row direction.

The drive torque input shaft 3 is releasably connected to the sun gear s2 via the clutch c0 and is releasably connected to the ring gear r1 via the clutch c1.
Further, the ring gear r1 is fixable by a brake b2, and the ring gear r2 is fixable by a brake b1.

The above carrier 1c is the second row of sun gear s.
1 and the ring gear r2, and is connected to the output shaft 4. Such a mechanism is suitable for FR type transmissions.

The input shaft 3 of the four-speed transmission mechanism is connected to a turbine of a torque converter (not shown), and the output shaft 4
Is connected to a differential gear (not shown).

<Embodiment 2> FIG. 2 is a gear train diagram of an OD-equipped 4-speed transmission mechanism according to an embodiment of the present invention.

The OD-equipped four-speed transmission mechanism and the UD
The 4-speed transmission mechanism with a planetary gear set (I, I
I), two clutches (C1, C2) and two brakes (b1, b2) have a common structure (including connection structure)
Therefore, the description thereof will be omitted, and only the partial configuration which is different in both mechanisms will be described.

Referring to FIG. 2, the OD-equipped four-speed transmission mechanism does not include a clutch c0 that connects the input shaft 3 and the sun gear s2 so that they can be connected and disconnected. Instead, a brake b0 for fixing the sun gear s2 to the case 5 is provided. In order to perform this fixing, the case 5 is provided with the ring gear r2 of the second row.
To the second row of sun gear s2 (key shape)
Is curved. The carrier 1c, which commonly supports the double pinions p1 and p2 in the first row, as in the previous embodiment, is connected to the output shaft 4 through a shaft inner tube (not shown) that supports the sun gear s1 in the second row. Has been done.

Here, in order to explain the meshing state of the gears of Embodiments 1 and 2, FIG. 2 schematically shows a radial cross section of the gear. The solid lines show the gears of the first row planetary gear set I and the dotted lines show the gears of the second row planetary gear set II.

Referring to FIGS. 1 and 2, the sun gear s1
Is formed to have a larger diameter than the sun gear s2, and the ring gear r1
Is formed to have a larger diameter than the ring gear r2, and the pinion p1
Has a smaller diameter than the pinion p2.

The pinion p common to the first and second rows is
1, the outer diameter of the second row is larger than the outer diameter of the first row, and one of the first row sun gear and double pinion p2, and the second row of sun gear s1 and pinion p.
Meshed with 2. By the way, the pinions p1 and p2 and the carrier 1c that pivotally supports them constitute one rotating member.

In common with the first and second four-speed transmission mechanisms, no clutch is arranged on the output side of these transmission mechanisms, so that the transmission mechanism is very compact especially in the input / output axis direction. The space occupied in the vehicle has been significantly reduced.

Next, the operation of each of the above-mentioned two first and second four-speed transmission mechanisms will be described for each gear stage with reference to Tables 1 and 2. However, the first to third speeds are common to the first and second speed change mechanisms, UD is provided only in the first speed change mechanism, and OD is provided only in the second speed change mechanism.

<4 of Example 1 (with UD) and Example 2 (OD)
Operation of High Speed Shift Mechanism> Table 1 relates to the internal speed ratio of the gears of the two planetary gear sets (I, II) in the four speed shift mechanism of Example 1 (with UD) and Example 2 (OD). 6 is a tooth number table showing the number of teeth to be formed.

[0033]

[Table 1]

Table 2 is a gear shift table showing each operating element and each gear ratio in four forward gears and one reverse gear. Note that the gear ratio is the same as that disclosed in Japanese Patent Laid-Open No. 3-4059 and Japanese Patent Laid-Open No. 3-2494.
It is calculated by applying the formula described in Japanese Patent No. 53.

[0035]

[Table 2]

<Extra Low (UD)> (Only the 4-speed transmission mechanism of the first embodiment) Referring to Table 1, the operating element at this time is the clutch c0.
And the brake b1. Input shaft 3 by clutch c0
Is connected to the sun gear s2, and the ring gear r1 is fixed to the case 5 by the brake b1. Sun gear s1
The torque input to is decelerated and output from the carrier 1c.

<1st speed> (common to the 4th speed transmission mechanism of the first and second embodiments) The operating elements at this time are the clutch c2 and the brake b1.
Is. The input shaft 3 and the sun gear s1 are connected by a clutch c2, and the carrier c2 is fixed to the case 5 by a brake b1. The torque input to the sun gear s1 is decelerated and output from the carrier 1c.

<Second speed> (common to the fourth speed transmission mechanism of the first and second embodiments) The operating elements at this time are that the input shaft 3 and the ring gear r1 are connected by the clutch c1 and the ring gear r2 is connected by the brake b1. Is fixed to the case 5, and the torque input to the ring gear r1 is decelerated and output from the carrier 1c.

<Third speed> (common to the fourth speed transmission mechanism of the first and second embodiments) The operating elements at this time are the clutch c1 and the clutch c2.
Is. Input shaft 3 and ring gear r1 by clutch c1
Is connected, and the input shaft 3 and the sun gear s2 are connected by the clutch c2, so that the first-row planetary gear set I is integrally driven. Therefore, the rotational torque input to the ring gear r1 and the sun gear s1 is output from the carrier 1c without being shifted.

<Overdrive, 4th speed> (Only the 4th speed transmission mechanism of the second embodiment) The operating elements at this time are the clutch c1 and the brake b0.
Is. Input shaft 3 and ring gear r1 by clutch c1
And the ring gear r1 is fixed to the case 5 by the brake b0. The torque input to the ring gear r1 is accelerated and output from the carrier 1c.

<Reverse travel> (common to the four-speed transmission mechanism of the first and second embodiments) The operating elements at this time are the clutch c2 and the brake b2.
Is. The input shaft 3 and the sun gear s1 are connected by a clutch c2, and the ring gear r1 is fixed to the case 5 by a brake b2. As a result, the sun gear s2 and the ring gear r2 rotate in reverse, and the reverse rotation / deceleration output is performed from the ring gear r2.

Due to the structure and operation of such a four-speed transmission mechanism, only six frictional engagement / fixing elements in total are provided with an underdrive (UD) or overdrive (OD) forward four-speed reverse one-speed transmission mechanism. Is particularly compact in the input / output axis direction. Moreover, in the underdrive or overdrive four-speed transmission mechanism, the planetary gear set portion, the two clutches and the two brakes are common constituent elements, so that the parts are made common, and the assembly line and the apparatus are Will be standardized, and a significant cost reduction will be realized. In addition, it is possible to use a common mechanism for both UD and OD as a 3rd speed transmission mechanism, and ultimately, a total of 3 different transmission mechanisms are provided based on one basic transmission mechanism. Further, since such a speed change mechanism has the input shaft 3 and the output shaft 4 which are on a straight line, it is preferable to employ such a speed change mechanism in an FR automatic transmission.

Normally, an ordinary passenger car equipped with an automatic transmission mechanism does not require the gear stages of the fifth speed, and the fact that the fifth speed makes the number of constituent elements increase and leads to cost increase. With or without OD 4 forward 1 reverse 1
The four-speed transmission mechanism with selectable gears is particularly preferably used for such an application.

Although the present invention has been described with reference to the above embodiments, the present invention is not limited to the above embodiments, but includes various embodiments according to the principle of the present invention.

[0045]

As described above, the first and second aspects of the present invention
According to the four-speed transmission mechanism according to the viewpoint (1), due to the structure and operation of such a four-speed transmission mechanism, a total of six friction engagements are achieved.
Due to the fixed element, a transmission mechanism with an underdrive (UD) or an overdrive (OD) of 4 forward speeds and 1 reverse speed is particularly compact in the input / output axis direction. Moreover, in the underdrive or overdrive four-speed transmission mechanism, the planetary gear set portion, the two clutches and the two brakes are common constituent elements, so that the parts are made common, and the assembly line and the apparatus are Will be standardized, and a significant cost reduction will be realized. In addition, it is possible to use a mechanism common to the transmission mechanism with UD and the transmission mechanism with OD as a third speed transmission mechanism, and eventually, three different transmission mechanisms are provided based on one basic transmission mechanism.

[Brief description of drawings]

FIG. 1 is a gear train diagram illustrating a 4-speed transmission mechanism with a UD according to an embodiment of the present invention.

FIG. 2 is a gear train diagram illustrating an OD-equipped four-speed transmission mechanism according to a second embodiment of the present invention.

FIG. 3 is a schematic cross-sectional view of a gear for explaining meshing of each gear of the four-speed transmission mechanism of the embodiment of the present invention shown in FIGS. 1 and 2.

FIG. 4 is a gear train diagram illustrating a conventional 5-speed transmission mechanism.

FIG. 5 is a gear train diagram illustrating a conventional 5-speed transmission mechanism.

[Explanation of symbols]

 I First-row planetary gear set II Second-row planetary gear set s1, s2 Sun gear p1, p2 Pinion r1, r2 Ring gear 1c Carrier c0, c1, c2 Clutch b0, b1, b2 Brake 3 Input shaft 4 Output shaft 5 Case

Claims (4)

[Claims] 1. A sun gear s1, a pinion p1, a pinion p2, and a ring gear r1 between an input shaft 3 and an output shaft 4 in this order.
And a second-row simple planetary gear set II including a sun gear s2, the pinion p1 of the first row, and a ring gear r2, and an input shaft 3 and an output shaft 4. The first-row and second-row planetary gear sets are juxtaposed between the two gears, and the torque from the input shaft is changed in speed through the planetary gear sets and is transmitted in series to the output shaft. There are three clutches (c0, c1, c) that connect and disconnect the torque.
2) and two brakes (b1, b2) that fix the rotating member in a non-rotatable manner, and a carrier 1c that commonly supports the pinion p1 and the pinion p2 in common, and the second row of pinions is The pinion p1 of the first row is extended in the second row direction, the input shaft 3 is detachably connected to the sun gear s2 via the clutch c0, and the ring gear is connected via the clutch c1. r1 is detachably connected and is also detachably connected to the sun gear s1 via the clutch c2, the ring gear r1 is fixable by the brake b2, and the ring gear r2 is the brake. The fourth speed transmission mechanism is characterized in that it is fixable by b1 and the carrier 1c is connected to the output shaft 4. 2. The four-speed transmission mechanism according to claim 1, wherein the carrier 1c is connected to the output shaft 4 through a space between the sun gear s1 and the ring gear r2 in the second row. 3. A sun gear s1, a pinion p1, a pinion p2, and a ring gear r1 between the input shaft 3 and the output shaft 4 in this order.
And a second-row simple planetary gear set including a sun gear s2, the pinion p1 of the first row, and a ring gear r2. The first-row double planetary gear set is provided between the input shaft 3 and the output shaft 4. The first-row and second-row planetary gear sets are arranged side by side, and the torque from the input shaft is changed in speed through these planetary gear sets and is transmitted in series to the output shaft. , Two clutches (c1, c2) for connecting and disconnecting the torque, and two brakes (b) for fixing the rotating member in a non-rotatable manner.
0, b1, b2), and a carrier 1c that supports the pinion p1 and the pinion p2 in common, and the second row pinion extends the first row pinion p1 in the second row direction. The input shaft 3 is detachably connected to the ring gear r1 via the clutch c1, and the clutch c2
Is connected to the sun gear s1 so as to be connectable to and disconnectable from the sun gear s1, the ring gear r1 is fixable by the brake b2, the ring gear r2 is fixable by the brake b1, and the sun gear s1 is The four-speed transmission mechanism is characterized in that it can be fixed by a brake b1 and the carrier 1c is connected to an output shaft 4. 4. The four-speed transmission mechanism according to claim 3, wherein the carrier 1c passes through the sun gear s1 in the second row and is connected to the output shaft 4.