Patent Publication Number: US-10309491-B2

Title: Planetary gear train of automatic transmission for vehicle

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application claims priority to and the benefit of Korean Patent Application No. 10-2017-0058306 filed on May 10, 2017, which is incorporated herein by reference in its entirety. 
     FIELD 
     The present disclosure relates to an automatic transmission for a vehicle. 
     BACKGROUND 
     The statements in this section merely provide background information related to the present disclosure and may not constitute prior art. 
     In the field of an automatic transmission, more multiplicity of shift-stages is useful technology for enhancement of fuel consumption and drivability of a vehicle. 
     Achieving more shift stages contributes to improve performance and efficiency of a vehicle in a trend so-called downsizing of an engine, and more linearity in step ratios of the shift-stages enhances drivability of the vehicle by improving uniformity of acceleration before and after a shifting, etc. 
     In order to achieve more shift-stages for an automatic transmission, the number of parts is typically increased, which may negatively affect installability, production cost, weight and/or power flow efficiency. 
     Therefore, in order to enhance fuel consumption of an automatic transmission having more shift-stages, it is desired that better efficiency is derived with less number of parts. 
     In this aspect, an eight-speed automatic transmission has been introduced recently and a planetary gear train for an automatic transmission enabling more shift-stages has been investigated. 
     A recent eight-speed automatic transmission typically shows a gear ratio span, which is a significant factor for securing linearity of step ratios, in a level of 6.5 to 7.5. 
     In addition, we have discovered that an eight-speed automatic transmission may become inferior in respect of linearity of step ratios of shift-stages even if the gear ratio span may rise a level above 9.0. 
     SUMMARY 
     The present disclosure provides a planetary gear train realizing ten forward speeds and at least one reverse speed by utilizing five planetary gear sets and six engagement elements, thereby reducing a drag loss and improving power delivery efficiency and fuel consumption. 
     Also, the present disclosure employs a torque-in-parallel scheme to an output side planetary gear set, thereby reducing torque loads of engagement elements and improving torque delivery efficiency and durability. 
     In addition, the present disclosure improves flexibility of output gear ratio, thereby improving linearity of step ratios of shift-stages. 
     One form of planetary gear train of an automatic transmission for a vehicle may include input and output shafts, first to fifth planetary gear sets respectively having first to third, fourth to sixth, seventh to ninth, tenth to twelfth, and thirteenth to fifteenth rotational elements, a first shaft connected with the second and fifth rotational elements and the input shaft, a second shaft connected with the fourteenth rotational element and the output shaft, a third shaft connected with the ninth and thirteenth rotational elements, a fourth shaft connected with the tenth and fifteenth rotational elements, a fifth shaft connected with the first, sixth, and seventh rotational elements, a sixth shaft connected with the third rotational element, a seventh shaft connected with the eighth and eleventh rotational element, an eighth shaft connected with the fourth rotational element, and a ninth shaft connected with the twelfth rotational element. 
     The planetary gear train may further include six engagement elements, each of which configured to selectively connect a corresponding pair among the first to ninth shaft, the input shaft, the output shaft, and the transmission housing, wherein three engagement elements are configured to operate for respective shift-stages. 
     The six engagement element may include three clutches and three brakes. 
     The six engagement elements may include: a first clutch arranged between the second shaft and the fifth shaft, a second clutch arranged between the sixth shaft and the seventh shaft, a third clutch arranged between the seventh shaft and the eighth shaft, a first brake arranged between the fourth shaft and the transmission housing, a second brake arranged between the eighth shaft and the transmission housing, a third brake arranged between the ninth shaft and the transmission housing. 
     The first, second, and third rotational elements may be a first sun gear, a first planet carrier, and a first ring gear of the planetary gear set. The fourth, fifth, and sixth rotational elements may be a second sun gear, a second planet carrier, and a second ring gear of the planetary gear set. The seventh, eighth, and ninth rotational elements may be a third sun gear, a third planet carrier, and a third ring gear of the planetary gear set. The tenth, eleventh, and twelfth rotational elements may be a fourth sun gear, a fourth planet carrier, and a fourth ring gear of the planetary gear set. The thirteenth, fourteenth, and fifteenth rotational elements may be a fifth sun gear, a fifth planet carrier, and a fifth ring gear of the planetary gear set. 
     The first, second, third, fourth, and fifth planetary gear sets may be arranged in an order of second, first, fourth, third, and fifth planetary gear sets from an engine side. The first, second, third, fourth, and fifth planetary gear sets may be arranged in an order of second, first, third, fourth, and fifth planetary gear sets from an engine side. 
     Another form of the present disclosure utilizes five planetary gear sets operated by six engagement elements, and thereby achieves the ten forward speeds and at least one reverse speed. 
     In addition, the gear ratio span of at least 9.8 may be achieved so as to enhance an engine driving efficiency, and a linearity of step ratios of shift-stages may be also improved, thereby contributing to a better drivability of the vehicle. 
     While achieving ten forward speeds and at least one reverse speed, engagement element operation is minimized so as to reduce a drag loss, thereby improving power delivery efficiency and fuel efficiency. 
     A torque-in-parallel scheme is applied to an output side planetary gear set, and thus the torque loads may be evenly distributed to planetary gear sets and engagement elements, thereby improving torque delivery efficiency and durability. 
     By using five planetary gear sets to realize ten forward speeds and at least one reverse speed, wider range of output gear ratios may be achieved, thereby improving linearity in step ratios of shift-stages. 
     Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure. 
    
    
     
       DRAWINGS 
       In order that the disclosure may be well understood, there will now be described various forms thereof, given by way of example, reference being made to the accompanying drawings, in which: 
         FIG. 1  is a schematic diagram of a planetary gear train; 
         FIG. 2  is an operational chart of engagement elements for respective shift-stages applied to a planetary gear train; and 
         FIG. 3  is a schematic diagram of a planetary gear train. 
     
    
    
     The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. 
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features. 
     In the following description, dividing names of components into first, second and the like is to divide the names because the names of the components are the same as each other and an order thereof is not particularly limited. Further, as used herein, description of elements being “fixedly” connected or interconnected includes elements that are always connected directly or indirectly, such that the fixedly connected elements rotate at a same speed. 
       FIG. 1  is a schematic diagram of a planetary gear train in some forms of the present disclosure. 
     Referring to  FIG. 1 , a planetary gear train in some forms of the present disclosure includes first, second, third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5  arranged on a same axis, an input shaft IS, an output shaft OS, nine shafts TM 1  to TM 9  interconnecting rotational elements of the first, second, third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5 , engagement elements of three clutches C 1  to C 3  and three brakes B 1  to B 3 , and a transmission housing H. 
     A torque of an engine input to the input shaft IS is shifted by cooperative operation of the first, second, third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5 , and a shifted torque is output through the output shaft OS. 
     In some forms of the present disclosure, the planetary gear sets are arranged in the order of the second, the first, and the fourth, third, fifth planetary gear set PG 2 , PG 1 , PG 4 , PG 3 , and PG 5 , 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 arranged on the same axis with the input shaft IS, and transmits the shifted 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 sun gear S 1 , a first planet carrier PC 1  rotatably supporting a plurality of first pinion gears P 1  externally gear-meshed with the first sun gear S 1 , and a first ring gear R 1  internally gear-meshed with the plurality of first pinion gears P 1 . The first sun gear S 1  acts as a first rotational element N 1 , the first planet carrier PC 1  acts as a second rotational element N 2 , and the first ring gear R 1  acts as a third rotational element N 3 . 
     The second planetary gear set PG 2  is a single pinion planetary gear set, and includes a second sun gear S 2 , a second planet carrier PC 2  rotatably supporting a plurality of second pinion gears P 2  externally gear-meshed with the second sun gear S 2 , and a second ring gear R 2  internally gear-meshed with the plurality of second pinion gears P 2 . The second sun gear S 2  acts as a fourth rotational element N 4 , the second planet carrier PC 2  acts as a fifth rotational element N 5 , and the second ring gear R 2  acts as a sixth rotational element N 6 . 
     The third planetary gear set PG 3  is a single pinion planetary gear set, and includes a third sun gear S 3 , a third planet carrier PC 3  rotatably supporting a plurality of third pinion gears P 3  externally gear-meshed with the third sun gear S 3 , and a third ring gear R 3  internally gear-meshed with the plurality of third pinion gears P 3 . The third sun gear S 3  acts as a seventh rotational element N 7 , the third planet carrier PC 3  acts as an eighth rotational element N 8 , and the third ring gear R 3  acts as a ninth rotational element N 9 . 
     The fourth planetary gear set PG 4  is a single pinion planetary gear set, and includes a fourth sun gear S 4 , a fourth planet carrier PC 4  rotatably supporting a plurality of fourth pinion gears P 4  externally gear-meshed with the fourth sun gear S 4 , and a fourth ring gear R 4  internally gear-meshed with the plurality of fourth pinion gears P 4 . The fourth sun gear S 4  acts as a tenth rotational element N 10 , the fourth planet carrier PC 4  acts as a eleventh rotational element N 11 , and the fourth ring gear R 4  acts as a twelfth rotational element N 12 . 
     The fifth planetary gear set PG 5  is a single pinion planetary gear set, and includes a fifth sun gear S 5 , a fifth planet carrier PC 5  rotatably supporting a plurality of fifth pinion gears P 5  externally gear-meshed with the fifth sun gear S 5 , and a fifth ring gear R 5  internally gear-meshed with the plurality of fifth pinion gears P 5 . The fifth sun gear S 5  acts as a thirteenth rotational element N 13 , the fifth planet carrier PC 5  acts as a fourteenth rotational element N 14 , and the fifth ring gear R 5  acts as a fifteenth rotational element N 15 . 
     In the arrangement of the first, second, third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5 , the second rotational element N 2  and the fifth rotational element N 5  are fixedly interconnected, the first rotational element N 1  and the sixth rotational element N 6  and seventh rotational element N 7  are fixedly interconnected, the eighth rotational element N 8  and the eleventh rotational element N 11  are fixedly interconnected, the ninth rotational element N 9  and the thirteenth rotational element N 13  are fixedly interconnected, the tenth rotational element N 10  and the fifteenth rotational element N 15  are fixedly interconnected, and nine shafts TM 1  to TM 9  are formed. 
     The nine shafts TM 1  to TM 9  are hereinafter described in detail. 
     Each of the ten shafts TM 1  to TM 9  may be a rotational member that fixedly interconnects the input and output shafts and rotational elements of the planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5 , or may be a rotational member that selectively interconnects a rotational element to the transmission housing H, or may be a fixed member fixed to the transmission housing H. 
     The first shaft TM 1  is connected with the second rotational element N 2  (first planet carrier PC 1 ) and the fifth rotational element N 5  (second planet carrier PC 2 ), and fixedly connected with the input shaft IS, thereby always acting as an input element. 
     The second shaft TM 2  is connected with the fourteenth rotational element (N 14 : fifth planet carrier PC 5 ), and fixedly connected with the output shaft OS, thereby always acting as an output element. 
     The third shaft TM 3  is connected with the ninth rotational element N 9  (third ring gear R 3 ) and the thirteenth rotational element N 13  (fifth sun gear S 5 ). 
     The fourth shaft TM 4  is connected with the tenth rotational element N 10  (fourth sun gear S 4 ) and the fifteenth rotational element N 15  (fifth ring gear R 5 ). 
     The fifth shaft TM 5  is connected with the first rotational element N 1  (first sun gear S 1 ), the sixth rotational element N 6  (second ring gear R 2 ), and the seventh rotational element N 7  (third sun gear S 3 ). 
     The sixth shaft TM 6  is connected with third rotational element N 3  (first ring gear R 1 ). 
     The seventh shaft TM 7  is connected with the eighth rotational element N 8  (third planet carrier PC 3 ) and the eleventh rotational element N 11  (fourth planet carrier PC 4 ). 
     The eighth shaft TM 8  is connected with the fourth rotational element N 4  (second sun gear S 2 ). 
     The ninth shaft TM 9  is connected with twelfth rotational element N 12  (fourth ring gear R 4 ). 
     The second shaft TM 2  is selectively connected with the fifth shaft TM 5 , and the sixth shaft TM 6  and the eighth shaft TM 8  are selectively connected with the seventh shaft TM 7 . 
     In addition, the fourth shaft TM 4 , the eighth shaft TM 8 , and ninth shaft TM 9  are selectively connected with the transmission housing H, thereby selectively acting as a fixed element. 
     The three engagement elements of clutches C 1 , C 2 , and C 3  are arranged between the nine shafts TM 1  to TM 9 , the input shaft IS, and the output shaft OS, so as to form selective connections. 
     The three engagement elements of brakes B 1 , B 2 , and B 3  are arranged between the nine shafts TM 1  to TM 9  and the transmission housing H, so as to form selective connections. 
     The six engagement element of the three clutches C 1  to C 3  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 fifth shaft TM 5 , and selectively connects the second shaft TM 2  and the fifth shaft TM 5 , thereby controlling power delivery therebetween. 
     The second clutch C 2  is arranged between the sixth shaft TM 6  and the seventh shaft TM 7 , and selectively connects the sixth shaft TM 6  and the seventh shaft TM 7 , thereby controlling power delivery therebetween. 
     The third clutch C 3  is arranged between the seventh shaft TM 7  and the eighth shaft TM 8 , and selectively connects the seventh shaft TM 7  and the eighth shaft TM 8 , thereby controlling power delivery therebetween. 
     The first brake B 1  is arranged between the fourth shaft TM 4  and the transmission housing H, and selectively connects the fourth shaft TM 4  to the transmission housing H. 
     The second brake B 2  is arranged between the eighth shaft TM 8  and the transmission housing H, and selectively connects the eighth shaft TM 8  to the transmission housing H. 
     The third brake B 3  is arranged between the ninth shaft TM 9  and the transmission housing H, and selectively connects the ninth shaft TM 9  to the transmission housing H. 
     The engagement elements of the first, second, and third clutches C 1 , C 2 , and C 3  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, however, it should not be understood to be limited thereto, since various other configuration that are electrically controllable may be available. 
       FIG. 2  is an operational chart of engagement elements for respective shift-stages applied to a planetary gear train in some forms of the present disclosure. 
     Referring to  FIG. 2 , a planetary gear train in some forms of the present disclosure realizes ten forward speeds and at least one reverse speed by operating three engagements among the first, second, and third clutches C 1 , C 2 , and C 3  and first, second, third brake B 1 , B 2 , and B 3 . 
     In the forward first speed D 1 , the second clutch C 2  and the first and second brakes B 1  and B 2  are simultaneously operated. 
     As a result, the sixth shaft TM 6  is connected with the seventh shaft TM 7  by the operation of the second clutch C 2 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth and eighth shafts TM 4  and TM 8  act as a fixed element by the operation of the first and second brakes B 1  and B 2 , thereby realizing the forward first speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward second speed D 2 , the second and third clutches C 2  and C 3  and the first brake B 1  are simultaneously operated. 
     As a result, the sixth shaft TM 6  is connected with the seventh shaft TM 7  by the operation of the second clutch C 2 , and the seventh shaft TM 7  is interconnected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth shaft TM 4  acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward second speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward third speed D 3 , the first and second clutch C 1  and C 2  and the first brake B 1  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 , and the sixth shaft TM 6  is interconnected with the seventh shaft TM 7  by the operation of the second clutch C 2 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth shaft TM 4  acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward third speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward fourth speed D 4 , the first and third clutches C 1  and C 3  and the first brake B 1  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 , and the seventh shaft TM 7  is interconnected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth shaft TM 4  acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward fourth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward fifth speed D 5 , the first, second, and third clutches C 1 , C 2 , and C 3  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 , and the sixth shaft TM 6  is interconnected with the seventh shaft TM 7  by the operation of the second clutch C 2 , and the seventh shaft TM 7  is interconnected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     Then, the first, second, third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5  integrally rotate, and the torque received at the first shaft TM 1  is outputted as inputted, thereby realizing the forward fifth speed and outputting a shifted torque through the output shaft OS connected with the second shaft TM 2 . 
     In the forward sixth speed D 6 , the first and third clutches C 1  and C 3  and the third brake B 3  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 , and the seventh shaft TM 7  is interconnected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the ninth shaft TM 9  acts as a fixed element by the operation of the third brake B 3 , thereby realizing the forward sixth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward seventh speed D 7 , the first clutch C 1  and the second and third brakes B 2  and B 3  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the eighth and ninth shafts TM 8  and TM 9  act as a fixed element by the operation of the second, third brake B 2  and B 3 , thereby realizing the forward seventh speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward eighth speed D 8 , the first and second clutch C 1  and C 2  and the third brake B 3  are simultaneously operated. 
     As a result, the second shaft TM 2  is connected with the fifth shaft TM 5  by the operation of the first clutch C 1 , and the sixth shaft TM 6  is interconnected with the seventh shaft TM 7  by the operation of the second clutch C 2 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the ninth shaft TM 9  acts as a fixed element by the operation of the third brake B 3 , thereby realizing the forward eighth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward ninth speed D 9 , the second clutch C 2  and the second and third brakes B 2  and B 3  are simultaneously operated. 
     As a result, the sixth shaft TM 6  is connected with the seventh shaft TM 7  by the operation of the second clutch C 2 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the eighth and ninth shafts TM 8  and TM 9  act as a fixed element by the operation of the second, third brake B 2  and B 3 , thereby realizing the forward ninth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the forward tenth speed D 10 , the second and third clutches C 2  and C 3  and the third brake B 3  are simultaneously operated. 
     As a result, the sixth shaft TM 6  is connected with the seventh shaft TM 7  by the operation of the second clutch C 2 , and the seventh shaft TM 7  is interconnected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the ninth shaft TM 9  acts as a fixed element by the operation of the third brake B 3 , thereby realizing the forward tenth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In some forms of the present disclosure, three reverse speeds are available. 
     In the reverse first speed REV 1 , the third clutch C 3  and the first and second brakes B 1  and B 2  are simultaneously operated. 
     As a result, the seventh shaft TM 7  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth and eighth shafts TM 4  and TM 8  act as a fixed element by the operation of the first and second brakes B 1  and B 2 , thereby realizing the reverse speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the reverse second speed REV 2 , the third clutch C 3  and the first and third brakes B 1  and B 3  are simultaneously operated. 
     As a result, the seventh shaft TM 7  is connected with the eighth shaft TM 8  by the operation of the third clutch C 3 . In this state, the input torque is input to the first shaft TM 1 . 
     In addition, the fourth and ninth shafts TM 4  and TM 9  act as a fixed element by the operation of the first, third brake B 1  and B 3 , thereby realizing the reverse speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
     In the reverse third speed REV 3 , the first, second, and third brakes B 1 , B 2 , and B 3  are simultaneously operated. 
     As a result, an input torque is input to the first shaft TM 1 . 
     In addition, the fourth and eighth, ninth shafts TM 4 , TM 8 , and TM 9  act as a fixed element by the operation of the first, second, third brake B 1 , B 2 , and B 3 , thereby realizing the reverse speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 . 
       FIG. 3  is a schematic diagram of a planetary gear train in some forms of the present disclosure. 
     According to a planetary gear train in some forms of the present disclosure shown in  FIG. 1 , the planetary gear sets are arranged in an order of second, first, fourth, third, and fifth planetary gear sets PG 2 , PG 1 , PG 4 , PG 3 , and PG 5  from an engine side. However, according to a planetary gear train in some forms of the present disclosure shown in  FIG. 3 , the planetary gear sets are arranged in an order of second, first, third, fourth, and fifth planetary gear sets PG 2 , PG 1 , PG 3 , PG 4 , and PG 5  from an engine side. 
     Such a form only differs in terms of the arrangement of the planetary gear set, and shows the same connection relations between the nine shafts TM 1  to TM 9 , three clutches C 1 , C 2 , and C 3 , and three brakes B 1  to B 3 , thereby providing the same operation. 
     As described above, a planetary gear train in some forms of the present disclosure utilizes five planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , and PG 5  operated by six engagement elements of three clutches C 1 , C 2 , and C 3  and three brakes B 1 , B 2 , and B 3 , and thereby achieves the ten forward speeds and at least one reverse speed. 
     In addition, the gear ratio span of at least 9.8 may be achieved so as to enhance an engine driving efficiency, and a linearity of step ratios of shift-stages may be improved as well, thereby contributing to a better drivability of the vehicle. 
     While achieving ten forward speeds and at least one reverse speed, engagement element operation is minimized so as to reduce a drag loss, thereby improving power delivery efficiency and fuel efficiency. 
     A torque-in-parallel scheme is applied to an output side planetary gear set, and thus the torque loads may be evenly distributed to planetary gear sets and engagement elements, thereby improving torque delivery efficiency and durability. 
     By using five planetary gear sets to realize ten forward speeds and at least one reverse speed, wider range of output gear ratios may be achieved, thereby improving linearity in step ratios of shift-stages. 
     The description of the disclosure is merely exemplary in nature and, thus, variations that do not depart from the substance of the disclosure are intended to be within the scope of the disclosure. Such variations are not to be regarded as a departure from the spirit and scope of the disclosure. 
     DESCRIPTION OF SYMBOLS 
     
         
         PG 1 , PG 2 , PG 3 , PG 4 , PG 5 : first, second, third, fourth, and fifth planetary gear sets 
         S 1 , S 2 , S 3 , S 4 , S 5 : first, second, third, fourth, and fifth sun gears 
         PC 1 , PC 2 , PC 3 , PC 4 , PC 5 : first, second, third, fourth, and fifth planet carriers 
         R 1 , R 2 , R 3 , R 4 , R 5 : first, second, third, fourth, and fifth ring gears 
         C 1 , C 2 , C 3 : first, second, and third clutches 
         B 1 , B 2 , B 3 : first, second, and third brakes 
         IS: input shaft 
         OS: output shaft 
         TM 1 , TM 2 , TM 3 , TM 4 , TM 5 , TM 6 , TM 7 , TM 8 , TM 9 : first, second, third, fourth, fifth, sixth, seventh, eighth, and ninth shafts