Planetary gear train of automatic transmission for vehicle

This application claims priority to and the benefit of Korean Patent Application No. 10-2016-0027656, filed on Mar. 8, 2016, the entire contents of which are incorporated herein by reference.

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.

Recently, increase of oil price is triggering a hard competition in enhancing fuel consumption of a vehicle.

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

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.

Therefore, in order to enhance fuel consumption, an automatic transmission has more shift stages. It is important for better efficiency to be derived by a smaller number of parts.

In this respect, an eight-speed automatic transmission has been recently introduced, and a planetary gear train for an automatic transmission enabling more shift stages is under investigation.

The above information disclosed in this 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 in this country to a person of ordinary skill in the art.

The present disclosure provides a planetary gear train of an automatic transmission for a vehicle having advantages of obtaining shift-stages of at least the ten forward speeds and at least one reverse speed by reduced number of parts, improving power delivery performance and fuel consumption by multi-stages of an automatic transmission, and also improving installability by decreasing a length of the transmission, and providing benefit in weight.

A planetary gear train according to one form of the present disclosure 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; a first shaft connected with the first rotational element; a second shaft connected with the second rotational element and directly connected with the input shaft; a third shaft connecting the third rotational element and the seventh rotational element and selectively connected with the second shaft; a fourth shaft connected with the fourth rotational element, and selectively connected with the first shaft and the second shaft, respectively; a fifth shaft connected with the fifth rotational element, and selectively connected with the third shaft; a sixth shaft interconnecting the sixth rotational element and the eighth rotational element and directly connected with the output shaft; and a seventh shaft connected with the ninth rotational element, and selectively connected with the fifth shaft.

The first shaft and the seventh shaft may be respectively selectively connected with a transmission housing.

The first, second, and third rotational elements of the first planetary gear set 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 of the second planetary gear set 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 of the third planetary gear set may be respectively a third sun gear, a third planet carrier, and a third ring gear of the third planetary gear set.

A planetary gear train according to one form of the present disclosure may further include: a first clutch selectively connecting the second shaft and the third shaft; a second clutch selectively connecting the second shaft and the fourth shaft; a third clutch selectively connecting the first shaft and the fourth shaft; a fourth clutch selectively connecting the third shaft and the fifth shaft; a fifth clutch selectively connecting the fifth shaft and the seventh shaft; a first brake selectively connecting the first shaft and the transmission housing; and a second brake selectively connecting the seventh shaft and the transmission housing.

According to another form of the present disclosure, shift-stages of at least ten forward speeds and at least one reverse speed may be realized by combination of three planetary gear sets of simple planetary gear sets and seven control elements.

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

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

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

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; and

FIG. 2 is an operational chart for respective control elements at respective shift-stages in 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.

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.

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

Referring to FIG. 1 , a planetary gear train includes: first, second, and third planetary gear sets PG 1 , PG 2 , and PG 3 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, and third planetary gear sets PG 1 , PG 2 , and PG 3 , five clutches C 1 to C 5 and two brakes B 1 and B 2 as control elements, and a transmission housing H.

Torque input from the input shaft IS is shifted by cooperative operation of the first, second, and third planetary gear sets PG 1 , PG 2 , and PG 3 , and then output through the output shaft OS.

The planetary gear sets are arranged in the order of first, second, and third planetary gear sets PG 1 , PG 2 , and PG 3 , 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, and being arranged on a same axis with the input shaft IS, delivers a shifted driving torque to a drive shaft through a differential apparatus.

The first planetary gear set PG 1 is a single pinion planetary gear set, and includes a SS, a first planet carrier PC 1 that supports first pinion gear P 1 externally engaged with the first sun gear S 1 , and a first ring gear R 1 that is internally engaged with the first pinion gear P 1 . The first sun gear S 1 acts as a first 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 SS, a second planet carrier PC 2 that supports second pinion gear P 2 externally engaged with the second sun gear S 2 , and a second ring gear R 2 that is internally engaged with the second pinion gear P 2 . The second sun gear S 2 acts as a fourth 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 SS, a third planet carrier PC 3 that supports third pinion gear P 3 externally engaged with the third sun gear S 3 , and a third ring gear R 3 that is internally engaged with the third pinion gear P 3 . The third sun gear S 3 acts as a seventh rotational element N 7 , the third planet carrier PC 3 acts as a eighth rotational element N 8 , and the third ring gear R 3 acts as a ninth rotational element N 9 .

In the arrangement of the first, second, and third planetary gear sets PG 1 , PG 2 , and PG 3 , the third rotational element N 3 is directly connected with the seventh rotational element N 7 , the sixth rotational element N 6 is directly connected with the eighth rotational element N 8 , by seven shafts TM 1 to TM 7 .

The seven shafts TM 1 to TM 7 are arranged as follows.

Each of the seven shafts TM 1 to TM 7 may be a rotational member that always interconnects the input and output shafts and rotational elements of the planetary gear sets PG 1 , PG 2 , and PG 3 , 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 selectively connected with the transmission housing H, thereby selectively acting as a fixed element.

The second shaft TM 2 is connected with the second rotational element N 2 (first planet carrier PC 1 ), and directly connected with the input shaft IS, thereby always acting as an input element.

The third shaft TM 3 directly connects the third rotational element N 3 (the first ring gear R 1 ) and the seventh rotational element N 7 (the third sun gear S 3 ), and is selectively connected with the second shaft TM 2 .

The fourth shaft TM 4 is connected with the fourth rotational element N 4 (second sun gear S 2 ), and selectively connected with the first shaft TM 1 and the second shaft TM 2 , respectively.

The fifth shaft TM 5 is connected with the fifth rotational element N 5 (second planet carrier PC 2 ), and selectively connected with the third shaft TM 3 .

The sixth shaft TM 6 directly connects the sixth rotational element N 6 (the second ring gear R 2 ) and the eighth rotational element N 8 (the third planet carrier PC 3 ), and is directly connected with the output shaft OS, thereby always acting as an output element.

The seventh shaft TM 7 is connected with the ninth rotational element N 9 (third ring gear R 3 ), selectively connected with the fifth shaft TM 5 , and selectively connected with the transmission housing H, thereby selectively acting as a fixed element,

The seven shafts TM 1 to TM 7 , the input shaft IS, and the output shaft OS may be selectively interconnected with one another by control elements of five clutches C 1 , C 2 , C 3 , C 4 , and C 5 .

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

The five clutches C 1 to C 5 and the two brakes B 1 and B 2 are arranged as follows.

The first clutch C 1 is arranged between the second shaft TM 2 and the third shaft TM 3 , and selectively connects the second shaft TM 2 and the third shaft TM 3 , thereby controlling power delivery therebetween.

The second clutch C 2 is arranged between the second shaft TM 2 and the fourth shaft TM 4 , and selectively connects the second shaft TM 2 and the fourth shaft TM 4 , thereby controlling power delivery therebetween.

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

The fourth clutch C 4 is arranged between the third shaft TM 3 and the fifth shaft TM 5 , and selectively connects the third shaft TM 3 and the fifth shaft TM 5 , thereby controlling power delivery therebetween.

The fifth clutch C 5 is arranged between the fifth shaft TM 5 and the seventh shaft TM 7 , and selectively connects the fifth shaft TM 5 and the seventh shaft TM 7 , thereby controlling power delivery therebetween.

The first brake B 1 is arranged between the first shaft TM 1 and the transmission housing H, and selectively connects the first shaft TM 1 to the transmission housing H.

The 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 control elements of the first, second, third, fourth, and fifth clutches C 1 , C 2 , C 3 , C 4 , and C 5 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.

FIG. 2 is an operational chart for respective control elements at respective shift-stages in a planetary gear train according to one form of the present disclosure.

Referring to FIG. 2 , a planetary gear train according to the present disclosure realizes ten forward speeds and one reverse speed by operating three control elements among the first, second, third, fourth, and fifth clutches C 1 , C 2 , C 3 , C 4 , and C 5 and the first and second brakes B 1 and B 2 at respective shift-stages.

In the forward first speed shift-stage D 1 , the second and fourth clutches C 2 and C 4 and the second brakes B 2 are simultaneously operated.

The second shaft TM 2 and the fourth shaft TM 4 are interconnected by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the fifth shaft TM 5 by the operation of the fourth clutch C 4 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the seventh shaft TM 7 acts as a fixed element by the operation of the second brake B 2 , thereby realizing the forward first speed and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 .

In the forward second speed shift-stage D 2 , the third and fourth clutches C 3 and C 4 and the second brakes B 2 are simultaneously operated.

The first shaft TM 1 and the fourth shaft TM 4 are interconnected by the operation of the third clutch C 3 , and the third shaft TM 3 is interconnected with the fifth shaft TM 5 by the operation of the fourth clutch C 4 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the forward third speed shift-stage D 3 , the first and third clutches C 1 and C 3 and the second brakes B 2 are simultaneously operated.

The second shaft TM 2 and the third shaft TM 3 are interconnected by the operation of the first clutch C 1 , and the first shaft TM 1 is interconnected with the fourth shaft TM 4 by the operation of the third clutch C 3 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the forward fourth speed shift-stage D 4 , the third clutch C 3 and the first and second brakes B 1 and B 2 are simultaneously operated.

The first shaft TM 1 and the fourth shaft TM 4 are interconnected by the operation of the third clutch C 3 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the first shaft TM 1 and the seventh shaft TM 7 act as a fixed element by the operation of the first and second brakes B 1 and B 2 , thereby realizing the forward fourth speed and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 .

In the forward fifth speed shift-stage D 5 , the third and fifth clutches C 3 and C 5 and the second brakes B 2 are simultaneously operated.

The first shaft TM 1 and the fourth shaft TM 4 are interconnected by the operation of the third clutch C 3 , and the fifth shaft TM 5 is interconnected with the seventh shaft TM 7 by the operation of the fifth clutch C 5 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the forward sixth speed shift-stage D 6 , the second, third, and fifth clutches C 2 , C 3 , and C 5 are simultaneously operated.

The second shaft TM 2 and the fourth shaft TM 4 are interconnected by the operation of the second clutch C 2 , the first shaft TM 1 is interconnected with the fourth shaft TM 4 by the operation of the third clutch C 3 , and the fifth shaft TM 5 is interconnected with the seventh shaft TM 7 by the operation of the fifth clutch C 5 .

In this case, entire planetary gear sets integrally rotate, and a torque inputted through the second shaft TM 2 is outputted as inputted, thereby forming the forward sixth speed and outputting the inputted torque to the output shaft OS connected with the sixth shaft TM 6 .

In the forward seventh speed shift-stage D 7 , the second and fifth clutches C 2 and C 5 and the first brakes B 1 are simultaneously operated.

The second shaft TM 2 and the fourth shaft TM 4 are interconnected by the operation of the second clutch C 2 , and the fifth shaft TM 5 is interconnected with the seventh shaft TM 7 by the operation of the fifth clutch C 5 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the first shaft TM 1 acts as a fixed element by the operation of the first brake B 1 , thereby realizing the forward seventh speed and outputting a shifted torque through the output shaft OS connected with the sixth shaft TM 6 .

In the forward eighth speed shift-stage D 8 , the fourth and fifth clutches C 4 and C 5 and the first brakes B 1 are simultaneously operated.

The third shaft TM 3 and the fifth shaft TM 5 are interconnected by the operation of the fourth clutch C 4 , and the fifth shaft TM 5 is interconnected with the seventh shaft TM 7 by the operation of the fifth clutch C 5 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the first shaft TM 1 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the forward ninth speed shift-stage D 9 , the second and fourth clutches C 2 and C 4 and the first brakes B 1 are simultaneously operated.

The second shaft TM 2 and the fourth shaft TM 4 are interconnected by the operation of the second clutch C 2 , and the third shaft TM 3 is interconnected with the fifth shaft TM 5 by the operation of the fourth clutch C 4 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the first shaft TM 1 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the forward tenth speed shift-stage D 10 , the third and fourth clutches C 3 and C 4 and the first brakes B 1 are simultaneously operated.

The first shaft TM 1 and the fourth shaft TM 4 are interconnected by the operation of the third clutch C 3 , and the third shaft TM 3 is interconnected with the fifth shaft TM 5 by the operation of the fourth clutch C 4 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the first shaft TM 1 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 through the output shaft OS connected with the sixth shaft TM 6 .

In the reverse speed REV and the second and fifth clutches C 2 and C 5 and the second brakes B 2 are simultaneously operated.

The second shaft TM 2 and the fourth shaft TM 4 are interconnected by the operation of the second clutch C 2 , and the fifth shaft TM 5 is interconnected with the seventh shaft TM 7 by the operation of the fifth clutch C 5 . In this state, torque of the Input shaft IS is input to the second shaft TM 2 , and the seventh shaft TM 7 acts as a fixed element by the operation of the second brake B 2 , thereby realizing the reverse speed and outputting a reverse torque through the output shaft OS connected with the sixth shaft TM 6 .

As described above, a planetary gear train according to one form of the present disclosure may realize at least forward ten speeds and at least one reverse speed by operating three planetary gear sets PG 1 , PG 2 , and PG 3 by controlling the five clutches C 1 , C 2 , C 3 , C 4 , and C 5 and the two brake B 1 and B 2 .

In addition, a planetary gear train according to the present disclosure may realize shift stages appropriate for rotation speed of an engine due to multi-stages of an automatic transmission and improve driving stability of a vehicle by utilizing a low rotation speed of an engine.

In addition, the planetary gear train improves engine driving efficiency by multi-stages of an automatic transmission, and may improve power delivery performance and fuel consumption.

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 present disclosure.

B 1 , B 2 : first and second brakes

C 1 , C 2 , C 3 , C 4 , C 5 : first, second, third, fourth, and fifth clutches

PG 1 , PG 2 , PG 3 : first, second, and third planetary gear sets

S 1 , S 2 , S 3 : first, second, and third sun gears

PC 1 , PC 2 , PC 3 : first, second, and third planet carriers

R 1 , R 2 , R 3 : first, second, and third ring gears

IS: input shaft

OS: output shaft

TM 1 , TM 2 , TM 3 , TM 4 , TM 5 , TM 6 , TM 7 : first, second, third, fourth, fifth, sixth, and seventh shafts