Planetary gear train of automatic transmission for vehicle

The present application claims priority to Korean Patent Application No. 10-2015-0167990, filed Nov. 27, 2015, the entire contents of which is incorporated herein for all purposes by this reference.

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 for a vehicle that improves power delivery performance and fuel economy by achieving eight forward speed stages with a minimum number of constituent elements being used and improves silent driving of the vehicle by using operation point positioned at a low engine speed.

Recent increases in oil prices are triggering stiff competition among auto-makers in enhancing fuel consumption of a vehicle.

Therefore, research is being conducted on engines in terms of reducing weight and improving fuel efficiency by down-sizing, and research is also being conducted to ensure both drivability and competitiveness for maximizing fuel efficiency by implementing an automatic transmission with multiple speed stages.

However, in the case of the automatic transmission, the number of internal components increases as the number of gear shift stages is increased, which may deteriorate installability, production cost, weight and/or power flow efficiency.

Accordingly, development of a planetary gear train which may achieve maximum efficiency with a small number of components is important in order to increase a fuel economy enhancement effect through the multiple-speeds.

In this aspect, in recent years, 8-speed automatic transmissions tend to be implemented and the research and development of a planetary gear train capable of implementing more speed stages has also been actively conducted.

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.

Various aspects of the present invention are directed to providing a planetary gear train of an automatic transmission for a vehicle having advantages of improving power delivery performance and fuel economy by achieving eight forward speed stages and one reverse speed stage.

Various aspects of the present invention are additionally directed to providing a planetary gear train of an automatic transmission for a vehicle having further advantages of improving silent driving of the vehicle by using operation point positioned at a low rotational speed region 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 receiving torque of an engine, an output shaft outputting changed torque of the engine, 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 rotation shaft directly connected to the first rotation element and selectively connectable to a transmission housing, a second rotation shaft directly connecting the second rotation element to the fourth rotation element, selectively connectable to the first rotation shaft, and directly connected to the input shaft, a third rotation shaft directly connecting the third rotation element to the sixth rotation element and selectively connectable to the transmission housing, a fourth rotation shaft directly connecting the fifth rotation element to the seventh rotation element, a fifth rotation shaft directly connecting the eighth rotation element to the twelfth rotation element and selectively connectable to at least one of the second rotation shaft and the third rotation shaft, a sixth rotation shaft directly connecting the ninth rotation element to the eleventh rotation element and directly connected to the output shaft, and a seventh rotation shaft directly connected to the tenth rotation element and selectively connectable to the transmission housing.

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

The planetary gear train may further includes a first clutch selectively connecting the first rotation shaft with the second rotation shaft, a second clutch selectively connecting the second rotation shaft with the fifth rotation shaft, a third clutch selectively connecting the third rotation shaft with the fifth rotation shaft, a first brake selectively connecting the first rotation shaft with the transmission housing, a second brake selectively connecting the third rotation shaft with the transmission housing, and a third brake selectively connecting the seventh rotation shaft with the transmission housing.

A first forward speed stage may be achieved by operation of the second and third brakes, a second forward speed stage may be achieved by operation of the third clutch and the third brake, a third forward speed stage may be achieved by operation of the first clutch and the third brake, a fourth forward speed stage may be achieved by operation of the first and third brakes, a fifth forward speed stage may be achieved by operation of the second clutch and the third brake, a sixth forward speed stage may be achieved by operation of the second clutch and the first brake, a seventh forward speed stage may be achieved by operation of the first and second clutches, an eighth forward speed stage may be achieved by operation of the second clutch and the second brake, and a reverse speed stage may be achieved by operation of the third clutch and the second brake.

A planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving torque of an engine, an output shaft outputting changed torque of the engine, a first planetary gear set being a single pinion planetary gear set and including first, second, and third rotation elements, a second planetary gear set being a single pinion planetary gear set and including fourth, fifth, and sixth rotation elements, a third planetary gear set being a single pinion planetary gear set and including seventh, eighth, and ninth rotation elements, a fourth planetary gear set being a single pinion planetary gear set and including tenth, eleventh, and twelfth rotation elements, a first rotation shaft directly connected to the first rotation element and selectively connectable to a transmission housing, a second rotation shaft directly connecting the second rotation element to the fourth rotation element, selectively connectable to the first rotation shaft, and directly connected to the input shaft, a third rotation shaft directly connecting the third rotation element to the sixth rotation element and selectively connectable to the transmission housing, a fourth rotation shaft directly connecting the fifth rotation element to the seventh rotation element, a fifth rotation shaft directly connecting the eighth rotation element to the twelfth rotation element and selectively connectable to at least one of the second rotation shaft and the third rotation shaft, a sixth rotation shaft directly connecting the ninth rotation element to the eleventh rotation element and directly connected to the output shaft, a seventh rotation shaft directly connected to the tenth rotation element and selectively connectable to the transmission housing, a first clutch selectively connecting the first rotation shaft with the second rotation shaft, a second clutch selectively connecting the second rotation shaft with the fifth rotation shaft, a third clutch selectively connecting the third rotation shaft with the fifth rotation shaft, a first brake selectively connecting the first rotation shaft with the transmission housing, a second brake selectively connecting the third rotation shaft with the transmission housing, and a third brake selectively connecting the seventh rotation shaft 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, respectively.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving torque of an engine, an output shaft outputting changed torque, a first planetary gear set being a single pinion planetary gear set and including a first sun gear, a first planet carrier, and a first ring gear, a second planetary gear set being a single pinion planetary gear set and including a second sun gear, a second planet carrier, and a second ring gear, a third planetary gear set being a single pinion planetary gear set and including a third sun gear, a third planet carrier, and a third ring gear, and a fourth planetary gear set being a single pinion planetary gear set and including a fourth sun gear, a fourth planet carrier, and a fourth ring gear, in which the first sun gear may be selectively connectable to a transmission housing and selectively connectable to the first planet carrier, the first planet carrier may be directly connected to the input shaft, directly connected to the second sun gear, and selectively connectable to the third planet carrier, the first ring gear may be selectively connectable to the transmission housing, directly connected to the second ring gear, and selectively connectable to the third planet carrier and the fourth ring gear, the second planet carrier may be directly connected to the third sun gear, the third planet carrier may be directly connected to the fourth ring gear, the third ring gear may be directly connected to the fourth planet carrier and directly connected to the output shaft, and the fourth sun gear may be selectively connectable to the transmission housing.

The planetary gear train may further include a first clutch selectively connecting the first sun gear with the first planet carrier, a second clutch selectively connecting the first planet carrier and the second sun gear with the third planet carrier and the fourth ring gear, a third clutch selectively connecting the first ring gear and the second ring gear with the third planet carrier and the fourth ring gear, a first brake selectively connecting the first sun gear with the transmission housing, a second brake selectively connecting the first ring gear with the transmission housing, and a third brake selectively connecting the fourth sun gear with the transmission housing.

The planetary gear train according to various embodiments of the present invention achieves eight forward speed stages and one reverse speed stage by combining four planetary gear sets being simple planetary gear sets with six control elements.

In addition, the planetary gear train according to various embodiments of the present invention improves silent driving because speed stages suitable to a rotational speed of the engine are achieved due to multiple-speed stages of the automatic transmission.

In addition, the planetary gear train according to various embodiments of the present invention maximizes driving efficiency of the engine 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.

FIG. 1 is a schematic diagram of a planetary gear train according to various embodiments of the present invention.

FIG. 2 is an operation chart of control elements at each speed stage 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.

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 sets PG 1 , PG 2 , PG 3 , and PG 4 disposed on the same axis, an input shaft IS, an output shaft OS, seven rotation shafts TM 1 to TM 7 connected to at least one of rotation elements of the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 , six control elements C 1 to C 3 and B 1 to B 3 , and a transmission housing H.

Torque input from the input shaft IS is changed by cooperation of the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 and the changed torque is output through the output shaft OS.

The planetary gear sets are disposed 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, after being torque-converted through a torque converter, is input into the input shaft IS.

The output shaft OS is an output member, is disposed in parallel with the input shaft IS, and transmits driving torque to a driving wheel 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 first pinion P 1 that is externally meshed with the first sun gear S 1 , and a first ring gear R 1 that is internally meshed with the first pinion P 1 respectively as first, second, and third rotation elements N 1 , N 2 , and 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 second pinion P 2 that is externally meshed with the second sun gear S 2 , and a second ring gear R 2 that is internally meshed with the second pinion P 2 respectively as fourth, fifth, and sixth rotation elements N 4 , N 5 , and 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 third pinion P 3 that is externally meshed with the third sun gear S 3 , and a third ring gear R 3 that is internally meshed with the third pinion P 3 respectively as seventh, eighth, and ninth rotation elements N 7 , N 8 , and 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 fourth pinion P 4 that is externally meshed with the fourth sun gear S 4 , and a fourth ring gear R 4 that is internally meshed with the fourth pinion P 4 respectively as tenth, eleventh, and twelfth rotation elements N 10 , N 11 , and N 12 .

The second rotation element N 2 is directly connected to the fourth rotation element N 4 , the third rotation element N 3 is directly connected to the sixth rotation element N 6 , the fifth rotation element N 5 is directly connected to the seventh rotation element N 7 , the eighth rotation element N 8 is directly connected to the twelfth rotation element N 12 , and the ninth rotation element N 9 is directly connected to the eleventh rotation element N 11 such that the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 includes seven rotation shafts TM 1 to TM 7 .

The seven rotation shafts TM 1 to TM 7 will be described in detail.

The first rotation shaft TM 1 is directly connected to the first rotation element Ni (first sun gear S 1 ) and is selectively connectable to the transmission housing H so as to be operated as a selective fixed element.

The second rotation shaft TM 2 directly connects the second rotation element N 2 (first planet carrier PC 1 ) with the fourth rotation element N 4 (second sun gear S 2 ), is selectively connectable to the first rotation shaft TM 1 , and is directly connected to the input shaft IS so as to be continuously operated as an input element.

The third rotation shaft TM 3 directly connects the third rotation element N 3 (first ring gear R 1 ) with the sixth rotation element N 6 (second ring gear R 2 ) and is selectively connectable to the transmission housing H so as to be operated as a selective fixed element.

The fourth rotation shaft TM 4 directly connects the fifth rotation element N 5 (second planet carrier PC 2 ) with the seventh rotation element N 7 (third sun gear S 3 ).

The fifth rotation shaft TM 5 directly connects the eighth rotation element N 8 (third planet carrier PC 3 ) with the twelfth rotation element N 12 (fourth ring gear R 4 ) and is selectively connectable to the third rotation shaft TM 3 .

The sixth rotation shaft TM 6 directly connects the ninth rotation element N 9 (third ring gear R 3 ) with the eleventh rotation element N 11 (fourth planet carrier PC 4 ) and is directly connected to the output shaft OS so as to be continuously operated as an output element.

The seventh rotation shaft TM 7 is directly connected to the tenth rotation element N 10 (fourth sun gear S 4 ) and is selectively connectable to the transmission housing H.

In addition, three clutches C 1 , C 2 , and C 3 that are control elements are disposed at portions at which two rotation shafts among the rotation shafts TM 1 to TM 7 are selectively connectable to each other.

In addition, three brakes B 1 , B 2 , and B 3 that are control elements are disposed at portions at which any one rotation shaft among the rotation shafts TM 1 to TM 7 is selectively connectable to the transmission housing H.

Arrangements of the six control elements C 1 to C 3 and B 1 to B 3 are described in detail.

The first clutch C 1 is disposed between the first rotation shaft TM 1 and the second rotation shaft TM 2 and selectively connects the first rotation shaft TM 1 with the second rotation shaft TM 2 .

The second clutch C 2 is disposed between the second rotation shaft TM 2 and the fifth rotation shaft TM 5 and selectively connects the second rotation shaft TM 2 with the fifth rotation shaft TM 5 .

The third clutch C 3 is disposed between the third rotation shaft TM 3 and the fifth rotation shaft TM 5 and selectively connects the third rotation shaft TM 3 with the fifth rotation shaft TM 5 .

The first brake B 1 is disposed between the first rotation shaft TM 1 and the transmission housing H and causes the first rotation shaft TM 1 to be operated as the selective fixed element.

The second brake B 2 is disposed between the third rotation shaft TM 3 and the transmission housing H and causes the third rotation shaft TM 3 to be operated as the selective fixed element.

The third brake B 3 is disposed between the seventh rotation shaft TM 7 and the transmission housing H and causes the seventh rotation shaft TM 7 to be operated as the selective fixed element.

The control elements including 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 multi-plates friction elements of wet type that are operated by hydraulic pressure.

FIG. 2 is an operation chart of control elements at each speed stage in the planetary gear train according to various embodiments of the present invention.

As shown in FIG. 2 , two control elements are operated at each speed stage in the planetary gear train according to various embodiments of the present invention.

The second and third brakes B 2 and B 3 are operated at a first forward speed stage D 1 .

In a state that torque of the input shaft IS is input to the second rotation shaft TM 2 , the third and seventh rotation shafts TM 3 and TM 7 are operated as the fixed elements by operation of the second and third brakes B 2 and B 3 . Therefore, the torque of the input shaft IS is shifted into the first forward speed stage, and the first forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The third clutch C 3 and the third brake B 3 are operated at a second forward speed stage D 2 .

In a state that the third rotation shaft TM 3 is connected to the fifth rotation shaft TM 5 by operation of the third clutch C 3 , the torque of the input shaft IS is input to the second rotation shaft TM 2 . In addition, the seventh rotation shaft TM 7 is operated as the fixed element by operation of the third brake B 3 . Therefore, the torque of the input shaft IS is shifted into the second forward speed stage, and the second forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The first clutch C 1 and the third brake B 3 are operated at a third forward speed stage D 3 .

In a state that the first rotation shaft TM 1 is connected to the second rotation shaft TM 2 by operation of the first clutch C 1 , the torque of the input shaft IS is input to the first rotation shaft TM 1 and the second rotation shaft TM 2 . In addition, the seventh rotation shaft TM 7 is operated as the fixed element by operation of the third brake B 3 . Therefore, the torque of the input shaft IS is shifted into the third forward speed stage, and the third forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The first and third brakes B 1 and B 3 are operated at a fourth forward speed stage D 4 . In a state that the torque of the input shaft IS is input to the second rotation shaft TM 2 , the first and seventh rotation shafts TM 1 and TM 7 are operated as the fixed elements by operation of the first and third brakes B 1 and B 3 . Therefore, the torque of the input shaft IS is shifted into the fourth forward speed stage, and the fourth forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The second clutch C 2 and the third brake B 3 are operated at a fifth forward speed stage D 5 .

In a state that the second rotation shaft TM 2 is connected to the fifth rotation shaft TM 5 by operation of the second clutch C 2 , the torque of the input shaft IS is input to the second rotation shaft TM 2 and the fifth rotation shaft TM 5 . In addition, the seventh rotation shaft TM 7 is operated as the fixed element by operation of the third brake B 3 . Therefore, the torque of the input shaft IS is shifted into the fifth forward speed stage, and the fifth forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The second clutch C 2 and the first brake B 1 are operated at a sixth forward speed stage D 6 .

In a state that the second rotation shaft TM 2 is connected to the fifth rotation shaft TM 5 by operation of the second clutch C 2 , the torque of the input shaft IS is input to the second rotation shaft TM 2 and the fifth rotation shaft TM 5 . In addition, the first rotation shaft TM 1 is operated as the fixed element by operation of the first brake B 1 . Therefore, the torque of the input shaft IS is shifted into the sixth forward speed stage, and the sixth forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The first clutch C 1 and the second clutch C 2 are operated at a seventh forward speed stage D 7 .

In a state that the first rotation shaft TM 1 is connected to the second rotation shaft TM 2 by operation of the first clutch C 1 and the second rotation shaft TM 2 is connected to the fifth rotation shaft TM 5 by operation of the second clutch C 2 , the torque of the input shaft IS is input to the first, second, and fifth rotation shafts TM 1 , TM 2 , and TM 5 . In this case, the first, second, third, and fourth planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 become lock-up states. Therefore, the torque of the input shaft IS is shifted into the seventh forward speed stage, and the seventh forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 . At the seventh forward speed stage, the same rotation speed as the input shaft IS is output.

The second clutch C 2 and the second brake B 2 are operated at an eighth forward speed stage D 8 .

In a state that the second rotation shaft TM 2 is connected to the fifth rotation shaft TM 5 by operation of the second clutch C 2 , the torque of the input shaft IS is input to the second rotation shaft TM 2 and the fifth rotation shaft TM 5 . In addition, the third rotation shaft TM 3 is operated as the fixed element by operation of the second brake B 2 . Therefore, the torque of the input shaft IS is shifted into the eighth forward speed stage, and the eighth forward speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The third clutch C 3 and the second brake B 2 are operated at a reverse speed stage REV.

In a state that the third rotation shaft TM 3 is connected to the fifth rotation shaft TM 5 by operation of the third clutch C 3 , the torque of the input shaft IS is input to the second rotation shaft TM 2 . In addition, the third rotation shaft TM 3 is operated as the fixed element by operation of the second brake B 2 . Therefore, the torque of the input shaft IS is shifted into the reverse speed stage, and the reverse speed stage is output through the output shaft OS connected to the sixth rotation shaft TM 6 .

The planetary gear train according to various embodiments of the present invention achieves eight forward speed stages and one reverse speed stage by combining four planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4 with the three clutches C 1 , C 2 , and C 3 and the three brakes B 1 , B 2 , and B 3 .

In addition, the planetary gear train according to various embodiments of the present invention improves silent driving because speed stages suitable to a rotational speed of the engine are achieved due to multiple-speed stages of the automatic transmission.

In addition, the planetary gear train according to various embodiments of the present invention maximizes driving efficiency of the engine 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.