Abstract:
A planetary gear train of an automatic transmission for a vehicle is provided. The planetary gear train includes an input shaft that receives an engine torque, an output shaft that outputs a shifted torque, and planetary gear sets. Additionally, shafts are connected with respective rotational elements. The planetary gear train thus improves power delivery performance and reduces fuel consumption by achieving nine forward speed stages using a minimum number of constituent elements.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application claims priority to and the benefit of Korean Patent Application No. 10-2016-0031665 filed in the Korean Intellectual Property Office on Mar. 16, 2016, the entire contents of which are incorporated herein by reference. 
     BACKGROUND 
     (a) Field of the Invention 
     The present invention relates to an automatic transmission for a vehicle, and more particularly, to a planetary gear train of an automatic transmission of a vehicle that improves power delivery performance and reduces fuel consumption by achieving nine forward speed stages using a minimum number of constituent elements. 
     (b) Description of the Related Art 
     Research regarding realizing more shift-stages of an automatic transmission is being conducted to achieve enhancement of fuel consumption and improved drivability, and recently, increase of oil price is triggering a competition in enhancing fuel consumption of a vehicle. In particular, research regarding an engine has been conducted to achieve weight reduction and to enhance fuel consumption by downsizing and research regarding an automatic transmission has been conducted to simultaneously provide improved drivability and fuel consumption by achieving more shift stages. 
     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, to maximally enhance fuel consumption of an automatic transmission having more shift stages, it is important for improved 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 being researched. 
     An automatic transmission of eight or more shift-stages typically includes three to four planetary gear sets and five to six control elements (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 has been contemplated. However, such an arrangement may not be widely applicable, and using dog clutches may deteriorate shift-feel. 
     The above information disclosed in this section is merely 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. 
     SUMMARY 
     The present invention provides a planetary gear train of an automatic transmission for a vehicle having advantages of obtaining shift-stages of at least nine forward speeds and at least one reverse speed by minimal number of parts, improving power delivery performance and fuel consumption by multi-stages of an automatic transmission, and improving driving stability of a vehicle by utilizing a low rotation speed of an engine. 
     A planetary gear train according to an exemplary embodiment of the present invention may include: an input shaft configured to receive an engine torque; an output shaft configured to output 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 fourth planetary gear set having tenth, eleventh, and twelfth rotational elements; a first shaft connected with the first rotational element; a second shaft interconnecting the second rotational element, the fourth rotational element, and seventh rotational element, and directly connected with the input shaft; a third shaft interconnecting the third rotational element and the eleventh rotational element; a fourth shaft interconnecting the fifth rotational element and the ninth rotational element, and selectively connected with the third shaft; a fifth shaft connected with the sixth rotational element; a sixth shaft connected with the eighth rotational element; a seventh shaft connected with the tenth rotational element, and selectively connected with the fourth shaft and the fifth shaft respectively; and an eighth shaft connected with the twelfth rotational element, selectively connected with the sixth shaft, and directly connected with the output shaft. 
     The first shaft and the third shaft may be selectively connected with a transmission housing respectively. The first, second, and third rotational element 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 element 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. The tenth, eleventh, and twelfth rotational elements of the fourth planetary gear set may be respectively a fourth sun gear, a fourth planet carrier, and a fourth ring gear of the fourth planetary gear set. 
     A planetary gear train according to an exemplary embodiment of the present invention may further include: a first clutch that selectively connects the sixth shaft and the eighth shaft; a second clutch that selectively connects the third shaft and the fourth shaft; a third clutch that selectively connects the fourth shaft and the seventh shaft; a fourth clutch that selectively connects the fifth shaft and the seventh shaft; a first brake that selectively connects the first shaft and the transmission housing; and a second brake that selectively connects the third shaft and the transmission housing. 
     According to an exemplary embodiment of the present invention, shift-stages of at least nine forward speeds and at least one reverse speed may be realized by a combination of four planetary gear sets of simple planetary gear sets and six control 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 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. Further, effects that may 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. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The above and other objects, features and advantages of the present disclosure will become more apparent to those of ordinary skill in the art by describing in detail exemplary embodiments thereof with reference to the accompanying drawings, in which: 
         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 in a planetary gear train according to an exemplary embodiment of the present invention. 
     
    
    
     DESCRIPTION OF SYMBOLS 
     
         
         
           
             B 1 , B 2  . . . first and second brakes 
             C 1 , C 2 , C 3 , C 4  . . . first, second, third, and fourth clutches 
             PG 1 , PG 2 , PG 3 , PG 4  . . . first, second, third, and fourth planetary gear sets 
             S 1 , S 2 , S 3 , S 4  . . . first, second, third, and fourth sun gears 
             PC 1 , PC 2 , PC 3 , PC 4  . . . first, second, third, and fourth planet carriers 
             R 1 , R 2 , R 3 , R 4  . . . first, second, third, and fourth ring gears 
             IS . . . input shaft 
             OS . . . output shaft 
             TM 1 , TM 2 , TM 3 , TM 4 , TM 5 , TM 6 , TM 7 , TM 8  . . . first, second, third, fourth, fifth, sixth, seventh, and eighth shafts 
           
         
       
    
     DETAILED DESCRIPTION 
     It is understood that the term “vehicle” or “vehicular” or other similar term 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, combustion, plug-in hybrid electric vehicles, hydrogen-powered vehicles and other alternative fuel vehicles (e.g. fuels derived from resources other than petroleum). 
     The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the singular forms “a”, “an” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms “comprises” and/or “comprising,” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items. 
     Although exemplary embodiment is described as using a plurality of units to perform the exemplary process, it is understood that the exemplary processes may also be performed by one or plurality of modules. Additionally, it is understood that the term controller refers to a hardware device that includes a memory and a processor. The memory is configured to store the modules and the processor is specifically configured to execute said modules to perform one or more processes which are described further below. 
     Unless specifically stated or obvious from context, as used herein, the term “about” is understood as within a range of normal tolerance in the art, for example within 2 standard deviations of the mean. “About” can be understood as within 10%, 9%, 8%, 7%, 6%, 5%, 4%, 3%, 2%, 1%, 0.5%, 0.1%, 0.05%, or 0.01% of the stated value. Unless otherwise clear from the context, all numerical values provided herein are modified by the term “about.” 
     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 may include first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , arranged on a same axis, an input shaft IS, an output shaft OS, eight shafts TM 1  to TM 8  interconnecting rotational elements of the first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , four clutches C 1  to C 4  and two brakes B 1  and B 2  as control elements, and a transmission housing H. 
     In particular, torque input from the input shaft IS may be 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 may be 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 may be input into the input shaft IS, after being torque-converted by a torque converter. The output shaft OS is an output member, may be disposed on a same axis with the input shaft IS, and may be configured to deliver a shifted driving torque to a drive shaft using a differential apparatus. 
     The first planetary gear set PG 1  is a single pinion planetary gear set, and may include 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  internally engaged with the first pinion gear P 1 . The first sun gear S 1  may operate as a first rotational element N 1 , the first planet carrier PC 1  may operate as a second rotational element N 2 , and the first ring gear R 1  may operate as a third rotational element N 3 . The second planetary gear set PG 2  is a single pinion planetary gear set, and may include 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  internally engaged with the second pinion gear P 2 . The second sun gear S 2  may operate as a fourth rotational element N 4 , the second planet carrier PC 2  may operate as a fifth rotational element N 4 , and the second ring gear R 2  may operate as a sixth rotational element N 6 . 
     Additionally, the third planetary gear set PG 3  is a single pinion planetary gear set, and may include 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  internally engaged with the third pinion gear P 3 . The third sun gear S 3  may operate as a seventh rotational element N 7 , the third planet carrier PC 3  may operate as an eighth rotational element N 8 , and the third ring gear R 3  may operate as a ninth rotational element N 9 . The fourth planetary gear set PG 4  is a single pinion planetary gear set, and may include a fourth planet carrier PC 4  that supports fourth pinion gear P 4  externally engaged with the fourth sun gear S 4 , and a fourth ring gear R 4  internally engaged with the fourth pinion gear P 4 . The fourth sun gear S 4  may operate as a tenth rotational element N 10 , the fourth planet carrier PC 4  may operate as a eleventh rotational element N 11 , and the fourth ring gear R 4  may operate as a twelfth rotational element N 12 . 
     In the first, second, third, and fourth planetary gear set PG 1 , PG 2 , PG 3 , and PG 4 , the second rotational element N 2  may be directly connected with the fourth rotational element N 4  and the seventh rotational element N 7 , the third rotational element N 3  may be directly connected with the eleventh rotational element N 11 , and the fifth rotational element N 5  may be directly connected with the ninth rotational element N 9 , by eight shafts TM 1  to TM 8 . The eight shafts TM 1  to TM 8  are hereinafter described in detail. Each of the eight shafts TM 1  to TM 8  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 , and PG 4 , or may be a fixed member fixed to the transmission housing H. 
     In particular, the first shaft TM 1  may be connected with the first rotational element N 1  (the first sun gear S 1 ), and selectively connected with the transmission housing H, to selectively operate as a fixed element. The second shaft TM 2  may directly connect the second rotational element N 2  (the first planet carrier PC 1 ), the fourth rotational element N 4 , and the seventh rotational element N 7  (the third sun gear S 3 ), and may be directly connected with the input shaft IS to operate as an input element. 
     The third shaft TM 3  may directly connect the third rotational element N 3  (the first ring gear R 1 ) and the eleventh rotational element N 11  (the fourth planet carrier PC 4 ), and selectively connected with the transmission housing H, to selectively operate as a fixed element. The fourth shaft TM 4  may directly connect the fifth rotational element N 5  (the second planet carrier PC 2 ) and the ninth rotational element N 9  (the third ring gear R 3 ), and may be selectively connected with the third shaft TM 3 . The fifth shaft TM 5  may be connected with the sixth rotational element N 6  (the second ring gear R 3 ). 
     Additionally, the sixth shaft TM 6  may be connected with the eighth rotational element N 8  (the third planet carrier PC 3 ). The seventh shaft TM 7  may be connected the tenth rotational element N 10  (the fourth sun gear S 4 ), and may be selectively connected with the fourth shaft TM 4  and fifth shaft TM 5  respectively. The eighth shaft TM 8  may be connected with the twelfth rotational element N 12  (the fourth ring gear R 4 ), may be selectively connected with the sixth TM 6 , and may be directly connected with the output shaft OS to operate as an output element. The eight shafts TM 1  to TM 8 , the input shaft IS, and the output shaft OS may be selectively interconnected with one another by control elements of four clutches C 1 , C 2 , C 3 , and C 4 . The various control elements may be operated by a single integrated controller. 
     The eight shafts TM 1  to TM 8  may be selectively connected with the transmission housing H, by control elements of two brakes B 1  and B 2 . The four clutches C 1  to C 4  and the two brakes B 1  and B 2  are arranged as described herein below. 
     The first clutch C 1  may be disposed between the sixth shaft TM 6  and the eighth shaft TM 8  and may selectively connect the sixth shaft TM 6  and the eighth shaft TM 8  connected with the output shaft OS to adjust power delivery therebetween. The second clutch C 2  may be disposed between the third shaft TM 3  and the fourth shaft TM 4 , and may selectively connect the third shaft TM 3  and the fourth shaft TM 4 , to adjust power delivery therebetween. The third clutch C 3  may be disposed between the fourth shaft TM 4  and the seventh shaft TM 7 , and may selectively connect the fourth shaft TM 4  and the seventh shaft TM 7 , to adjust power delivery therebetween. The fourth clutch C 4  may be disposed between the fifth shaft TM 5  and the seventh shaft TM 7 , and may selectively connect the fifth shaft TM 5  and the seventh shaft TM 7 , to adjust power delivery therebetween. 
     The first brake B 1  may be disposed between the first shaft TM 1  and the transmission housing H, and may selectively connect the first shaft TM 1  to the transmission housing H. The second brake B 2  may be disposed between the third shaft TM 3  and the transmission housing H, and may selectively connect the third shaft TM 3  to the transmission housing H. The respective control 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 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 an exemplary embodiment of the present invention. Referring to  FIG. 2 , a planetary gear train according to an exemplary embodiment of the present invention may realize nine forward speeds and one reverse speed by operating three control elements among 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  at respective shift-stages. 
     In the forward first speed shift-stage D 1 , the first brake B 1  and the first and third clutches C 1  and C 3  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 . Particularly, the torque of the input shaft IS may be input to the second shaft TM 2 . In addition, the third shaft TM 3  may operate as a fixed element by the operation of the second brake B 2 , thereby realizing the forward first speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward second speed shift-stage D 2 , the second brake B 2  and the first and second clutches C 1  and C 2  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the third shaft TM 3  is connected with the fourth shaft TM 4  by the operation of the second clutch C 2 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the third shaft TM 3  may operate as a fixed element by the operation of the second brake B 2 , thereby realizing the forward second speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward third speed shift-stage D 3 , the second brake B 2  and the first and fourth clutches C 1  and C 4  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the fifth shaft TM 5  may be connected with the seventh shaft TM 7  by the operation of the fourth clutch C 4 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the third shaft TM 3  may operate as a fixed element by the operation of the second brake B 2 , thereby realizing the forward third speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward fourth speed shift-stage D 4 , the first, third, and fourth clutch C 1 , C 3 , and C 4  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 , and the fifth shaft TM 5  may be connected with the seventh shaft TM 7  by the operation of the fourth clutch C 4 . Particularly, the torque of the input shaft IS may be input to the second shaft TM 2 . The second, third, and fourth planetary gear sets PG 2 , PG 3 , and PG 4  may be configured to rotate integrally, and a torque may be output as input, thereby forming the forward fourth speed and may be configured to thus output the inputted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward fifth speed shift-stage D 5 , the first brake B 1  and the first and fourth clutches C 1  and C 4  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the fifth shaft TM 5  may be connected with the seventh shaft TM 7  by the operation of the fourth clutch C 4 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the first shaft TM 1  may operate as a fixed element by the operation of the first brake B 1 , thereby realizing the forward fifth speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward sixth speed shift-stage D 6 , the first brake B 1  and the first and second clutches C 1  and C 2  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the third shaft TM 3  may be connected with the fourth shaft TM 4  by the operation of the fourth clutch C 2 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the first shaft TM 1  may operate as a fixed element by the operation of the first brake B 1 , thereby realizing the forward sixth speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward seventh speed shift-stage D 7 , the first brake B 1  and the first and third clutches C 1  and C 3  may be operated simultaneously. As a result, the sixth shaft TM 6  may be connected with the eighth shaft TM 8  by the operation of the first clutch C 1 , and the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the first shaft TM 1  may operate as a fixed element by the operation of the first brake B 1 , thereby realizing the forward seventh speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward eighth speed shift-stage D 8 , the first brake B 1  and the second and third clutches C 2  and C 3  may be operated simultaneously. As a result, the third shaft TM 3  may be connected with the fourth shaft TM 4  by the operation of the second clutch C 2 , and the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the first shaft TM 1  may operate as a fixed element by the operation of the first brake B 1 , thereby realizing the forward eighth speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the forward ninth speed shift-stage D 9 , the first brake B 1  and the third and fourth clutches C 3  and C 4  may be operated simultaneously. As a result, the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 , and the fifth shaft TM 5  may be connected with the seventh shaft TM 7  by the operation of the fourth clutch C 4 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the first shaft TM 1  may operate as a fixed element by the operation of the first brake B 1 , thereby realizing the forward ninth speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     In the reverse speed REV, the second brake B 2  and the third and fourth clutches C 3  and C 4  may be operated simultaneously. As a result, the fourth shaft TM 4  may be connected with the seventh shaft TM 7  by the operation of the third clutch C 3 , and the fifth shaft TM 5  may be connected with the seventh shaft TM 7  by the operation of the fourth clutch C 4 . Particularly, the torque of the input IS may be input to the second shaft TM 2 . In addition, the third shaft TM 3  may operate as a fixed element by the operation of the second brake B 2 , thereby realizing the reverse speed by cooperative operation of respective shafts and may be configured to thus output a shifted torque to the output shaft OS connected with the eighth shaft TM 8 . 
     As described above, a planetary gear train according to an exemplary embodiment of the present invention may realize at least nine forward speeds and at least one reverse speed by operating four planetary gear sets PG 1 , PG 2 , PG 3 , and PG 4  by operating 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 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. 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 exemplary embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.