Patent Publication Number: US-9897174-B2

Title: Planetary gear train of automatic transmission for vehicles

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     The present application claims priority to Korean Patent Application No. 10-2016-0038480, filed Mar. 30, 2016, the entire contents of which is incorporated herein for all purposes by this reference. 
     BACKGROUND OF THE INVENTION 
     Field of the Invention 
     The present invention relates to an automatic transmission for a vehicle. More particularly, the present invention relates to a planetary gear train of an automatic transmission of a vehicle that improves power delivery performance and reduces fuel consumption by achieving eleven forward speed stages using a minimum number of constituent elements. 
     Description of Related Art 
     Research on realizing more shift-stages of an automatic transmission has been undertaken to achieve enhancement of fuel consumption and better drivability, and recent increases in oil prices are triggering stiff competition in enhancing fuel consumption of a vehicle. 
     In this sense, research on an engine has been undertaken to achieve weight reduction and to enhance fuel consumption by so-called downsizing and research on an automatic transmission has been performed to simultaneously provide better drivability and fuel consumption by achieving more shift stages. 
     However, in the automatic transmission, as the number of speed stages increase, the number of parts is typically increased, which may deteriorate installability and/or power flow efficiency and may increase production cost, and weight. 
     Therefore, in order to maximally enhance fuel consumption of an automatic transmission having more shift stages, it is important for better efficiency to be derived by a smaller number of parts. 
     In this respect, an eight-speed automatic transmission has been recently introduced, and a planetary gear train for an automatic transmission enabling more shift stages is under investigation. 
     An automatic transmission of eight or more shift-stages typically includes three to four planetary gear sets and five to six control elements (frictional elements), and may easily become lengthy, thereby deteriorating installability. 
     In this regard, disposing planetary gear sets in parallel or employing dog clutches instead of wet-type control elements has been attempted. However, such an arrangement may is not widely applicable, and using dog clutches may easily deteriorate shift-feel. 
     The information disclosed in this Background of the Invention section is only for enhancement of understanding of the general background of the invention and should 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. 
     BRIEF SUMMARY 
     Various aspects of the present invention are directed to providing a planetary gear train of an automatic transmission for a vehicle having advantages of obtaining shift-stages of at least eleven forward speeds and at least one reverse speed by minimal number of parts, improving power delivery performance and fuel consumption by multi-stages of an automatic transmission, and improving driving stability of a vehicle by utilizing a low rotation speed of an engine. 
     According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft for receiving an engine torque, an output shaft for outputting a shifted torque, a first planetary gear set including first, second, and third rotation elements, a second planetary gear set including fourth, fifth, and sixth rotation elements, a third planetary gear set including seventh, eighth, and ninth rotation elements, a fourth planetary gear set including tenth, eleventh, and twelfth rotation elements, a first shaft connected with the first rotation element, a second shaft connected with the second rotation element, a third shaft interconnecting the third rotation element and the fifth rotation element, a fourth shaft connected with the fourth rotation element, and directly connected with a transmission housing, a fifth shaft interconnecting the sixth rotation element, the seventh rotation element and tenth rotation element, and selectively connectable with the second shaft, a sixth shaft connected with the eighth rotation element, and directly connected with the output shaft, a seventh shaft connected with the ninth rotation element, an eighth shaft connected with the eleventh rotation element, selectively connectable with the first shaft and the second shaft, and directly connected with the input shaft, and a ninth shaft connected with the twelfth rotation element, and selectively connectable with the sixth shaft. 
     The first shaft, the second shaft and the seventh shaft may each be selectively connectable with the transmission housing. 
     The first, second, and third rotation elements may be a first sun gear, a first planet carrier, and a first ring gear, the fourth, fifth, and sixth rotation elements may be a second sun gear, a second planet carrier, and a second ring gear, the seventh, eighth, and ninth rotation elements may be a third sun gear, a third planet carrier, and a third ring gear, and the tenth, eleventh, and twelfth rotation elements may be a fourth sun gear, a fourth planet carrier, and a fourth ring gear. 
     The planetary gear train may further include a first clutch selectively connecting the second shaft and the eighth shaft, a second clutch selectively connecting the second shaft and the fifth shaft, a third clutch selectively connecting the first shaft and the eighth shaft, a fourth clutch selectively connecting the sixth shaft and the ninth shaft, a first brake selectively connecting the second shaft and the transmission housing, a second brake selectively connecting the seventh shaft and the transmission housing, and a third brake selectively connecting the first shaft and the transmission housing. 
     According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft for receiving an engine torque, an output shaft for outputting a shifted torque, a first planetary gear set including first, second, and third rotation elements, a second planetary gear set including fourth, fifth, and sixth rotation elements, a third planetary gear set including seventh, eighth, and ninth rotation elements, and a fourth planetary gear set including tenth, eleventh, and twelfth rotation elements, in which the input shaft may be directly connected with the eleventh rotation element, the output shaft may be directly connected with the eighth rotation element, the third rotation element may be directly connected with the fifth rotation element, the sixth rotation element may be selectively connectable with the second rotation element, the seventh rotation element and the tenth rotation element directly may be connected with the sixth rotation element, the eighth rotation element may be selectively connectable with the first rotation element and the second rotation element, and the twelfth rotation element may be selectively connectable with the eighth rotation element. 
     The first rotation element and the second rotation element and the ninth rotation element may each be selectively connectable with the transmission housing. 
     The planetary gear train may further include a first clutch selectively connecting the second rotation element and the eleventh rotation element, a second clutch selectively connecting the second rotation element and the sixth rotation element, a third clutch selectively connecting the first rotation element and the eleventh rotation element, a fourth clutch selectively connecting the eighth rotation element and the twelfth rotation element, a first brake selectively connecting the second rotation element and the transmission housing, a second brake selectively connecting the ninth rotation element and the transmission housing, and a third brake selectively connecting the first rotation element and the transmission housing. 
     Speed shift-stages implemented by selectively operating the first, second, third and fourth clutches and the first, second and third brakes may include a forward first speed shift-stage, implemented by operating the second and third clutches, and the second brake, a forward second speed shift-stage, implemented by operating the first and second clutches, and the second brake, a forward third speed shift-stage, implemented by operating the first and third clutches, and the second brake, a forward fourth speed shift-stage, implemented by operating the first clutch, and the second and third brakes, a forward fifth speed shift-stage, implemented by operating the fourth clutch, and the second and third brakes, a forward sixth speed shift-stage, implemented by operating the first and fourth clutches and the third brake, a forward seventh speed shift-stage, implemented by operating the first, third and fourth clutches, a forward eighth speed shift-stage, implemented by operating the first, second and fourth clutches, a forward ninth speed shift-stage, implemented by operating the second, third and fourth clutches, a forward tenth speed shift-stage, implemented by operating the second and fourth clutches, and the first brake, a forward eleventh speed shift-stage, implemented by operating the third and fourth clutches, and the first brake, and a reverse-speed shift-stage, implemented by operating the third clutch, and the first and second brakes. 
     According to various embodiments of the present invention, shift-stages of at least eleventh forward speeds and at least one reverse speed are realized by combination of four planetary gear sets and seven control elements. 
     In addition, a planetary gear train according to various embodiments of the present invention substantially improves driving stability by realizing shift-stages appropriate for rotation speed of an engine due to multiple speed-stages of an automatic transmission. 
     Furthermore, a planetary gear train according to various embodiments of the present invention maximizes engine driving efficiency by multiple speed-stages of an automatic transmission, and improves power delivery performance and fuel consumption. 
     It is understood that the term “vehicle” or “vehicular” or other similar terms as used herein is inclusive of motor vehicles in general such as passenger automobiles including sports utility vehicles (SUV), buses, trucks, various commercial vehicles, watercraft including a variety of boats and ships, aircraft, and the like, and includes hybrid vehicles, electric vehicles, plug-in hybrid electric vehicles, hydrogen-powered vehicles and other alternative fuel vehicles (e.g., fuel derived from resources other than petroleum). As referred to herein, a hybrid vehicle is a vehicle that has two or more sources of power, for example, both gasoline-powered and electric-powered vehicles. 
     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. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a schematic diagram of a planetary gear train according to various embodiments of the present invention. 
         FIG. 2  is an operational chart for respective control elements at respective shift-stages in the planetary gear train according to various embodiments of the present invention. 
     
    
    
     It should 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 invention. The specific design features of the present invention as disclosed herein, including, for example, specific dimensions, orientations, locations, and shapes will be determined in part by the particular intended application and use environment. 
     DETAILED DESCRIPTION 
     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 invention(s) will be described in conjunction with exemplary embodiments, it will be understood that the present description is not intended to limit the invention(s) to those exemplary embodiments. On the contrary, the invention(s) is/are intended to cover not only the exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims. 
       FIG. 1  is a schematic diagram of a planetary gear train according to various embodiments of the present invention. 
     Referring to  FIG. 1 , a planetary gear train according to various embodiments of the present invention includes first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , arranged on a same axis, an input shaft IS, an output shaft OS, eight shafts TM 1  to TM 8  interconnecting rotation elements of the first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , four clutches C 1  to C 4  and three brakes B 1  to B 3  as control elements, and a transmission housing H. 
     Torque input from the input shaft IS is shifted by cooperative operation of the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , and then output through the output shaft OS. 
     The planetary gear sets are arranged in the order of first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , from an engine side. 
     The input shaft IS is an input member and the torque from a crankshaft of an engine is input into the input shaft IS, after being torque-converted through a torque converter. 
     The output shaft OS is an output member, and being arranged on a same axis with the input shaft IS, delivers a shifted driving torque to a drive shaft through a differential apparatus. 
     The first planetary gear set PG 1  is a single pinion planetary gear set, and includes a first planet carrier PC 1  that supports first pinion gear P 1  externally engaged with the first sun gear S 1 , and a first ring gear R 1  that is internally engaged with the first pinion gear P 1 . The first sun gear S 1  acts as a first rotation element N 1 , the first planet carrier PC 1  acts as a second rotation element N 2 , and the first ring gear R 1  acts as a third rotation element N 3 . 
     The second planetary gear set PG 2  is a single pinion planetary gear set, and includes a second planet carrier PC 2  that supports second pinion gear P 2  externally engaged with the second sun gear S 2 , and a second ring gear R 2  that is internally engaged with the second pinion gear P 2 . The second sun gear S 2  acts as a fourth rotation element N 4 , the second planet carrier PC 2  acts as a fifth rotation element N 4 , and the second ring gear R 2  acts as a sixth rotation element N 6 . 
     The third planetary gear set PG 3  is a single pinion planetary gear set, and includes a third planet carrier PC 3  that supports third pinion gear P 3  externally engaged with the third sun gear S 3 , and a third ring gear R 3  that is internally engaged with the third pinion gear P 3 . The third sun gear S 3  acts as a seventh rotation element N 7 , the third planet carrier PC 3  acts as an eighth rotation element N 8 , and the third ring gear R 3  acts as a ninth rotation element N 9 . 
     The fourth planetary gear set PG 4  is a single pinion planetary gear set, and includes a fourth planet carrier PC 4  that supports fourth pinion gear P 4  externally engaged with the fourth sun gear S 4 , and a fourth ring gear R 4  that is internally engaged with the fourth pinion gear P 4 . The fourth sun gear S 4  acts as a tenth rotation element N 10 , the fourth planet carrier PC 4  acts as a eleventh rotation element N 11 , and the fourth ring gear R 4  acts as a twelfth rotation element N 12 . 
     In the first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , the second rotation element N 2  is directly connected with the fourth rotation element N 4  and the eighth rotation element N 8 , the fifth rotation element N 5  is directly connected with the twelfth rotation element N 12 , and the seventh rotation element N 7  is directly connected with the tenth rotation element N 10 , by nine shafts TM 1  to TM 9 . 
     The nine shafts TM 1  to TM 9  are hereinafter described in detail. 
     Each of the nine shafts TM 1  to TM 9  may be a rotation member that directly interconnects the input and output shafts and rotation elements of the planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , or may be a fixed member fixed to the transmission housing H. 
     The first shaft TM 1  is connected with the first rotation element N 1  (the first sun gear S 1 ), and is selectively connectable with the transmission housing H. 
     The second shaft TM 2  is connected with the second rotation element N 2  (the first planet carrier PC 1 ), and is selectively connectable with the transmission housing H. 
     The Third shaft TM 3  connects the third rotation element N 3  (the first ring gear R 1 ) and the fifth rotation element N 5  (the second planet carrier PC 2 ). 
     The fourth shaft TM 4  is connected with the fourth rotation element N 4  (the second sun gear S 2 ), and is directly connected with the transmission housing H. 
     The fifth shaft TM 5  connects the sixth rotation element N 6  (the second ring gear R 2 ), the seventh rotation element N 7  (the third sun gear S 3 ), and the tenth rotation element N 10  (the fourth sun gear S 4 ), and is selectively connectable with the second shaft TM 2 . 
     The sixth shaft TM 6  is connected with the eighth rotation element N 8  (the third planet carrier PC 3 ), and is directly connected with the output shaft OS, thereby continuously acting as an output element. 
     The seventh shaft TM 7  is connected with the ninth rotation element N 9  (the third ring gear R 3 ), and selectively connectable with the transmission housing H. 
     The eighth shaft TM 8  is connected with the eleventh rotation element N 11  (the fourth planet carrier PC 4 ), is selectively connectable with the first shaft TM 1  and the second shaft TM 2 , and is directly connected with the input shaft IS, thereby continuously acting as an input element. 
     The ninth shaft TM 9  is connected with the twelfth rotation element N 12  (the fourth ring gear R 4 ), and is selectively connectable with the sixth shaft TM 6 . 
     The nine shafts TM 1  to TM 9 , the input shaft IS, and the output shaft OS may be selectively interconnected with one another by control elements of four clutches C 1 , C 2 , C 3 , and C 4 . 
     The nine shafts TM 1  to TM 9  may be selectively connectable with the transmission housing H, by control elements of three brakes B 1 , B 2  and B 3 . 
     The four clutches C 1  to C 4  and the three brakes B 1  to B 3  are arranged as follows. 
     The first clutch C 1  is arranged between the second shaft TM 2  and the eighth shaft TM 8 , and selectively connects the second shaft TM 2  and the eighth shaft TM 8  connected with the output shaft OS thereby controlling power delivery therebetween. 
     The second clutch C 2  is arranged between the second shaft TM 2  and the fifth shaft TM 5 , and selectively connects the second shaft TM 2  and the fifth shaft TM 5  connected with the output shaft OS thereby controlling power delivery therebetween. 
     The third clutch C 3  is arranged between the first shaft TM 1  and the eighth shaft TM 8 , and selectively connects the first shaft TM 1  and the eighth shaft TM 8  connected with the output shaft OS thereby controlling power delivery therebetween. 
     The fourth clutch C 4  is arranged between the sixth shaft TM 6  and the ninth shaft TM 9 , and selectively connects the sixth shaft TM 6  and the ninth shaft TM 9  connected with the output shaft OS thereby controlling power delivery therebetween. 
     The first brake B 1  is arranged between the second shaft TM 2  and the transmission housing H, and selectively connects the second shaft TM 2  to the transmission housing H. 
     The second brake B 2  is arranged between the seventh shaft TM 7  and the transmission housing H, and selectively connects the seventh shaft TM 7  to the transmission housing H. 
     The third brake B 3  is arranged between the first shaft TM 1  and the transmission housing H, and selectively connects the first shaft TM 1  to the transmission housing H. 
     The respective control elements of the first, second, third, and fourth clutches C 1 , C 2 , C 3 , and C 4  and the first, second, and third brakes B 1 , B 2 , and B 3  may be realized as multi-plate hydraulic pressure friction devices that are frictionally engaged by hydraulic pressure. 
       FIG. 2  is an operational chart for respective control elements at respective shift-stages in a planetary gear train according to various embodiments of the present invention. 
     Referring to  FIG. 2 , a planetary gear train according to various embodiments of the present invention realizes eleven forward speeds and one reverse speed by operating three control elements among the first, second, third, and fourth clutches C 1 , C 2 , C 3 , and C 4  and the first, second, and third brakes B 1 , B 2 , and B 3  at respective shift-stages. 
     In the forward first speed shift-stage D 1 , the second and third clutches C 2  and C 3  and the second brake B 2  are operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the second clutch C 2 , and the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the torque of the input shaft IS is input to the first shaft TM 1  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the seventh shaft TM 7  simultaneously acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward first speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward second speed shift-stage D 2 , the first and second clutches C 1  and C 2  and the second brake B 2  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the second clutch C 2 . In this state, the torque of the input shaft IS is input to the second shaft TM 2 , the fifth shaft TM 5 , and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the seventh shaft TM 7  simultaneously acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward second speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward third speed shift-stage D 3 , the first and third clutches C 1  and C 3  and the second brake B 2  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the torque of the input shaft IS is input to the second shaft TM 2  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the seventh shaft TM 7  simultaneously acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward third speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward fourth speed shift-stage D 4 , the first clutch C 1  and the second and third brakes B 2  and B 3  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 . In this state, the torque of the input shaft IS is input to the second shaft TM 2  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the first shaft TM 1  and the seventh shaft TM 7  simultaneously act as fixed elements by the operation of the second and third brakes B 2  and B 3 , thereby realizing the forward fourth speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward fifth speed shift-stage D 5 , the fourth clutch C 4  and the second and third brakes B 2  and B 3  are operated. 
     As a result, the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the second shaft TM 2  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the first shaft TM 1  and the seventh shaft TM 7  simultaneously act as fixed elements by the operation of the second and third brakes B 2  and B 3 , thereby realizing the outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward sixth speed shift-stage D 6 , the first and fourth clutches C 1  and C 4  and the third brake B 3  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the second shaft TM 2  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the first shaft TM 1  simultaneously acts as a fixed element by the operation of the third brake B 3 , thereby realizing the forward sixth speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward seventh speed shift-stage D 7 , the first, third, and fourth clutches C 1 , C 3 , and C 4  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the first shaft TM 1 , the second shaft TM 2 , and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element, thereby realizing the forward seventh speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward eighth speed shift-stage D 8 , the first, second, and fourth clutches C 1 , C 2 , and C 4  are operated. 
     As a result, the second shaft TM 2  is connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the second clutch C 2 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the first shaft TM 1 , the fifth shaft TM 5 , and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element, thereby realizing the forward eighth speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward ninth speed shift-stage D 9 , the second, third, and fourth clutches C 2 , C 3 , and C 4  are operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the second clutch C 2 , the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the first shaft TM 1  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element, thereby realizing the forward ninth speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward tenth speed shift-stage D 10 , the second and fourth clutches C 2  and C 4  and the first brake B 1  are operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the second clutch C 2 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the second shaft TM 2  simultaneously acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward tenth speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the forward eleventh speed shift-stage D 11 , the third and fourth clutches C 3  and C 4  and the first brake B 1  are operated. 
     As a result, the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 , and the sixth shaft TM 6  is connected with the ninth shaft TM 9  by the operation of the fourth clutch C 4 . In this state, the torque of the input shaft IS is input to the first shaft TM 1  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the second shaft TM 2  simultaneously acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward eleventh speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     In the reverse speed REV, the third clutch C 3  and the first and second brake B 1  and B 2  are operated. 
     As a result, the first shaft TM 1  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the torque of the input shaft IS is input to the first shaft TM 1  and the eighth shaft TM 8 . 
     In addition, the fourth connecting member TM 4  continuously acts as a fixed element and the second shaft TM 2  and the seventh shaft TM 7  simultaneously act as fixed elements by the operation of the first and second brakes B 1  and B 2 , thereby realizing the reverse speed by cooperative operation of respective connecting members and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 . 
     As described above, a planetary gear train according to various embodiments of the present invention realizes at least eleven forward speeds and at least one reverse speed by operating four planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4  by controlling the four clutches C 1 , C 2 , C 3 , and C 4  and the three brakes B 1 , B 2 , and B 3 . 
     In addition, a planetary gear train according to various embodiments of the present invention realizes shift stages appropriate for rotation speed of an engine due to multiple speed-stages of an automatic transmission and improves driving stability of a vehicle by utilizing a low rotation speed of an engine. 
     Furthermore, a planetary gear train according to various embodiments of the present invention maximizes engine driving efficiency by multiple speed-stages of an automatic transmission, and improves power delivery performance and fuel consumption. 
     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 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 in order to explain certain principles of the invention and their practical application, to thereby 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 invention be defined by the Claims appended hereto and their equivalents.