KR0158169B1 - The power train of automatic transmission for a vehicle - Google Patents

Abstract

A torque converter that receives power from the engine and converts the torque to output the torque to the input shaft to reduce stress acting on each member of the planetary gear set and to increase the torque at the same size; And a double pinion planetary gear set which is composed of a single pinion planetary gear set which is disposed around the input shaft and in which the ring gear is connected to the power transmitting member by output means and which shares the sun gear with the ring gear of the single pinion planetary gear set, A first friction element disposed between the first pinion carrier and the input shaft for selecting the double pinion carrier as an input element and a second friction element for selecting the single pinion carrier as a reaction element during operation of the first friction element, A third frictional element for selecting the sun gear as a reaction element in operation of the first frictional element and a fourth frictional element for selecting the sun gear as an input element in operation of the first frictional element; With the fasting; A single pinion planetary gear set to which the pinion carrier and the transfer drive gear are connected to receive the output of the peripheral speed portion and to use the ring gear as an input element and the pinion carrier as output means, A third friction element, a fifth friction element for selecting the sun gear of the single pinion planetary gear set as the reaction element during the operation of the first and fourth friction elements, and a fifth friction element for selecting the sun gear of the single- And a sixth friction element that locks the pinion gear and the sun gear of the set as an output element to be locked, thereby providing a powertrain of a vehicular automatic transmission.

Description

Automotive powertrain powertrain

1 is a view showing a power train of a transmission according to a first embodiment of the present invention,

FIG. 2 is an operation table of frictional elements for each shift position of the transmission according to the first embodiment of the present invention,

3 is a graph for explaining the speed ratio of the power train of FIG. 1 by the lever analysis method,

4 is a view showing a power train of a transmission according to a second embodiment of the present invention,

FIG. 5 is an operation table of friction elements for each shift position of the transmission according to the second embodiment of the present invention.

[Industrial Applications]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a powertrain of an automatic transmission for a vehicle, and more particularly to a powertrain of a vehicular automatic transmission in which stress acting on each member of a planetary gear set is reduced and torque is increased.

[0003]

BACKGROUND ART [0002] In general, a vehicular automatic transmission includes a transmission control unit that automatically controls a transmission ratio according to a running speed of a vehicle and a variation in load.

The transmission control unit controls the plurality of friction elements installed in the gear train to operate or non-operate to select any one of the three elements (sun gear, ring gear, and planet carrier) of the planetary gear as input elements, The number is adjusted.

In order to design a power train capable of substantially thrusting forward 4 speed and 1 reverse speed, one complex planetary gear set and at least five friction elements must be used.

Among these friction elements, the turning radius of the clutch element has a structural constraint that it must be smaller than the turning radius of the output element to be connected to the input shaft and smaller than the turning radius of the reaction force element.

Therefore, the connection structure of the clutch means or the brake means for connecting the respective elements of the planetary gear set to each other is limited.

For this reason, the complex planetary gear set proposed so far has two simple types that connect a planetary carrier and a ring gear and connect another ring gear and another planetary carrier, but also connect a sun gear and a sun gear, The most common type of ring gear is the Simpson type.

Particularly, in the above-described complex planetary gear set, a sun gear or a ring gear is widely used as an input element by being connected to the input shaft of the engine.

[Problems to be solved by the present invention]

However, it has been found that a complex planetary gear set using such a conventional configuration has been used for a considerable period of time, thereby increasing the stress acting on each member of the planetary gear set.

Further, the planetary gear set has a problem in that it has structural limitations in that it has a limitation in size to increase the torque in order to improve the output.

[MEANS FOR SOLVING THE PROBLEM]

SUMMARY OF THE INVENTION The present invention has been made in order to solve the problems of the prior art as described above, and it is an object of the present invention to provide a planetary gear set which can reduce stress acting on each member of a planetary gear set, And to provide a powertrain of an automatic transmission.

In order to achieve the object of the present invention, there is provided a torque converter comprising: a torque converter that receives power from an engine and converts the torque to output the torque to an input shaft;

And a double pinion planetary gear set which is composed of a single pinion planetary gear set which is disposed around the input shaft and in which the ring gear is connected to the power transmitting member by output means and which shares the sun gear with the ring gear of the single pinion planetary gear set, A first friction element disposed between the gear set and the input shaft for selecting the double pinion carrier as an input element, and a second friction element for selecting the singe pinion carrier as a reaction element in operation of the first friction element A third frictional element for selecting the sun gear as a reaction element in operation of the first frictional element and a fourth frictional element for selecting the sun gear as an input element in operation of the first frictional element; With the fasting; A single pinion planetary gear set to which the pinion carrier and the transfer drive gear are connected to receive the output of the peripheral speed portion and to use the ring gear as an input element and the pinion carrier as output means, A third friction element, a fifth friction element for selecting the sun gear of the single pinion planetary gear set as the reaction element during the operation of the first and fourth friction elements, and a fifth friction element for selecting the sun gear of the single- And a sixth friction element that locks the pinion gear and the sun gear of the set as an output element to be locked, thereby providing a powertrain of a vehicular automatic transmission.

[Action]

The double pinion carrier of the peripheral speed multiple planetary gear set of the present invention acts as an input element in the D range and the ring gear acts as an output element to output to the auxiliary speed change portion.

The ring gear of the negative speed change section is used as an input element and the pinion carrier of the single pinion planetary gear set of the negative speed change section is used as an output element to transmit power to the drive shaft via the transfer drive gear.

[Example]

BRIEF DESCRIPTION OF THE DRAWINGS The above and other features and advantages of the present invention will be more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which:

1 is a view showing a power train of a transmission according to a first embodiment of the present invention in which the rotational power of the engine E is torque-converted by the torque converter T and is transmitted to the input shaft 1 of the peripheral speed section 2 And has a structure that can be transmitted.

A compound planetary gear device 5 is disposed on the outer periphery of a portion of the input shaft 1 which extends laterally to the side of the input shaft 1 and is connected to the peripheral speed portion 2 so as to receive the power of the input shaft 1 through the clutch means and the brake means. .

And a second planetary gear unit 5 is disposed to receive the driving force of the peripheral speed unit 2 and to be transmitted to a differential unit (not shown) through a clutch drive unit and a brake unit via a transfer drive gear 7, (4).

The complex planetary gear set 5 of the peripheral speed portion 2 is composed of a combination of the single pinion planetary gear set 6 and the double pinion planetary gear 8, and the single pinion 9 and the double pinion 11 And the ring gear 13 and the sun gear 15 are shared and arranged in parallel.

The ring gear 13 is used as an output means connected to the power transmitting member 17 and capable of outputting to the negative speed change portion 4 through the drive gear 19. [

In order to allow the rotational power of the input shaft 1 to be transmitted to the double pinion carrier 21 of the compound planetary gear set 3, a first friction element C1 (C1) is provided between the input shaft 1 and the double pinion carrier 21, Is installed.

The single pinion carrier 24 and the power transmitting member 25 are connected to each other so that the single pinion carrier 24 is selected as the reaction element at the speed change stage in which the input element is selected. Element B1 is installed.

The transmission housing 27 and the third friction element B2 are connected by connecting the sun gear 15 and the power transmitting member 29 in order to realize another gear stage having the double pinion carrier 27 as an input element, (15) as a reaction force element.

A fourth friction element (not shown) is disposed between the opposite end of the input shaft 1 and the power transmitting member 29 connected to the sun gear 15 to implement another gear stage having the double pinion carrier 21 as an input element. C2 are installed.

The auxiliary speed change section 4 for realizing another speed change stage in which the double pinion carrier 21 is also an input element is arranged so that the driven gear 31 is directly connected to the drive gear 19, And the output element is composed of the input element.

The driven gear 31 is connected to the ring gear 35 by the power transmitting member 33 so that the ring gear 35 of the single speed change gear unit 4 and the single planetary gear set 5 acts as an input element .

A pinion gear 7 is engaged with the inside of the ring gear 35 and connected by a carrier 39. The pinion carrier 39 is connected to a power transmission member 41 via a transmission drive gear 7, And is used as an output means capable of outputting.

The sun gear 43 is meshed with the pinion gear 37 at the center of the pinion carrier 39. The center of the sun gear 43 is rotatably supported by the pinion gears 37, And has a long elongated structure.

Between the rotary shaft 45 of the sun gear 43 and the pinion carrier 39 in order to realize another speed change stage at the speed change stage in which the double pinion carrier 21 of the peripheral speed section 2 is selected as the input element, 43 and the pinion carrier 37 as output elements at the same time.

A fifth friction element (not shown) which is selectively operated between the rotary shaft 45 of the sun gear 43 and the transmission housing 27 to select the sun gear 43 as a reaction element is selectively operated in the reverse (R) range and the forward B3).

On the other hand, the first, fourth and sixth friction elements C1, C2 and C3 described above are composed of a multi-plate clutch as a clutch means and the second, third and fifth friction elements B1, B2, And a band brake as a means.

The torque converter (T) is usually provided with a damper clutch (D) for increasing the power transmission efficiency.

Although the configuration of the first embodiment includes an example in which the auxiliary speed change portion is included to implement the reverse (R) first speed and the forth (D) fourth speed, the present invention is not limited thereto. It is also possible to configure the second embodiment by omitting the auxiliary speed change portion to implement the third speed forward (D) and the reverse speed (R) first speed.

The transmission according to the present invention thus constructed is configured such that any one of the three elements of the planetary gear set is input as the input and the other element Is selected as a reaction force element, and the following forward speed 4 speed and reverse speed 1 speed ratio are outputted.

The range-specific operation table relating to the friction element for which operation and non-operation are selected by the transmission control unit is shown in FIG.

3 is a graph explaining the speed ratio when the powertrain is controlled as shown in the table of the operating elements and shifting is performed by the lever analysis method. The left end of the lever L, which indicates the peripheral speed portion 2, The pinion carrier 24 is located at a position adjacent to the first node N1 and the ring gear 13 is located at the third node N2, (N3), and the right end is indicated by a fourth node N4 in which the double pinion carrier 21 exists.

The left end of the lever 1 indicating the auxiliary speed change section 4 is connected to the fifth node N5 where the ring gear 35 of the single pinion planetary gear set 5 exists and the adjacent position is set to the single pinion carrier 39 And the seventh node N7 in which the sun gear 43 is present at the right end of the sixth node N6.

The first friction element C1 of the peripheral speed portion 2 in which the power of the engine is inputted is operated to select the double pinion carrier 21 as the input element and the second friction element B1 is selected as the input element, To select the single pinion carrier 24 as a reaction force element.

The fourth node N4 corresponding to the double pinion carrier 21 becomes the input end and the second node N2 corresponding to the single pinion carrier 24 becomes the fixed end and the speed input of the fourth node N4 The line L2 is connected to the second node N2 at an arbitrary position on the line L1 and a line obtained by connecting the straight line L2 and the third node N3, Speed output speed line L3.

In the second speed, the first friction element C1 is continuously operated to continuously select the double pinion carrier 21 as the input element. At the same time as the second friction element B1 is disengaged, the third friction element B2 To select the sun gear 15 as a reaction force element.

Therefore, the fourth node N4 becomes the input end and the first node N1 corresponding to the sun gear 15 becomes the fixed end and the fourth node N4 becomes the fixed end, since the double pinion carrier 21 continues to be the input element. A line L4 obtained by connecting the first node N1 and the straight line L4 at an arbitrary position on the speed input line L1 of the first speed line L1 and connecting the straight line L4 to the third node N3, Speed output speed line L5 of the second speed.

Further, in the third speed, the first friction element C1 is continuously operated to continuously select the double pinion carrier 21 as the input element, and the third friction element B2 is released, and at the same time, To select the sun gear 15 as an input element.

Therefore, the fourth node N4 corresponding to the double pinion carrier 21 and the first node N1 corresponding to the sun gear 15 serve as input ends, so that the ends of these input speed lines L1, And a line obtained by connecting the straight line L7 in the vertical direction at the third node N3 serving as the output terminal becomes the third peripheral speed line output speed line L8.

The rotational power of the first, second and third speeds obtained in the peripheral speed section 2 is decelerated again in the auxiliary speed change section 4. In the auxiliary speed change section 4, the drive gear 19 and the driven gear 31 And the fifth node N5 corresponding to the ring gear 35 of the single pinion planetary gear set 5 connected by the power transmitting member 33 are fixed by the fifth friction element B3, The seventh node N7 corresponding to the sun gear 43 of the single pinion planetary gear set 5 becomes a fixed end.

And the sixth node N6 corresponding to the single pinion carrier 39 of the single pinion planetary gear set 5 constituting the auxiliary speed change section 4 becomes the output end.

The fifth node N5 is connected to the input speed line L3 so that the third node N3 has the same size as the peripheral speed line L3, L5, L8 of the third node N3, A line obtained by connecting the straight line L9 (L10) L11 obtained by connecting the seventh node N7 and the seventh node N7 from the sixth node N6 to the sixth node N6 is output from the negative speed change section 4 The first, second and third speed output lines L12, 13 and 14, respectively.

Therefore, torque is increased as the output from the peripheral speed portion 2 is decelerated again in the negative speed change portion 4.

Then, in the fourth speed, the operation of the fifth friction element B3 of the negative speed change portion 4 is stopped and the sixth friction element C3 is operated in the third speed state of the peripheral speed portion 2, The sun gear 43 of the sun gear 5 is locked with the pinion carrier 39 of the single pinion planetary gear set 5 so that the input is made to the seventh node N7 corresponding to the sun gear 43, A line obtained by connecting the straight line L16 connecting the end of the speed input line L8 of the fifth node N5 and the sixth node N6 at the shortest distance is connected to the fourth output line L17, .

Therefore, the output torque of the engine is 1: 1, so that the torque of the engine can be maximized.

In the reverse range, the fourth friction element C2 of the peripheral speed section 2 is operated to select the sun gear 15 as the input element, and the second friction element B1 is operated to operate the single pinion carrier 24) is selected as the reaction force element.

In the auxiliary speed change section 2, the fifth friction element B3 is operated to select the sun gear 43 of the single pinion planetary gear set 5 as a reaction force element.

Therefore, the first node N1 corresponding to the sun gear 15 of the peripheral speed section 2 becomes the input end and the second node corresponding to the single pinion carrier 24 becomes the fixed end. Therefore, the straight line L18 And a third node N3 serving as an output terminal are connected to each other vertically downward to form a reverse output line L19 of the peripheral speed section 2. [

The output obtained from the peripheral speed section 2 is input to the fifth node N5 of the negative speed change section 4 in the same size and reverse direction and the seventh node N7 is connected to the fixed end, The line connecting the straight line L20 and the sixth node N6 becomes the final reverse output line L21.

[Effects of the Invention]

The powertrain of the automatic transmission of the present invention can reduce the stress acting on the sun gear and the ring gear by using the double pinion carrier as the input element in the forward range state and increase the torque at the same size, In order to achieve the same torque, weight reduction can be realized even if the size is reduced.

Claims (3)

A torque converter that receives power from an engine and converts the torque to output the torque to an input shaft; And a double pinion planetary gear set which is composed of a single pinion planetary gear set which is disposed around the input shaft and in which the ring gear is connected to the power transmitting member by output means and which shares the sun gear with the ring gear of the single pinion planetary gear set, A first friction element disposed between the first pinion carrier and the input shaft for selecting the double pinion carrier as an input element and a second friction element for selecting the single pinion carrier as a reaction element during operation of the first friction element, A third frictional element for selecting the sun gear as a reaction element in operation of the first frictional element and a fourth frictional element for selecting the sun gear as an input element in operation of the first frictional element; With the fasting; A single pinion planetary gear set to which the pinion carrier and the transfer drive gear are connected to receive the output of the peripheral speed portion and to use the ring gear as an input element and the pinion carrier as output means, A third friction element, a fifth friction element for selecting the sun gear of the single pinion planetary gear set as the reaction element during the operation of the first and fourth friction elements, and a fifth friction element for selecting the sun gear of the single- And a sixth friction element for selecting a pinion gear and a sun gear of the set as an output element so as to be locked. The powertrain of an automatic transmission for a vehicle according to claim 1, characterized in that the first, fourth and sixth friction elements comprise a multi-plate clutch as a clutch means. The powertrain of a vehicular automatic transmission as claimed in claim 1, wherein the second, third, and fifth friction elements comprise band brakes as brake means.