Planetary gear train of automatic transmission for vehicle

The present application claims priority to Korean Patent Application No. 10-2018-0101599, filed Aug. 28, 2018, the entire contents of which is incorporated herein for all purposes by this reference.

The present invention relates to a planetary gear train of an automatic transmission for a vehicle.

Multi-staging of a transmission aims to improve the fuel efficiency of a vehicle by facilitating operation of an engine in a more efficient region over the entire driving range of a vehicle, and to improve the driving performance of the vehicle by rapidly providing a more suitable gear ratio in a response to a driver's demand.

Therefore, to achieve the above-mentioned effect of multi-staging of the transmission as described above, it is preferable for an inter-stage ratio, which is a difference in gear ratio between adjacent shifting stages, to be appropriately secured while increasing a gear ratio span, which is the total gear ratio range which may be provided by the transmission, and for the inter-stage ratio to change in as linear a manner as possible.

The information included in this Background of the Invention section is only for enhancement of understanding of the general background of the invention and may not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

Various aspects of the present invention are directed to providing a planetary gear train of an automatic transmission for a vehicle, which is configured for providing 10 forward shifting stages and a reverse stage and ensuring sufficient durability due to the relatively low torque which is borne by components thereof while ensuring a wide gear ratio span, an inter-stage ratio of a predetermined level or more, and linearity of the inter-stage ratios.

To achieve the above-described aspect, a planetary gear train of an automatic transmission for a vehicle may include: an input shaft configured to receive power; an output shaft configured to output power; a first planetary gear set having first, second, and third rotation elements; a second planetary gear set having fourth, fifth, and sixth rotation elements; a third planetary gear set having seventh, eighth, and ninth rotation elements; a fourth planetary gear set having tenth, eleventh, and twelfth rotation elements; a fifth planetary gear set having thirteenth, fourteenth, and fifteenth rotation elements; a first shaft connected to the first rotation element and to the input shaft; a second shaft connected to the fourteenth rotation element and to the output shaft; a third shaft connected to the third rotation element; a fourth shaft connected to the sixth rotation element, to the eleventh rotation element, and to the fifteenth rotation element; a fifth shaft connected to the seventh rotation element and to the thirteenth rotation element; a sixth shaft connected to the eighth rotation element and to the twelfth rotation element; a seventh shaft connected to the second rotation element and to the fourth rotation element; an eighth shaft connected to the fifth rotation element and to the ninth rotation element; and a ninth shaft connected to the tenth rotation element.

The planetary gear train may include six coupling elements configured to selectively connect two shafts among the first to ninth shafts or the transmission housing and a shaft among the first to ninth shafts, and three coupling elements among the six coupling elements may be operatively controlled such that a specific shifting stage among the forward and reverse shifting stages is implemented.

The six coupling elements may include: three clutches configured to interconnect two shafts among the first to ninth shafts; and three brakes configured to selectively connect a shaft, which is not connected to the input shaft or the output shaft among the first to ninth shafts, to the transmission housing.

The six coupling elements may include: a first clutch mounted between the first shaft and the fifth shaft; a second clutch mounted between the first shaft and the sixth shaft; a third clutch mounted between the third shaft and the sixth shaft; a first brake mounted between the seventh shaft and the transmission housing; a second brake mounted between the eighth shaft and the transmission housing; and a third brake mounted between the ninth shaft and the transmission housing.

The first, second, and third rotation elements may include a first sun gear, a first planet carrier, and a first ring gear; the fourth, fifth, and sixth rotation elements may include a second sun gear, a second planet carrier, and a second ring gear; the seventh, eighth, and ninth rotation elements may include a third sun gear, a third planet carrier, and a third ring gear; the tenth, eleventh, and twelfth rotation elements may include a fourth sun gear, a fourth planet carrier, and a fourth ring gear; and the thirteenth, fourteenth, and fifteenth rotation elements may include a fifth sun gear, a fifth planet carrier, and a fifth ring gear.

The first to fifth planetary gear sets may be mounted in the order of the first, second, third, fourth, and fifth planetary gear sets from one side to the other side thereof.

Furthermore, the planetary gear train of the automatic transmission for a vehicle according to an exemplary embodiment of the present invention may include: a first planetary gear set having three rotation elements, one of which is connected to an input shaft; a second planetary gear set having three rotation elements, one of which is continuously connected to any one of the first to third rotation elements of the first planetary gear set; a third planetary gear set having three rotation elements, one of which is connected to the input shaft in a disconnectable manner by a first clutch, another one of which is connected to two rotation elements of the first planetary gear set in a disconnectable manner by a second clutch and a third clutch, respectively, and a remaining one of which is continuously connected to one rotation element of the second planetary gear set; a fourth planetary gear set having three rotation elements, one of which is continuously connected to any one of the first to third rotation elements of the third planetary gear set; a fifth planetary gear set having three rotation elements, one of which is continuously connected to one rotation element of the third planetary gear set, another one of which is connected to the output shaft, and a remaining one of which is continuously connected to one rotation element of the fourth planetary gear set; a first brake mounted to restrain rotation of the rotation element which is continuously connected to the rotation element of the first planetary gear set, among the first to third rotation elements of the second planetary gear set; a second brake mounted to restrain rotation of the rotation element which is continuously connected to the rotation element of the third planetary gear set, among the first to third rotation elements of the second planetary gear set; and a third brake mounted to restrain rotation of the remaining rotation element, which is not any of the other rotation elements, among the first to third rotation elements of the fourth planetary gear set.

The rotation element of the first planetary gear set, which is connected to the input shaft, may be a first rotation element; a first rotation element of the second planetary gear set may be continuously connected to a second rotation element of the first planetary gear set; a first rotation element of the third planetary gear set may be connected to the input shaft in a disconnectable manner, a second rotation element of the third planetary gear set may be connected to each of the first rotation element and the third rotation element of the first planetary gear set in a disconnectable manner, and a third rotation element of the third planetary gear set may be continuously connected to the second rotation element of the second planetary gear set; the third rotation element of the fourth planetary gear set may be continuously connected to the second rotation element of the third planetary gear set; and a first rotation element of the fifth planetary gear set may be continuously connected to the first rotation element of the third planetary gear set, a second rotation element of the fifth planetary gear set may be directly connected to the output shaft, and a third rotation element of the fifth planetary gear set may be continuously connected to the second rotation element of the fourth planetary gear set.

The first rotation element of the first planetary gear set may be a first sun gear, the second rotation element of the first planetary gear set may be a first planet carrier, and the third rotation element of the first planetary gear set may be a first ring gear; the first rotation element of the second planetary gear set may be a second sun gear, the second rotation element of the second planetary gear set may be a second planet carrier, and the third rotation element of the second planetary gear set may be a second ring gear; the first rotation element of the third planetary gear set may be a third sun gear, the second rotation element of the third planetary gear set may be a third planet carrier, and the third rotation element of the third planetary gear set may be a third ring gear; the first rotation element of the fourth planetary gear set may be a fourth sun gear, the second rotation element of the fourth planetary gear set may be a fourth planet carrier, and the third rotation element of the fourth planetary gear set may be a fourth ring gear; and the first rotation element of the fifth planetary gear set may be a fifth sun gear, the second rotation element of the fifth planetary gear set may be a fifth planet carrier, and the third rotation element of the fifth planetary gear set may be a fifth ring gear.

The first brake may be mounted to restrain rotation of the first planet carrier of the first planetary gear set and the second sun gear of the second planetary gear set, the second brake may be mounted to restrain rotation of the second planet carrier of the second planetary gear set, and the third brake may be mounted to restrict rotation of the fourth sun gear of the fourth planetary gear set.

The first clutch may be mounted to connect the third sun gear of the third planetary gear set and the input shaft in a disconnectable manner, the second clutch may be mounted to the third planet carrier of the third planetary gear set and the first sun gear of the first planetary gear set in a disconnectable manner, and the third clutch may be mounted to connect the third planet carrier of the third planetary gear set and the first ring gear of the first planetary gear set in a disconnectable manner.

The input shaft and the output shaft may be mounted concentrically, and the first to fifth planetary gear sets may be mounted in the order of the first planetary gear set, the second planetary gear set, the third planetary gear set, the fourth planetary gear set, and the fifth planetary gear set in a direction from the input shaft toward the output shaft.

Furthermore, the planetary gear train of the automatic transmission for a vehicle according to an exemplary embodiment of the present invention may include: a first planetary gear set, a second planetary gear set, a third planetary gear set, a fourth planetary gear set, and a fifth planetary gear set, each of which may include three rotation elements; six coupling elements configured to provide a variable frictional force; and nine shafts connected to the rotation elements of the planetary gear sets.

The first shaft is directly connected to the first rotation element of the first planetary gear set and to the input shaft, the second shaft is directly connected to the second rotation element of the fifth planetary gear set and to the output shaft, the third shaft is directly connected to the third rotation element of the first planetary gear set, the fourth shaft is directly connected to the third rotation element of the second planetary gear set, to the second rotation element of the fourth planetary gear set, and to the third rotation element of the fifth planetary gear set, the fifth shaft is directly connected to the first rotation element of the third planetary gear set and to the first rotation element of the fifth planetary gear set, the sixth shaft is directly connected to the second rotation element of the third planetary gear set and to the third rotation element of the fourth planetary gear set, and the remaining three shafts are mounted to be configured for being fixed to the transmission housing.

The remaining three shafts, which are configured for being fixed to the transmission housing, may include the seventh shaft, the eighth shaft, and the ninth shaft, the seventh shaft may be directly connected to the second rotation element of the first planetary gear set and to the first rotation element of the second planetary gear set, the eighth shaft may be directly connected to the second rotation element of the second planetary gear set and to the third rotation element of the third planetary gear set, and the ninth shaft may be directly connected to the first rotation element of the fourth planetary gear set.

Among the six coupling elements, the first clutch may be mounted between the first shaft and the fifth shaft, the second clutch may be mounted between the first shaft and the sixth shaft, the third clutch may be mounted between the third shaft and the sixth shaft, the first brake may be mounted between the seventh shaft and the transmission housing, the second brake may be mounted between the eighth shaft and the transmission housing, and the third brake may be mounted between the ninth shaft and the transmission housing.

The first to fifth planetary gear sets may be mounted in the order of the first planetary gear set, the second planetary gear set, the third planetary gear set, the fourth planetary gear set, and the fifth planetary gear set in the axial direction of the input shaft and the output shaft.

The rotation elements of each of the first to fifth planetary gear sets may be mounted in the order of the first rotation elements, the second rotation elements, and the third rotation elements toward the radially external side from the rotation center.

A planetary gear train of an automatic transmission for a vehicle according to an exemplary embodiment of the present invention forms shifting stages of 10 forward speeds and 1 reverse speed and has a gear ratio span of 9.0. Thus, the fuel efficiency of the vehicle may be improved by making it possible to drive the engine mainly in a more efficient region.

Furthermore, according to an exemplary embodiment of the present invention, it is possible to achieve the minimum inter-stage ratio of 1.192 or more and linearity in the change of the inter-stage ratio according to the change of the shifting stage. Thus, vehicle acceleration, the sense of the sense of rhythm of engine speed, and the like before and after shifting may be improved, so that the driving performance of the vehicle may be maximized.

Furthermore, according to an exemplary embodiment of the present invention, it is possible to ensure sufficient durability due to the relatively low torque which is borne by components while ensuring a wide gear ratio span, an inter-stage ratio of a predetermined level or more, and linearity of the inter-stage ratios.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.

FIG. 1 is a view exemplarily illustrating various exemplary embodiments of a planetary gear train of an automatic transmission for a vehicle according to an exemplary embodiment of the present invention;

FIG. 2 is an operation table of the planetary gear train of FIG. 1 .

It may be understood that the appended drawings are not necessarily to scale, presenting a somewhat simplified representation of various features illustrative of the basic principles of the present invention. The specific design features of the present invention as included herein, including, for example, specific dimensions, orientations, locations, and the particular intended application and use environment shapes will be determined in part by the particularly intended application and use environment.

In the figures, reference numbers refer to the same or equivalent parts of the present invention throughout the several figures of the drawing.

Reference will now be made in detail to various embodiments of the present invention(s), examples of which are illustrated in the accompanying drawings and described below. While the present invention(s) will be described in conjunction with exemplary embodiments of the present invention, it will be understood that the present description is not intended to limit the present invention(s) to those exemplary embodiments. On the other hand, the present invention(s) is/are intended to cover not only the exemplary embodiments of the present invention, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the present invention as defined by the appended claims.

Referring to FIG. 1 , a planetary gear train of an automatic transmission for a vehicle of the present invention includes: an input shaft IN configured to receive power from a power source such as an engine or the like; an output shaft OUT configured to output power; a first planetary gear set PG 1 including first, second, and third rotation elements; a second planetary gear set PG 2 including fourth, fifth, and sixth rotation elements; a third planetary gear set PG 3 including seventh, eighth, and ninth rotation elements; a fourth planetary gear set PG 4 including tenth, eleventh, and twelfth rotation elements; and a fifth planetary gear set PG 5 including the thirteenth, fourteenth, and fifteenth rotation elements.

The planetary gear train includes: a first shaft SH 1 connected to the first rotation element and to the input shaft IN; a second shaft SH 2 connected to the fourteenth rotation element and to the output shaft OUT; a third shaft SH 3 connected to the third rotation element; a fourth shaft SH 4 connected to the sixth rotation element, to the eleventh rotation element, and to the fifteenth rotation element; a fifth shaft SH 5 connected to the seventh rotation element and to the thirteenth rotation element; a sixth shaft SH 6 connected to the eighth rotation element and to the twelfth rotation element; a seventh axis SH 7 connected to the second rotation element and to the fourth rotation element; an eighth shaft SH 8 connected to the fifth rotation element and to the ninth rotation element; and a ninth shaft SH 9 connected to the tenth rotation element.

The first to fifth planetary gear sets PG 1 to PG 5 are mounted in the order of the first planetary gear set PG 1 , the second planetary gear set PG 2 , the third planetary gear set PG 3 , the fourth planetary gear set PG 4 , and the fifth planetary gear set PG 5 from one side toward the other side thereof with respect to an engine side.

That is, a power source such as an engine is configured to provide power through the input shaft IN from the engine side and the first shaft SH 1 , and the power supplied as described above is configured to be appropriately shifted through the configuration of the present invention, in which the first planetary gear set PG 1 , the second planetary gear set PG 2 , the third planetary gear set PG 3 , the fourth planetary gear set PG 4 , and the fifth planetary gear the set PG 5 are mounted in order, and then to be drawn to the output shaft OUT through the fourteenth rotation element of the fifth planetary gear set PG 5 and the second shaft SH 2 .

Each of the first planetary gear set PG 1 , the second planetary gear set PG 2 , the third planetary gear set PG 3 , the fourth planetary gear set PG 4 , and the fifth planetary gear set PG 5 , which form the planetary gear train described above, is configured as a single pinion planetary gear set having three rotation elements.

The planetary gear train is mounted in a transmission housing CS, a torque converter may be provided between the power source such as the engine and the input shaft IN, and the power drawn to the output shaft OUT may be transmitted to a drive wheel of the vehicle through a differential.

The planetary gear train includes six coupling elements for selectively connecting two shafts among the first to ninth shafts SH 1 to SH 9 or the transmission housing CS and a shaft among the first to ninth shafts SH 1 to SH 9 , and three coupling elements among the six coupling elements are operatively controlled to be simultaneously coupled to each other such that a reverse shifting stage is implemented.

That is, in implementing any one of 1 to 10 forward shifting stages and an R stage, which is a reverse stage, as illustrated in FIG. 2 , it is possible to combine three specified coupling elements among the six coupling elements to implement a corresponding shifting stage.

Of course, the planetary gear train is configured to enable clutch-to-clutch shifting, in which, when shifting to an adjacent speed change stage among the shifting stages, shifting is performed by releasing one coupling element, at the current shifting stage, from the three coupling elements required for implementing each shifting stage, and at the same time, by coupling another coupling element at a target shifting stage.

The six coupling elements include three clutches that connect two shafts among the first to ninth shafts SH 1 to SH 9 , and three brakes that selectively connect the transmission housing CS and a shaft which is not connected to the input shaft IN or the output shaft OUT among the first to ninth shafts SH 1 to SH 9 .

In the various exemplary embodiments of FIG. 1 , the six coupling elements include a first clutch CL 1 mounted between the first shaft SH 1 and the fifth shaft SH 5 , a second clutch CL 2 mounted between the first shaft SH 1 and the sixth shaft SH 6 , a third clutch CL 3 mounted between the third shaft SH 3 and the sixth shaft SH 6 , a first brake B 1 mounted between the seventh shaft SH 7 and the transmission housing CS, a second brake B 2 mounted between the eighth shaft SH 8 and the transmission housing CS, and a third brake B 3 mounted between the ninth shaft SH 9 and the transmission housing CS.

In the exemplary embodiment described above, the first, second, and third rotation elements include a first sun gear S 1 , a first planet carrier C 1 , and a first ring gear R 1 , the fourth, fifth, and sixth rotation elements include a second sun gear S 2 , a second planet carrier C 2 , and a second ring gear R 2 , the seventh, eighth, and ninth rotation elements include a third sun gear S 3 , a third planet carrier C 3 , and a third ring gear R 3 , the tenth, eleventh and twelfth rotation elements include a fourth sun gear S 4 , a fourth planet carrier C 4 , and a fourth ring gear R 4 , and the thirteenth, fourteenth, and fifteenth rotation elements include a fifth sun gear S 5 , a fifth planet carrier C 5 , and a fifth ring gear R 5 .

Furthermore, the planetary gear train of the automatic transmission for a vehicle of the present invention illustrated in FIG. 1 may be expressed as follows.

That is, the planetary gear train of the automatic transmission for a vehicle of the present invention includes: a first planetary gear set PG 1 having three rotation elements, one of which is connected to an input shaft IN; a second planetary gear set PG 2 having three rotation elements, one of which is continuously connected to any one of the first to third rotation elements of the first planetary gear set PG 1 ; a third planetary gear set PG 3 having three rotation elements, one of which is connected to the input shaft in a disconnectable manner by a first clutch CL 1 , another one of which is connected to two rotation elements of the first planetary gear set PG 1 in a disconnectable manner by a second clutch CL 2 and a third clutch CL 3 , respectively, and a remaining one of which is continuously connected to one rotation element of the second planetary gear set PG 2 ; a fourth planetary gear set PG 4 having three rotation elements, one of which is continuously connected to any one of the first to third rotation elements of the third planetary gear set PG 3 ; a fifth planetary gear set PG 5 having three rotation elements, one of which is continuously connected to one rotation element of the third planetary gear set PG 3 , another one of which is connected to the output shaft OUT, and a remaining one of which is continuously connected to one rotation element of the fourth planetary gear set PG 4 ; a first brake B 1 mounted to restrain rotation of the rotation element which is continuously connected to the rotation element of the first planetary gear set PG 1 , among the first to third rotation elements of the second planetary gear set PG 2 ; a second brake B 2 mounted to restrain rotation of the rotation element which is continuously connected to the rotation element of the third planetary gear set PG 3 , among the first to third rotation elements of the second planetary gear set PG 2 ; and a third brake B 3 mounted to restrain rotation of the remaining rotation element, which is not connected to any other rotation element, among the first to third rotation elements of the fourth planetary gear set PG 4 .

The rotation element of the first planetary gear set PG 1 connected to the input shaft IN is a first rotation element; a first rotation element of the second planetary gear set PG 2 is continuously connected to a second rotation element of the first planetary gear set PG 1 ; a first rotation element of the third planetary gear set PG 3 is connected to the input shaft in a disconnectable manner, a second rotation element of the third planetary gear set PG 3 is connected to each of the first rotation element and the third rotation element of the first planetary gear set PG 1 in a disconnectable manner, and a third rotation element of the third planetary gear set PG 3 is continuously connected to the second rotation element of the second planetary gear set PC 2 ; a third rotation element of the fourth planetary gear set PG 4 is continuously connected to the second rotation element of the third planetary gear set PG 3 ; a first rotation element of the fifth planetary gear set PG 5 is continuously connected to the first rotation element of the third planetary gear set PG 3 , a second rotation element of the fifth planetary gear set PG 5 is directly connected to the output shaft OUT, and a third rotation element of the fifth planetary gear set PG 5 is continuously connected to the second rotation element of the fourth planetary gear set PG 4 .

The first brake B 1 is mounted to restrict rotation of the first planet carrier C 1 of the first planetary gear set PG 1 and the second sun gear S 2 of the second planetary gear set PG 2 , the second brake B 2 is mounted to restrain rotation of the second planet carrier C 2 of the second planetary gear set PG 2 , and the third brake B 3 is mounted to restrict rotation of the fourth sun gear S 4 of the fourth planetary gear set PG 4 .

The first clutch CL 1 is mounted to connect the third sun gear S 3 of the third planetary gear set PG 3 and the input shaft in a disconnectable manner, the second clutch CL 2 is mounted to connect the third planet carrier C 3 of the third planetary gear set PG 3 and the first sun gear S 1 of the first planetary gear set PG 1 in a disconnectable manner, and the third clutch CL 3 is mounted to connect the third planet carrier C 3 of the third planetary gear set PG 3 and the first ring gear R 1 of the first planetary gear set PG 1 in a disconnectable manner.

Furthermore, the planetary gear train of the automatic transmission for a vehicle of the present invention illustrated in FIG. 1 may be expressed as follows.

That is, the planetary gear train of an automatic transmission for a vehicle according to an exemplary embodiment of the present invention includes a first planetary gear set PG 1 , a second planetary gear set PG 2 , a third planetary gear set PG 3 , a fourth planetary gear set PG 4 , and a fifth planetary gear set PG 5 , each of which may include three rotation elements; six coupling elements configured to provide a variable frictional force; and nine shafts connected to the rotation elements of the planetary gear sets.

Here, the first shaft SH 1 is directly connected to the first rotation element of the first planetary gear set PG 1 and to the input shaft IN, the second shaft SH 2 is directly connected to the second rotation element of the fifth planetary gear set PG 5 and to the output shaft OUT, the third shaft SH 3 is directly connected to the third rotation element of the first planetary gear set PG 1 , the fourth shaft SH 4 is directly connected to the third rotation element of the second planetary gear set PG 2 , to the second rotation element of the fourth planetary gear set PG 4 , and to the third rotation element of the fifth planetary gear set PG 5 , the fifth shaft SH 5 is directly connected to the first rotation element of the third planetary gear set PG 3 and to the first rotation element of the fifth planetary gear set PG 5 , the sixth shaft SH 6 is directly connected to the second rotation element of the third planetary gear set PG 3 and to the third rotation element of the fourth planetary gear set PG 4 , the seventh shaft SH 7 is directly connected to the second rotation element of the first planetary gear set PG 1 and to the first rotation element of the second planetary gear set PG 2 , the eighth shaft SH 8 is directly connected to the second rotation element of the second planetary gear set PG 2 and to the third rotation element of the third planetary gear set PG 3 , and the ninth shaft SH 9 is directly connected to the first rotation element of the fourth planetary gear set PG 4 .

Among the six coupling elements, the first clutch CL 1 is mounted between the first shaft SH 1 and the fifth shaft SH 5 , the second clutch CL 2 is mounted between the first shaft SH 1 and the sixth shaft SH 6 , the third clutch CL 3 is mounted between the third shaft SH 3 and the sixth shaft SH 6 , the first brake B 1 is mounted between the seventh shaft SH 7 and the transmission housing, the second brake B 2 is mounted between the eighth shaft SH 8 and the transmission housing, and the third brake B 3 is mounted between the ninth shaft SH 9 and the transmission housing.

The first to fifth planetary gear sets PG 1 to PG 5 are mounted in the axial direction of the input shaft IN and the output shaft OUT in the order of the first planetary gear set PG 1 , the second planetary gear set PG 2 , the third planetary gear set PG 3 , the fourth planetary gear set PG 4 , and the fifth planetary gear set PG 5 .

The rotation elements of each of the first to fifth planetary gear sets PG 1 to PG 5 are mounted in an order of the first rotation element, the second rotation element, and the third rotation element toward a radially external side from a rotation center thereof.

The planetary gear train of an automatic transmission for a vehicle according to an exemplary embodiment of the present invention configured as described above implements shifting stages according to an operation table as represented in FIG. 2 .

The first shifting stage is implemented by causing the first clutch CL 1 , the third clutch CL 3 , and the second brake B 2 to be engaged with each other.

By the engagement of the first clutch CL 1 , the power of the input shaft IN and the first shaft SH 1 is supplied to the first sun gear S 1 of the first planetary gear set PG 1 , and is directly transmitted to the third sun gear S 3 of the third planetary gear set PG 3 and to the fifth sun gear S 5 of the fifth planetary gear set PG 5 .

Since the second brake B 2 is engaged and thus the third ring gear R 3 of the third planetary gear set PG 3 is fixed by the eighth shaft SH 8 , the power supplied to the third sun gear S 3 is made slower through the third planet carrier C 3 to be transmitted to the fourth ring gear R 4 and is simultaneously transmitted to the first ring gear R 1 through the third clutch CL 3 , and the rotational force of the first planet carrier C 1 determined by the rotation of the first ring gear R 1 and the first sun gear S 1 is transmitted to the second sun gear S 2 through the seventh shaft SH 7 . Since the second planet carrier C 2 is fixed, the power transmitted to the second sun gear S 2 is reversed and transmitted to the second ring gear R 2 and is then transmitted to the fourth planet carrier C 4 and the fifth ring gear R 5 through the fourth shaft SH 4 .

Therefore, the power transmitted to the fifth sun gear S 5 is made slower by the reaction force provided as the fifth ring gear R 5 is reversely rotated to be output and drawn out to the second shaft SH 2 and the output shaft OUT as a first shifting stage is formed by the fifth planet carrier C 5 .

A second shifting stage is implemented by releasing the third clutch CL 3 from the first shifting stage state and engaging the first brake B 1 .

In the state where the first brake B 1 and the second brake B 2 are engaged and thus the seventh shaft SH 7 and the eighth shaft SH 8 are fixed, the power of the input shaft IN is transmitted to the third sun gear S 3 and the fifth sun gear S 5 simultaneously through the first sun gear S 1 as well as the first clutch CL 1 , and is then shifted and made slower by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the second shifting stage.

A third shifting stage is implemented by releasing the second brake B 2 from the second shifting stage state and engaging the third brake B 3 .

In the state where the first brake B 1 and the third brake B 3 are engaged and thus the first planet carrier C 1 and the second sun gear S 2 connected to the seventh shaft SH 7 are fixed and the fourth sun gear S 4 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third sun gear S 3 , and the fifth sun gear S 5 , and is then shifted and made slower by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the third shifting stage.

A fourth shifting stage is implemented by releasing the first brake B 1 from the third shifting stage state and engaging the third clutch CL 3 .

In the state where the third brake B 3 is engaged and thus the fourth sun gear S 4 connected to the ninth shaft SH 9 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third sun gear S 3 , and the fifth sun gear S 5 , and is then shifted and made slower by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the fourth shifting stage.

A fifth shifting stage is implemented by releasing the third clutch CL 3 from the fourth shifting stage state and engaging the second clutch CL 2 .

In the state where the third brake B 3 is engaged and thus the fourth sun gear S 4 connected to the ninth shaft SH 9 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third sun gear S 3 , and the fifth sun gear S 5 , and is then shifted and made slower by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the fifth shifting stage.

A sixth shifting stage is implemented by releasing the third brake B 3 from the fifth shifting stage state and engaging the third clutch CL 3 .

That is, in the state where all of the first clutch CL 1 , the second clutch CL 2 , and the third clutch CL 3 are engaged, all the first to third rotation elements of the first planetary gear set PG 1 are integrated by the engagement of the second clutch CL 2 and the third clutch CL 3 , and the third sun gear S 3 and the third planet carrier C 3 are integrated by the first clutch CL 1 . Consequently, all of the first to third rotation elements of the third planetary gear set PG 3 are also integrated, and furthermore, the rotation elements of all of the planetary gear sets are integrated, so that the power input to the input shaft IN is output as it is by forming a 1:1 gear ratio with the output shaft OUT, implementing the sixth shifting stage.

A seventh shifting stage is implemented by releasing the third clutch CL 3 from the sixth shifting stage state and engaging the first brake B 1 .

In the state where the first brake B 1 is engaged and thus the first planet carrier C 1 and the second sun gear S 2 connected to the seventh shaft SH 7 are fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third sun gear S 3 , and the fifth sun gear S 5 , and is then shifted and made faster by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the seventh shifting stage.

An eighth shifting stage is implemented by releasing the first clutch CL 1 from the seventh shifting stage state and engaging the third brake B 3 .

In the state where the first brake B 1 is engaged so that the first planet carrier C 1 and the second sun gear S 2 connected to the seventh shaft SH 7 are fixed and the third brake B 3 is engaged so that the fourth sun gear S 4 connected to the ninth shaft SH 9 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third planet carrier C 3 , and the fourth ring gear R 4 , and is then shifted and made faster by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the eighth shifting stage.

A ninth shifting stage is implemented by releasing the third brake B 3 from the eighth shifting stage state and engaging the second brake B 2 .

In the state where the first brake B 1 is engaged so that the first planet carrier C 1 and the second sun gear S 2 connected to the seventh shaft SH 7 are fixed and the second brake B 2 is engaged so that the second planet carrier C 2 and the third ring gear R 3 connected to the eighth shaft SH 8 are fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third planet carrier C 3 , and the fourth ring gear R 4 , and is then shifted and made faster by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the ninth shifting stage.

A tenth shifting stage is implemented by releasing the first brake B 1 from the ninth shifting stage state and engaging the third brake B 3 .

In the state where the second brake B 2 is engaged so that the second planet carrier C 2 and the third ring gear R 3 connected to the eighth shaft SH 8 are fixed and the third brake B 3 is engaged so that the fourth sun gear S 4 connected to the ninth shaft SH 9 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , the third planet carrier C 3 , and the fourth ring gear R 4 , and is then shifted and made faster by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the tenth shifting stage.

An R-stage, which is the reverse shifting stage, is implemented by causing the third clutch CL 3 , the second brake B 2 , and the third brake B 3 to be engaged with each other.

In the state where the second brake B 2 are engaged and thus the second planet carrier C 2 and the third ring gear R 3 connected to the eighth shaft SH 8 are fixed and the third brake B 3 is engaged and thus the fourth sun gear S 4 connected to the ninth shaft SH 9 is fixed, the power of the input shaft IN is input to the first sun gear S 1 , and is then reversed and made slower by the fifth planet carrier C 5 of the fifth planetary gear set PG 5 , forming the reverse shifting stage.

As described above, with the configuration described above, the planetary gear train of an automatic transmission for a vehicle according to an exemplary embodiment of the present invention forms shifting stages of 10 forward speeds and 1 reverse speed and has a gear ratio span of 9.0. Thus, fuel efficiency may be improved by making it possible to drive the engine mainly in a more efficient region.

In an exemplary embodiment of the present invention, the minimum inter-stage ratio is 1.192 or more, and linearity is ensured in the transition of change of the inter-stage ratio according to a shifting stage change, similarly to the ideal tendency of change of the inter-stage ratio, so that vehicle acceleration, the sense of the sense of rhythm of the engine speed, and the like before and after shifting may be improved, maximizing the driving performance of the vehicle.

For convenience in explanation and accurate definition in the appended claims, the terms “upper”, “lower”, “inner” and “outer”, “up,” “down,” “upper”, “lower,” “upwards,” “downwards”, “front”, “rear”, “back”, “inside”, “outside”, “inwardly,” “outwardly,” “internal”, “external”, “inner,” “outer”, “forwards” and “backwards” are used to describe features of the exemplary embodiments with reference to the positions of such features as displayed in the figures.

For convenience in explanation and accurate definition in the appended claims, the terms “upper”, “lower”, “inner” and “outer” are used to describe features of the exemplary embodiments with reference to the positions of such features as displayed in the figures.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the present invention to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teachings. The exemplary embodiments were chosen and described to explain certain principles of the present invention and their practical application, to enable others skilled in the art to make and utilize various exemplary embodiments of the present invention, as well as various alternatives and modifications thereof. It is intended that the scope of the present invention be defined by the Claims appended hereto and their equivalents.