KR0158170B1 - 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 gear set and the input shaft for selecting the double pinion carrier as an input element and a second friction element for selecting the single pinion as a reaction element in operation of the first friction element, A first one-way clutch disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as the reaction element roll in operation of the first friction element, A second one-way clutch extending from the extension of the power transmitting member to which the sun gear and the third friction element are connected, A seventh frictional element installed to select a sun gear as a reaction element between the two-way clutch and the transmission housing, and a fourth frictional element disposed between the two-way clutch and the transmission housing for selecting a sun gear as an input 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 a reaction element in operation of the first and fourth friction elements, and a fifth friction element for intervening between the sun gear shaft of the single pinion planetary gear set and the transmission housing And a sixth friction element for selecting the pinion gear and the sun gear of the single-pinion planetary gear set as the output elements for locking during operation of the first and fourth friction elements, And a power transmission of the vehicular automatic transmission including the auxiliary transmission portion.

Description

Automotive powertrain powertrain

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

FIG. 2 is an operating table of friction elements for each shift position of the transmission according to the first embodiment of the present invention; FIG.

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

FIG. 4 is a view showing a powertrain of a transmission according to a second embodiment of the present invention; FIG.

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

6 is a view showing a power train of a transmission according to a third embodiment of the present invention.

FIG. 7 is an operating table of friction elements for each shift position of the transmission according to the third embodiment of the present invention; FIG.

FIG. 8 is a view showing a power train of a transmission according to a fourth embodiment of the present invention; FIG.

FIG. 9 is an operation table of friction elements for each gear position of the transmission according to the fourth embodiment of the present invention; FIG.

[Industrial Applications]

The present invention relates to a power train of an automatic transmission for a vehicle, and more particularly, to a power train of an automatic transmission for a vehicle, which reduces stress acting on each member of the planetary gear set and increases torque at the same magnitude, To a power train of a vehicular automatic transmission for improving a shift feeling at the time of shifting from third speed to third speed.

[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-operating to select any one of the three elements (sun gear, ring gear, and planet carrier) of the planetary gear as input elements, .

In order to design a powertrain capable of outputting substantially the forward speed of the fourth forward speed and the reverse speed of the first reverse speed, one complex planetary gear set and at least five friction elements must be used.

Of 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.

In such a vehicular automatic transmission, a transmission is formed as a peripheral speed portion and a negative speed portion in order to output a speed ratio in multiple stages, and a plurality of clutch means and brake means are disposed in place in order to facilitate shifting control.

[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.

In addition, in the case of an automatic transmission constructed of the above-mentioned planetary gear set, the speed change from the third speed to the fourth speed in the range from the first speed to the second speed of the D range and from the second range to the second speed, The shifting is made only by the operation and the non-operation control at the time of shifting.

[MEANS FOR SOLVING THE PROBLEM]

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above problems occurring in the prior art, and it is an object of the present invention to improve the output by reducing the stress acting on each member of the planetary gear set, , The D range and the second range are switched to the first speed, and the transmission feeling is improved by the action of the one-way clutch at the time of shifting from the first speed to the second speed, from the second speed to the third speed, To provide a powertrain of the 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 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 first one-way clutch disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing; a third friction element disposed on one side of the second friction element for selecting the sun gear as a reaction element during operation of the first friction element; A second one-way clutch extending from the power transmission member to which the sun gear and the third friction element are connected and extending on the extended line, A seventh frictional element installed to select a sun gear as a reaction element between the second one-way clutch and the transmission housing, and a fourth frictional element for selecting the sun gear as an input element in operation of the first frictional element With the surrounding inferno; 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 a reaction element in operation of the first and fourth friction elements, and a fifth friction element for intervening between the sun gear shaft of the single pinion planetary gear set and the transmission housing And a sixth friction element for selecting the pinion gear and the sun gear of the single-pinion planetary gear set as the output elements for locking during operation of the first and fourth friction elements, A powertrain of a vehicular automatic transmission including an auxiliary speed change section.

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 friction element and the input shaft for selecting the double pinion carrier as an input element and a second friction element for selecting a single pinion carrier as a reaction element in operation with the first friction element, A first friction element disposed at one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as a reaction element during operation of the first friction element, A fourth friction element for selecting the sun gear as an input element during operation of the first friction element; 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.

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 first one-way clutch disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing; a third friction element disposed on one side of the second friction element for selecting the sun gear as a reaction element during operation of the first friction element; A second one-way clutch extending from the power transmission member to which the sun gear and the third friction element are connected and extending on the extended line, A seventh frictional element installed to select a sun gear as a reaction element between the second one-way clutch and the transmission housing, and a fourth frictional element for selecting the sun gear as an input element during operation of the first frictional element With the surrounding inferno; 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.

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 first friction element disposed at one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as a reaction element during operation of the first friction element, A fourth friction element for selecting the sun gear as an input element during operation of the first friction element; 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 a reaction element in operation of the first and fourth friction elements, and a fifth friction element for intervening between the sun gear shaft of the single pinion planetary gear set and the transmission housing And a sixth friction element for selecting a pinion gear and a sun gear of the single pinion planetary gear set as an output element to be locked during operation of the first and fourth friction elements, The powertrain of the vehicular automatic transmission including the power transmission portion is provided.

[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 set 3 is disposed on the outer periphery of a portion of the input shaft 1 that 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. .

The single planetary gear set 5 is disposed to receive the driving force of the peripheral speed portion 2 and is transmitted to the differential gear (not shown) through the clutch drive means and the brake means via the clutch drive means 7, (4).

The complex planetary gear set 3 of the peripheral speed portion 2 is constituted by 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.

And a second friction element B1 is provided between the transmission housing 27 and the single pinion carrier 24 for selecting the single pinion carrier 24 as a reaction element at the speed change stage in which the input element is selected .

A first one-way clutch F1 is provided between the single pinion carrier 24 and the transmission housing 27 so that the single pinion carrier 24 is rotated in the rotational direction of the input shaft 1. [

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 second one-way clutch F2 is provided by extending the power transmitting member 29 in the axial direction and a seventh friction element B4 is provided between the second one-way clutch F2 and the transmission housing 27 Is installed.

The second one-way clutch F2 is freely rotatable in the rotational direction of the input shaft 1 and is not rotated in the opposite direction.

Of course, the second one-way clutch F2 is operated as described above when the seventh friction element B4 is actuated.

The second one-way clutch F2 and the seventh friction element B4 are for allowing the sun gear 15 to act as a reaction force element.

A fourth friction element (not shown) is connected between one 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 37 is engaged with the inside of the ring gear 35 and connected with a carrier 39. The pinion carrier 39 is connected to the transfer drive gear 7 side by a power transmitting member 41, 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 third one-way clutch F3 is provided between the rotation shaft 45 of the sun gear 43 and the transmission housing 27 of the single pinion planetary gear set 5 so as to rotate in the rotation direction of the engine ought.

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).

The first, fourth, and sixth friction elements C1, C2, and C3 described above are composed of a multi-plate clutch as the clutch means and the second, third, fifth, and fourth friction elements B1, B2, (B4) is constituted by a band brake as a braking means.

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

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.

A range-specific operation table relating to the friction elements 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.

First, in the parking (P) range and the neutral (N) range, only the fifth friction element B3 operates in this range as a stop or stopping range of the vehicle. However, So that no friction element is activated and power transmission to the peripheral speed section 2 is not performed and the parking springs engage the parking sprocket gear by a parking lever (not shown) by the driver , The rotation of the output shaft is stopped.

The first forward speed D of the peripheral speed section 2 operates the first friction element C1 of the peripheral speed section 2 to which the engine power is inputted to select the double pinion carrier 21 as the input element, And the one-way clutch F1 is operated to select the single pinion carrier 24 as the reaction force element.

Therefore, the fourth node N4 corresponding to the double pinion carrier 21 becomes the input end,

The second node N2 corresponding to the single pinion carrier 24 becomes the fixed end and is connected to the second node N2 at the arbitrary position of the speed input line L1 of the fourth node N4 by a straight line L2 And a line obtained by connecting the straight line L2 in the vertical direction at the third node N3 serving as the output terminal becomes the first peripheral speed line output speed line L3.

Then, in the second speed, the first friction element C1 is continuously operated to continuously select the double pinion carrier 21 as the input element, and when the seventh friction element B4 is operated, the second one-way clutch F2, So that the sun gear 15 is selected as the 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 seventh friction element B4 is released, and at the same time, To select the sun gear 15 as an input element.

At this time, even if the seventh frictional element B4 is released due to the hydraulic pressure control and the correct time can not be set, the second one-way clutch F2 is freewheeling in the same direction as the input shaft 1, .

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 is the input end and the reaction force of the third one way clutch F3 The seventh node N7 corresponding to the sun gear 43 of the single pinion planetary gear set 5 fixed by the first pinion gear set 5 becomes a fixed end.

The third one-way clutch F3 is capable of reducing the shift shock by operating with a reaction force preferentially at the time of operating control of the fifth friction element B4.

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 53 of the single pinion planetary gear set 5 as a reaction 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 fixed, The line connecting the sixth node N20 and the sixth node N6 becomes the final reverse output line L12.

In addition, the first and third speed ranges of the two ranges are the same as the first and third speed ranges of the D range.

In the second range 2, the sun gear 15 acts as a reaction force element by the operation of the third friction element B2 to form the speed line L5 in the D range 2.

Subsequently, the operation in the auxiliary speed change section 4 has the same action as that in the D range 2.

However, when the torque of the driving wheel becomes larger than the torque of the engine E, the reverse driving force is transmitted to the engine E via the sun gear 15, thereby obtaining the effect of the engine brake.

The first speed of the L range is different from the first speed range in that the first friction element B1 is operated to select the single pinion carrier 24 as a reaction force element and the operation is the same as that of the D range 1. However, The effect of the engine brake is obtained.

And the second L range 2 has the same action and effect as the second range 2.

4 shows a power train of a transmission according to a second embodiment of the present invention. In the first embodiment, the second one-way clutch F2 of the peripheral speed section 2 and the seventh friction element (B4) and the third one-way clutch F3 of the auxiliary speed change section 4 are omitted.

The components other than the above-described components are arranged in the same manner as in the first embodiment.

The transmission according to the second embodiment of the present invention is made up of the operating element table shown in FIG. 5, and the same operation as that of the first embodiment is substituted for the first embodiment and description thereof is omitted.

The result of the lever analysis according to the operating element table of the above-described scheme is the same as that of the third embodiment, and therefore, it is also omitted.

First, the parking (P) range and the neutral (N) range are the same as those of the first embodiment, and thus the description of the first embodiment is substituted.

The first friction element C1 of the peripheral speed portion 2 to which the engine power is input is selected to select the double pinion carrier 21 as the input element and the one-way clutch F1 is selected as the input element, And selects the single pinion carrier 24 as the 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.

Then, in the second 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 operated to select the sun gear 15 as the reaction 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 a fifth node N5 corresponding to the ring gear 35 of the single pinion planetary gear set 5 connected by the power transmitting member 33 is an input end and 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 section 2 is decelerated again in the auxiliary speed change section 4.

Then, in the fourth speed, the operation of the fifth friction element B3 of the negative speed change portion 4 is stopped in the third speed state of the peripheral speed portion 2, The sixth frictional element C3 is operated so that the sun gear 43 of the single pinion planetary gear device 5 is locked with the pinion carrier 39 of the single pinion planetary gear device 5 and the sun gear 43 of the seventh An input is also made to the node N7 so that the straight line L16 and the sixth node N6 connecting the speed input line L15 thereof to the end of the speed input line L8 of the fifth node N5, And the line obtained by connecting at the distance becomes the output line L17 of the fourth speed.

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 vertically downwardly connected to 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.

In addition, two of the first, second, third, and L ranges of the two ranges have the same action and effect with the first, second, third, and second gears of the D range.

The first speed of the L range is different from the first speed range in that the single pinion carrier 24 is selected as the reaction force element by operating the second friction element B1, and the same effect as the D range 1 speed is obtained, but the engine brake effect is additionally obtained .

In the second embodiment described above, the shifting impact is reduced by the action of the first one-way clutch F1 at the time of shifting to D and the range of the second range 1, and the number of parts is reduced by reducing the friction factor compared with the first embodiment And it is possible to make a more compact production.

6 is a configuration diagram of a transmission according to a third embodiment of the present invention. The configuration of the peripheral speed section 2 is the same as that of the first embodiment described above. However, in the auxiliary speed change section 4, And the one-way clutch F3 is omitted.

The above-described third embodiment is also similar to the third embodiment in that the result of the lever analysis by the operating element table shown in FIG. 7 is the same as that of the third embodiment.

In the transmission according to the third embodiment of the present invention, the parking (P) range and the neutral (N) range are the same as those of the first and second embodiments.

Further, the forward speed (D) formed in the peripheral speed section (2) is operated in the same manner as the first embodiment, and a detailed description thereof will be omitted.

As described in the first embodiment, 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, 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 the input ends, The seventh node N7 corresponding to the sun gear 43 of the single pinion planetary gear set 5 fixed by the element B3 becomes a fixed end.

And the sixth node N6 corresponding to the single pinion carrier 39 of the single pinion planetary gear set 5 of the single pinion planetary gear set 5 constituting the auxiliary speed change portion 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 because the output from the peripheral speed section 2 is decelerated again in the auxiliary speed change section 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, .

Also, the reverse range (R) range is the same as that of the first embodiment, and thus description thereof is omitted.

The function and effect of the above-described configuration is the same as in the second embodiment, but in the second embodiment, the shift shock is reduced by the action of the first one-way clutch F1 during the shift from D to the first range.

As described above, according to the third embodiment of the present invention, in the first embodiment, the shift shock is reduced by the action of the one-way clutch in all the shift ranges, while the second, third, The shift shock is reduced.

Compared to the first embodiment, by reducing the friction factor, the number of parts can be reduced, and at the time of manufacturing the transmission, space can be secured and the degree of freedom of design can be increased.

FIG. 8 is a configuration diagram of a transmission device according to a fourth embodiment of the present invention, in which the second one-way clutch and the seventh friction element are omitted in the configuration of the first embodiment.

The transmission according to the present invention is operated in accordance with the operating element table of FIG. 9, and the results of the lever analysis method according to the operating element table are the same as those of the third embodiment. It is replaced by the description of the first embodiment.

First, the parking (P) range and the neutral (N) range are also the same as those in the first embodiment, and therefore, the description is replaced with the description of the first embodiment.

The first friction element C1 of the peripheral speed portion 2 to which the engine power is input is selected to select the double pinion carrier 21 as the input element and the one-way clutch F1 is selected as the input element, And selects the single pinion carrier 24 as the 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.

Then, in the second speed, the first friction element C1 is continuously operated to continuously select the double pinion carrier carrier 21 as the input element, and the third friction element B2 is operated to select the sun gear 15 as the reaction element do.

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 of the speed input line L1 of the first speed line L1 and connecting the straight line L4 to the third node N3 serving as the output stage, 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 and the third node N3 serving as the output end in the vertical direction is the third speed peripheral speed section 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. Since the auxiliary speed change section 4 has the same operational effect as that of the first embodiment A detailed description thereof will be omitted.

However, in the first embodiment, the structure is such that the shift shock is reduced at all gear positions. However, in the fourth embodiment according to the present invention, the action of the one-way clutch causes D to shift from the second range to the second range, Thereby reducing the shift shock.

In the backward range, the same effect as that of the first embodiment is obtained, and the two first, second, third, and L ranges of the two ranges are equivalent to the first, second, third, and second ranges of the D range .

The first one of the L ranges is different from the first one in that the single pinion carrier 24 is selected as the reaction force element by operating the second friction element B1, and the action is the same as that of the D range 1, but the effect of the engine brake is obtained.

[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.

When the first one-way clutch acts as a reaction force element only in the D, 2 range 1, and when the third-speed range is changed from the second range to the D range and the fourth-speed range from the third range to the fourth range, the second one- It acts only as a reaction force element, and in the other range, it becomes a freewheeling state, so that a shift shock is reduced and a transmission feeling is improved.

Claims (12)

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 first one-way clutch disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing; a third friction element disposed on one side of the second friction element for selecting the sun gear as a reaction element during operation of the first friction element; A second one-way clutch extending from the power transmission member to which the sun gear and the third friction element are connected and extending on the extended line, A seventh frictional element installed to select a sun gear as a reaction element between the second one-way clutch and the transmission housing, and a fourth frictional element for selecting the sun gear as an input element in operation of the first frictional element With the surrounding inferno; 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 a reaction element in operation of the first and fourth friction elements, and a fifth friction element for intervening between the sun gear shaft of the single pinion planetary gear set and the transmission housing And a sixth friction element for selecting the pinion gear and the sun gear of the single-pinion planetary gear set as the output elements for locking during operation of the first and fourth friction elements, A powertrain of a vehicular automatic transmission including an auxiliary speed change section. 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. 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 friction element 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 in operation, A one-way clutch disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as a reaction element during operation of the first friction element, A fourth friction element for selecting the sun gear as an input element when the first friction element is in operation; 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 as an output element for locking. 5. The powertrain of an automatic transmission for a vehicle according to claim 4, characterized in that the first, fourth and sixth friction elements comprise a multi-plate clutch as a clutch means. 5. The powertrain of an automatic transmission for a vehicle according to claim 4, wherein the second, third, and fifth friction elements comprise band brakes as break means. A torque converter that receives power from an engine and converts the torque to output the torque to an input shaft; A double pinion carrier planetary gear set including a single pinion planetary gear set disposed around the input shaft and having a ring gear connected to a power transmitting member as output means, and a double pinion carrier planetary gear that shares the sun gear with the single pinion planetary gear set; A second friction element for selecting the single pinion carrier as a reaction force element in operation of the first friction element, and a second friction element for selecting the double pinion carrier as an input element, A first friction element disposed on one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as a reaction element during operation of the first friction element, A second one-way clutch extending from the power transmission member to which the third friction element is connected and extending on the extended line, A seventh frictional element installed to select a sun gear as a reaction element between the two-way clutch and the transmission housing, and a fourth frictional element disposed between the two-way clutch and the transmission housing for selecting a sun gear as an input element With the fasting; A single pinion planetary gear set in which a pinion carrier and a transfer drive gear are connected to receive an output of the peripheral speed portion as a ring gear as an input element and a pinion carrier as an output means, A fifth friction element for selecting the sun gear of the single pinion planetary gear set as a reaction element in operation of the first and third friction elements, and a fifth friction element for selecting the single pinion planetary gear set And a sixth friction element for selecting a pinion gear and a sun gear as an output element for locking. 8. The powertrain of a vehicular automatic transmission as set forth in claim 7, wherein the first, fourth, and sixth friction elements comprise a multi-plate clutch as a clutch means. 8. The powertrain of an automatic transmission for a vehicle according to claim 7, wherein the second, third, and fifth friction elements comprise a band brake as a brake means. 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 first friction element disposed at one side of the second friction element and interposed between the single pinion carrier and the transmission housing, a third friction element for selecting the sun gear as a reaction element during operation of the first friction element, A fourth friction element for selecting the sun gear as an input element during operation of the first friction element; 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 a reaction element in operation of the first and fourth friction elements, and a fifth friction element for intervening between the sun gear shaft of the single pinion planetary gear set and the transmission housing And a sixth friction element for selecting a pinion gear and a sun gear of the single pinion planetary gear set as an output element to be locked during operation of the first and fourth friction elements, A power train of an automatic transmission for a vehicle. 11. The powertrain of a vehicular automatic transmission as set forth in claim 10, wherein the first, fourth, and sixth friction elements comprise clutch plates as clutch means. 11. The powertrain of an automatic transmission for a vehicle according to claim 10, wherein the second, third, and fifth friction elements comprise a band brake as a brake means.