Planetary gear train of transmission for vehicle

This application claims priority to Korean Patent Application No. 10-2017-0116709, filed in the Korean Intellectual Property Office on Sep. 12, 2017, which application is hereby incorporated herein by reference.

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

Research on realizing more shift-stages of an automatic transmission is undertaken to achieve enhancement of fuel consumption and better drivability, and recently, the increase in oil prices has triggered a hard competition in enhancing fuel consumption of a vehicle.

In this sense, research on an engine to achieve weight reduction and to enhance fuel consumption by so-called downsizing research for use with an automatic transmission has been performed to simultaneously provide better drivability and fuel consumption by achieving more shift stages for the automatic transmission.

In order to achieve more shift stages for an automatic transmission, the number of parts is typically increased, which may adversely affect installability, production cost, weight and/or power flow efficiency.

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 with 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 seven engagement elements (which may be 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, is sometimes attempted. However, such an arrangement may not be widely applicable, and using dog clutches may easily deteriorate shift-feel.

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

Embodiments in the present disclosure relate to a planetary gear train of an automatic transmission for a vehicle enabling at least ten forward speeds, thereby providing better performance and fuel efficiency of a vehicle.

A planetary gear train according to an exemplary embodiment includes an input shaft for receiving an engine torque, an output shaft for outputting a shifted torque, a first planetary gear set having first, second, and third rotational elements, a second planetary gear set having fourth, fifth, and sixth rotational elements, a third planetary gear set having seventh, eighth, and ninth rotational elements, and a fourth planetary gear set having tenth, eleventh, and twelfth rotational elements. An embodiment planetary gear train may further include a first shaft fixedly connected with the third rotational element and selectively connected with the input shaft, a second shaft fixedly connected with the ninth rotational element and selectively connected with the input shaft, a third shaft fixedly connected with the eleventh rotational element and fixedly connected with the output shaft, a fourth shaft fixedly connected with the first rotational element, the fourth rotational element, and the seventh rotational element, a fifth shaft fixedly connected with the second rotational element and the tenth rotational element, and a plurality of shafts each selectively connecting a corresponding element to the transmission housing, with the corresponding element being a rotational element of the second, third, and fourth planetary gear sets that is not fixedly interconnected.

The plurality of shafts may include a sixth shaft fixedly connected with the fifth rotational element and the eighth rotational element and selectively connected with the transmission housing, and a seventh shaft fixedly connected with the sixth rotational element and the twelfth rotational element and selectively connected with the transmission housing. The input shaft and the first shaft, the input shaft and the second shaft, the first shaft and the fifth shaft, and the first shaft and the sixth shaft may be selectively interconnected with each other respectively.

Embodiments of the planetary gear train may further include four clutches each selectively connecting a corresponding pair among the input shaft, the output shaft, and the first to seventh shafts, and two brakes selectively connecting the sixth shaft and the seventh shaft to the transmission housing respectively.

The four clutches may include a first clutch arranged between the input shaft and the first shaft, a second clutch arranged between the input shaft and the second shaft, a third clutch arranged between the first shaft and the fifth shaft, and a fourth clutch arranged between the first shaft and the sixth shaft. The two brakes may include a first brake arranged between the sixth shaft and the transmission housing, and a second brake arranged between the seventh shaft and the transmission housing.

The first planetary gear set may be a single pinion planetary gear set having a first sun gear, a first planet carrier, and a first ring gear as the first, second, and third rotational elements. The second planetary gear set may be a single pinion planetary gear set having a second sun gear, a second planet carrier, and a second ring gear as the fourth, fifth, and sixth rotational elements. The third planetary gear set may be a single pinion planetary gear set having a third sun gear, a third planet carrier, and a third ring gear as the seventh, eighth, and ninth rotational elements. The fourth planetary gear set may be a single pinion planetary gear set having a fourth sun gear, a fourth planet carrier, and a fourth ring gear as the tenth, eleventh, and twelfth rotational elements.

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

A planetary gear train according to an exemplary embodiment of the present invention may realize at least ten forward speeds and one reverse speed by combination of four planetary gear sets using simple planetary gear sets together with six engagement elements.

In addition, a planetary gear train according to an exemplary embodiment of the present invention may substantially improve driving stability by realizing shift-stages appropriate for rotation speed of an engine using multi-stages of an automatic transmission.

In addition, a planetary gear train according to an exemplary embodiment of the present invention may maximize engine driving efficiency using multi-stages of an automatic transmission, and may improve power delivery performance and fuel consumption.

Further, effects that can be obtained or expected from exemplary embodiments of the present invention are directly or suggestively described in the following detailed description. That is, various effects expected from exemplary embodiments of the present invention will be described in the following detailed description.

FIG. 1 is a schematic diagram of a planetary gear train according to an exemplary embodiment of the present invention; and

FIG. 2 is an operational chart for respective control elements at respective shift-stages applicable to a planetary gear train according to an exemplary embodiment of the present invention.

Hereinafter, an exemplary embodiment of the present invention will be described in detail with reference to drawings.

The drawings and description are to be regarded as illustrative in nature and not restrictive, and like reference numerals designate like elements throughout the specification.

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.

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

Referring to FIG. 1 , a planetary gear train according to an exemplary embodiment of the present invention includes first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 arranged on a same axis, an input shaft IS, an output shaft OS, seven shafts TM 1 to TM 7 interconnecting rotational elements of the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , engagement elements of four clutches C 1 to C 4 and two brakes B 1 and B 2 , 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 the third, the second, and the fourth, first planetary gear set (PG 3 , PG 2 , PG 4 , PG 1 ), from an engine side.

The input shaft IS is an input member and may receive a torque from a crankshaft of an engine through a torque converter.

The output shaft OS is an output member arranged on a same axis with the input shaft IS, and outputs a shifted driving torque to a driveshaft 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 engaged with the first sun gear S 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 engaged with the second sun gear S 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 engaged with the third sun gear S 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 engaged with the fourth sun gear S 4 . The fourth sun gear S 4 acts as a tenth rotational element N 10 , the fourth planet carrier PC 4 acts as an eleventh rotational element N 11 , and the fourth ring gear R 4 acts as a twelfth rotational element N 12 .

In the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , the first rotational element N 1 is fixedly connected with the fourth rotational element N 4 and the seventh rotational element N 7 , the second rotational element N 2 is fixedly connected with the tenth rotational element N 10 , the fifth rotational element N 5 is fixedly connected with the eighth rotational element N 8 , the sixth rotational element N 6 is fixedly connected with twelfth rotational element N 12 , and seven shafts TM 1 to TM 7 are formed.

The seven shafts TM 1 to TM 7 are hereinafter described in detail.

The first shaft TM 1 is fixedly connected with the third rotational element N 3 (first ring gear R 1 ), and selectively connected with the input shaft IS, thereby selectively acting as an input element.

The second shaft TM 2 is fixedly connected with the ninth rotational element N 9 (third ring gear R 3 ), and selectively connected with the input shaft IS, thereby selectively acting as an input element.

The third shaft TM 3 is fixedly connected with the eleventh rotational element N 11 (fourth planet carrier PC 4 ), and fixedly connected with the output shaft OS thereby always acting as an output element.

The fourth shaft TM 4 is fixedly connected with the first rotational element N 1 (first sun gear S 1 ), the fourth rotational element N 4 (second sun gear S 2 ), and the seventh rotational element N 7 (third sun gear S 3 ).

The fifth shaft TM 5 is fixedly connected with second rotational element N 2 (first planet carrier PC 1 ) and tenth rotational element N 10 (fourth sun gear S 4 ).

The sixth shaft TM 6 is fixedly connected with fifth rotational element N 5 (second planet carrier PC 2 ) and eighth rotational element N 8 (third planet carrier PC 3 ).

The seventh shaft TM 7 is fixedly connected with sixth rotational element N 6 (second ring gear R 2 ) and twelfth rotational element N 12 (fourth ring gear R 4 ).

Each of the seven shafts TM 1 to TM 7 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 , and PG 4 , 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.

In the disclosure, when two or more members are described to be “fixedly connected”, where the member may be any one or more of a shaft, an input shaft, an output shaft, a rotational member, and a transmission housing, it means that the fixedly connected members always rotate at a same speed.

When two or more members are described to be “selectively connected” by an engagement element, it means that the selectively connected members rotates separately when the engagement element is not engaged, and rotates at a same speed when the engagement element is engaged. It may be understood that in the case that a member is “selectively connected” with a transmission housing by an engagement element, the member may be stationary when the engagement element is engaged.

The first shaft TM 1 is selectively connected with the input shaft IS, the second shaft TM 2 is selectively connected with the input shaft IS, and the first shaft TM 1 is selectively connected with the fifth shaft TM 5 and the sixth shaft TM 6 respectively.

The sixth shaft TM 6 and the seventh shaft TM 7 are selectively connected with the transmission housing H, thereby selectively acting as fixed elements respectively.

The engagement elements of four clutches C 1 , C 2 , C 3 , and C 4 are arranged between the seven shafts TM 1 to TM 7 , the input shaft IS, and the output shaft OS, so as to form selective connections.

The seven shafts TM 1 to TM 7 may be selectively connected with the transmission housing H, by control elements of two brakes B 1 and B 2 .

The six engagement elements of the four clutches C 1 to C 4 and the two brakes B 1 and B 2 are arranged as follows.

The first clutch C 1 is arranged between the input shaft IS and the first shaft TM 1 , and selectively connects the input shaft IS and the first shaft TM 1 , thereby controlling power delivery therebetween.

The second clutch C 2 is arranged between the input shaft IS and the second shaft TM 2 , and selectively connects the input shaft IS and the second shaft TM 2 , thereby controlling power delivery therebetween.

The third clutch C 3 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 fourth clutch C 4 is arranged between the first shaft TM 1 and the sixth shaft TM 6 , and selectively connects the first shaft TM 1 and the sixth shaft TM 6 , thereby controlling power delivery therebetween.

The first brake B 1 is arranged between the sixth shaft TM 6 and the transmission housing H, and selectively connects the sixth shaft TM 6 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 engagement elements of the first, second, third, and fourth clutches C 1 , C 2 , C 3 , and C 4 and the first and second brakes B 1 and B 2 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 for respective control elements at respective shift-stages applicable to a planetary gear train according to an exemplary embodiment of the present invention.

Referring to FIG. 2 , a planetary gear train according to an exemplary embodiment of the present invention realizes shifting between ten forward speeds and one reverse speed by operating three elements among the engagement elements of the first, second, third, and fourth clutches C 1 , C 2 , C 3 , and C 4 and the first and second brakes B 1 and B 2 .

In the forward first speed D 1 , the first clutch C 1 and the first and second brakes B 1 and B 2 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the input shaft IS by the operation of the first clutch C 1 . In this state, the input torque is input to the first shaft TM 1 .

In the above state, the sixth and seventh shafts TM 6 and TM 7 act as fixed elements respectively 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 third shaft TM 3 .

In the forward second speed D 2 , 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 input shaft IS by the operation of the first clutch C 1 , and the first shaft TM 1 is connected with the fifth shaft TM 5 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 second brake B 2 , thereby realizing the forward second speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

In the forward third speed D 3 , the first and fourth clutches C 1 and C 4 and the second brake B 2 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the input shaft IS by the operation of the first clutch C 1 , and the first shaft TM 1 is connected with the sixth shaft TM 6 by the operation of the fourth clutch C 4 . 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 second brake B 2 , thereby realizing the forward third speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

In the forward fourth speed D 4 , the first and second clutch C 1 and C 2 and the second brake B 2 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the input shaft IS by the operation of the first clutch C 1 , and the second shaft TM 2 is connected with the input shaft IS by the operation of the second clutch C 2 . In this state, an input torque is input to the first shaft TM 1 and the second shaft TM 2 .

In addition, the seventh shaft TM 7 acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward fourth speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

In the forward fifth speed D 5 , the second and fourth clutches C 2 and C 4 and the second brake B 2 are simultaneously operated.

As a result, the second shaft TM 2 is connected with the input shaft IS by the operation of the second clutch C 2 , and the first shaft TM 1 is connected with the sixth shaft TM 6 by the operation of the fourth clutch C 4 . In this state, the input torque is input to the second shaft TM 2 .

In addition, the seventh shaft TM 7 acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward fifth speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

In the forward sixth speed D 6 , the second and third clutches C 2 and C 3 and the second brake B 2 are simultaneously operated.

As a result, the second shaft TM 2 is connected with the input shaft IS by the operation of the second clutch C 2 , and the first shaft TM 1 is connected with the fifth shaft TM 5 by the operation of the third clutch C 3 . In this state, the input torque is input to the second shaft TM 2 .

In addition, the seventh shaft TM 7 acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward sixth speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

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 input shaft IS by the operation of the first clutch C 1 , the second shaft TM 2 is connected with the input shaft IS by the operation of the second clutch C 2 , and the first shaft TM 1 is fixedly connected with the fifth shaft TM 5 by the operation of the third clutch C 3 .

Then, the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 integrally rotate, and a torque is input to the first shaft TM 1 and the second shaft TM 2 , thereby realizing the forward seventh speed where a torque is output as inputted, and outputting a shifted torque to the output shaft OS connected with the third shaft TM 3 .

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

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

In the forward ninth speed D 9 , the first and fourth clutches C 1 and C 4 and the first brake B 1 are simultaneously operated.

As a result, the first shaft TM 1 is connected with the input shaft IS by the operation of the first clutch C 1 , and the first shaft TM 1 is connected with the sixth shaft TM 6 by the operation of the fourth clutch C 4 . In this state, the input torque is input to the first shaft TM 1 .

In addition, the sixth shaft TM 6 acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward ninth speed and outputting a shifted torque to the output shaft OS connected with the third shaft TM 2 .

In the forward tenth speed D 10 , the first and second clutch C 1 and C 2 and the first brake B 1 are simultaneously operated.

As a result, the first shaft TM 1 and the second shaft TM 2 are connected with the input shaft IS by the operation of the first and second clutch C 1 and C 2 . In this state, a torque is input to the first shaft TM 1 and the second shaft TM 2 .

In addition, the sixth shaft TM 6 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 third shaft TM 3 .

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

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

As described above, a planetary gear train according to an exemplary embodiment of the present invention may realize ten forward speeds and one reverse speed by operating the 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 two brakes B 1 and B 2 .

In addition, a planetary gear train according to an exemplary embodiment of the present invention may substantially improve driving stability by realizing shift-stages appropriate for rotation speed of an engine due to multi-stages of an automatic transmission.

In addition, a planetary gear train according to an exemplary embodiment of the present invention may maximize engine driving efficiency by multi-stages of an automatic transmission, and may improve power delivery performance and fuel consumption.

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