Planetary gear train of automatic transmission for vehicle

This application claims priority to and the benefit of Korean Patent Application No. 10-2017-0058309, filed on May 10, 2017, which is incorporated herein by reference in its entirety.

The present disclosure relates to an automatic transmission for a vehicle.

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 improving performance and efficiency of a vehicle in a so-called engine downsizing trend, and better linearity 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 deteriorate installability, production cost, weight and/or power flow efficiency.

In order to enhance fuel consumption of an automatic transmission having more shift-stages, an eight-speed automatic transmission has been introduced recently, and a planetary gear train for an automatic transmission enabling more shift-stages has been developed.

A recent eight-speed automatic transmission typically shows a gear ratio span, which affects the linearity of step ratios, in a level of 6.5 to 7.5.

In addition, 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 become a level above 9.0. Thus, high efficiency automatic transmission providing at least nine forward speeds may be more appropriate for enhancing driving efficiency and drivability of a vehicle.

The above information disclosed in this Background section is only for enhancement of understanding of the background of the present disclosure and therefore it may contain information that does not form the prior art that is already known to a person of ordinary skill in the art.

The present disclosure has been made in an effort to provide 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.

In addition, the present disclosure is motivated to employ 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 is motivated to improve flexibility of output gear ratio, thereby improving linearity of step ratios of shift-stages.

An exemplary planetary gear train of an automatic transmission for a vehicle includes: an input shaft; an output shaft; 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 fixedly connected with the first rotational element and the input shaft; a second shaft fixedly connected with the fourteenth rotational element and the output shaft; and a third shaft fixedly connected with the sixth rotational element and the thirteenth rotational element.

The planetary gear train further includes: a fourth shaft fixedly connected with the eighth rotational element, the eleventh rotational element, and the fifteenth rotational element; a fifth shaft fixedly connected with the fifth rotational element; a sixth shaft fixedly connected with the twelfth rotational element; a seventh shaft fixedly connected with the second rotational element and the fourth rotational element; an eighth shaft fixedly connected with the third rotational element and the seventh rotational element; and a ninth shaft fixedly connected with the ninth rotational element and the tenth rotational element.

The planetary gear train may further include six engagement elements, and each of the six engagement elements selectively connects a corresponding pair selected from the nine shafts, the input shaft, the output shaft, and the transmission housing. In particular, three engagement elements selected from the six engagement elements are operated for respective shift-stages.

The six engagement elements may include three clutches and three brakes.

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

The first, second, and third rotational elements may be respectively a first sun gear, a first planet carrier, and a first ring gear of the first planetary gear set. The fourth, fifth, and sixth rotational elements may be respectively a second sun gear, a second planet carrier, and a second ring gear of the second planetary gear set. The seventh, eighth, and ninth rotational elements may be respectively a third sun gear, a third planet carrier, and a third ring gear of the third planetary gear set. The tenth, eleventh, and twelfth rotational elements may be respectively a fourth sun gear, a fourth planet carrier, and a fourth ring gear of the fourth planetary gear set. The thirteenth, fourteenth, and fifteenth rotational elements may be respectively a fifth sun gear, a fifth planet carrier, and a fifth ring gear of the fifth planetary gear set.

The first, second, third, fourth, and fifth planetary gear sets may be arranged in an order of first, second, third, fourth, and fifth planetary gear sets from an engine side.

An exemplary 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 10.3 may be achieved so as to increase an engine driving efficiency, and a linearity of step ratios of shift-stages may be improved, thereby improving drivability of the vehicle.

While achieving ten forward speeds and at least one reverse speed, engagement element operation is limited so as to reduce a drag loss, thereby improving power delivery efficiency and fuel consumption.

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.

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 according to an exemplary form of the present disclosure; and

FIG. 2 is an operational chart of engagement elements for respective shift-stages applied to a planetary gear train according to an exemplary form of the present disclosure.

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

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 “directly” connected or interconnected includes elements that are fixedly connected, i.e. one element directly and/or fixedly connected to another element for rotation therewith.

FIG. 1 is a schematic diagram of a planetary gear train according to an exemplary form of the present disclosure.

Referring to FIG. 1 , a planetary gear train 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.

According to an exemplary form of the present disclosure, the planetary gear sets are arranged in the order of the first, the second, and the third, fourth, and fifth planetary gear sets PG 1 , PG 2 , PG 3 , PG 4 , 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 fourth rotational element N 4 are fixedly interconnected, the third rotational element N 3 and the seventh rotational element N 7 are fixedly interconnected, the ninth rotational element N 9 and the tenth rotational element N 10 are fixedly interconnected, the sixth rotational element N 6 and the thirteenth rotational element N 13 are fixedly interconnected, the eighth rotational element N 8 , the eleventh rotational element N 11 , 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 arranged as follows.

Each of the ten shafts TM 1 to TM 9 may be a rotational member that directly 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 first rotational element N 1 (first sun gear S 1 ), 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 sixth rotational element N 6 (second ring gear R 2 ) and the thirteenth rotational element N 13 (fifth sun gear S 5 ).

The fourth shaft TM 4 is fixedly connected with the eighth rotational element N 8 (third planet carrier PC 3 ), the eleventh rotational element N 11 (fourth planet carrier PC 4 ), and the fifteenth rotational element N 15 (fifth ring gear R 5 ).

The fifth shaft TM 5 is connected with fifth rotational element N 5 (second planet carrier PC 2 ).

The sixth shaft TM 6 is connected with twelfth rotational element N 12 (fourth ring gear R 4 ).

The seventh shaft TM 7 is connected with the second rotational element N 2 (first planet carrier PC 1 ) and the fourth rotational element N 4 (second sun gear S 2 ).

The eighth shaft TM 8 is connected with the third rotational element N 3 (first ring gear R 1 ) and the seventh rotational element N 7 (third sun gear S 3 ).

The ninth shaft TM 9 is connected with the ninth rotational element N 9 (third ring gear R 3 ) and the tenth rotational element N 10 (fourth sun gear S 4 ).

The third shaft TM 3 is selectively connected with the sixth shaft TM 6 , and the third shaft TM 3 and the fifth shaft TM 5 are selectively connected with the first shaft TM 1 .

In addition, the seventh shaft TM 7 , 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 elements including 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 first shaft TM 1 and the third shaft TM 3 , and selectively connects the first shaft TM 1 and the third shaft TM 3 , thereby controlling power delivery therebetween.

The second clutch C 2 is arranged between the first shaft TM 1 and the fifth shaft TM 5 , and selectively connects the first shaft TM 1 and the fifth shaft TM 5 , thereby controlling power delivery therebetween.

The third clutch C 3 is arranged between the third shaft TM 3 and the sixth shaft TM 6 , and selectively connects the third shaft TM 3 and the sixth shaft TM 6 , thereby controlling power delivery therebetween.

The first brake B 1 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 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 first clutch C 1 and the second clutch C 2 have been described above to selectively connecting the third shaft TM 3 and the fifth shaft TM 5 to the first shaft TM 1 . Referring to FIG. 1 , the first shaft TM 1 is always connected to the input shaft IS, and thus, it may be regarded that the first and second clutches C 1 and C 2 selectively connect the input shaft IS to the third and fifth shafts TM 3 and TM 5 respectively.

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 according to an exemplary form of the present disclosure.

Referring to FIG. 2 , a planetary gear train 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 first clutch C 1 and the first and third brakes B 1 and B 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the third shaft TM 3 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 seventh and ninth shafts TM 7 and TM 9 act as a fixed element by the operation of the first, third brake B 1 and B 3 , 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 clutch C 2 and the first and third brakes B 1 and B 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the fifth shaft TM 5 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 seventh and ninth shafts TM 7 and TM 9 act as a fixed element by the operation of the first, third brake B 1 and B 3 , 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 second clutch C 2 and the second and third brakes B 2 and B 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the fifth shaft TM 5 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 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 second clutch C 1 and C 2 and the third brake B 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the third shaft TM 3 by the operation of the first clutch C 1 , and the first shaft TM 1 is interconnected with the fifth shaft TM 5 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 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 second and third clutches C 2 and C 3 and the third brake B 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the fifth shaft TM 5 by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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 fifth speed and outputting a shifted torque to 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 first shaft TM 1 is connected with the third shaft TM 3 by the operation of the first clutch C 1 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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, second, and third clutches C 1 , C 2 , and C 3 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the third shaft TM 3 by the operation of the first clutch C 1 , the first shaft TM 1 is interconnected with the fifth shaft TM 5 by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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 seventh speed and outputting a shifted torque through the output shaft OS connected with the second shaft TM 2 .

In the forward eighth speed D 8 , the first and third clutches C 1 and C 3 and the second brake B 2 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the third shaft TM 3 by the operation of the first clutch C 1 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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 eighth shaft TM 8 acts as a fixed element by the operation of the second brake B 2 , 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 and third clutches C 2 and C 3 and the second brake B 2 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the fifth shaft TM 5 by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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 eighth shaft TM 8 acts as a fixed element by the operation of the second brake B 2 , 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 first brake B 1 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the fifth shaft TM 5 by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the sixth shaft TM 6 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 seventh shaft TM 7 acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward tenth speed and outputting a shifted torque to the output shaft OS connected with the second shaft TM 2 .

In the reverse speed REV, the third clutch C 3 and the first and third brakes B 1 and B 3 are simultaneously operated.

As a result, the third shaft TM 3 is connected with the sixth shaft TM 6 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 seventh and ninth shafts TM 7 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 .

As described above, a planetary gear train according to an exemplary form 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 10.3 may be achieved so as to increase an engine driving efficiency, and a linearity of step ratios of shift-stages may be improved, thereby improving drivability of the vehicle.

While achieving ten forward speeds and at least one reverse speed, engagement element operation is limited so as to reduce a drag loss, thereby improving power delivery efficiency and fuel consumption.

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.

While this present disclosure has been described in connection with what is presently considered to be practical exemplary forms, it is to be understood that the present disclosure is not limited to the disclosed forms, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

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