US20060052208A1 - Six-speed powertrain of an automatic transmission - Google Patents

Six-speed powertrain of an automatic transmission Download PDF

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Publication number
US20060052208A1
US20060052208A1 US11/028,136 US2813604A US2006052208A1 US 20060052208 A1 US20060052208 A1 US 20060052208A1 US 2813604 A US2813604 A US 2813604A US 2006052208 A1 US2006052208 A1 US 2006052208A1
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Prior art keywords
planetary gearset
clutch
input shaft
powertrain
planetary
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Abandoned
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US11/028,136
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English (en)
Inventor
Jong Sool Park
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Hyundai Motor Co
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Hyundai Motor Co
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Assigned to HYUNDAI MOTOR COMPANY reassignment HYUNDAI MOTOR COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PARK, JONG SOOL
Assigned to HYUNDAI MOTOR COMPANY reassignment HYUNDAI MOTOR COMPANY CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE'S ADDRESS IN INCORRECT AND ASSIGNOR'S DATE OF SIGNATURE IS INCORRECT ON TRANSMITTAL. PREVIOUSLY RECORDED ON REEL 016506 FRAME 0374. ASSIGNOR(S) HEREBY CONFIRMS THE HYUNDAI MOTOR COMPANY, 231 YANGJAE-DONG, SEOCHO-KU, SEOUL, REPUBLIC OF KOREA. DATE OF SIGNATURE OF ASSIGNMENT IS APRIL 6, 2005. Assignors: PARK, JONG SOOL
Publication of US20060052208A1 publication Critical patent/US20060052208A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the present invention relates to an automatic transmission. More particularly, the present invention relates to a powertrain of an automatic transmission that realizes multiple shift speeds with a combination of a plurality of planetary gearsets.
  • a typical shift mechanism of an automatic transmission utilizes a combination of a plurality of planetary gearsets.
  • a powertrain of such an automatic transmission that includes the plurality of planetary gearsets changes rotation speed and torque received from a torque converter of the automatic transmission, and accordingly changes and transmits the changed torque to an output shaft.
  • These six-speed powertrains may include multiple friction elements, clutches and brakes. However, the more friction elements used the heavier and larger the automatic transmission.
  • the present invention has been made in an effort to provide a six-speed powertrain having stability and durability by having a small number of frictional elements.
  • An exemplary six-speed powertrain of an automatic transmission includes: a first planetary gearset having operational elements of a first sun gear, a first ring gear, and a first carrier; a second planetary gearset having operational elements of a second sun gear, a second ring gear, and a second carrier; a third planetary gearset having operational elements of a third sun gear, a third ring gear, and a third carrier; a fourth planetary gearset having operational elements of a fourth sun gear, a fourth ring gear, and a fourth carrier; an input shaft; an output gear; and a transmission case.
  • the first ring gear is fixedly connected to the third carrier and the fourth ring gear.
  • the first carrier is fixedly connected to the fourth carrier.
  • the first sun gear is fixedly connected to the second sun gear.
  • the second ring gear is always stationary by being fixedly connected to the transmission case.
  • the third sun gear always acts as an input element by being fixedly connected to the input shaft.
  • the third carrier always acts as an output element by being fixedly connected to the output gear.
  • the fourth sun gear is variably connected to the input shaft via a first clutch. At least one of the fixedly connected first and fourth carriers is variably connected to the input shaft via a second clutch.
  • the second carrier is variably connected to the third ring gear via a third clutch.
  • At least one of the fixedly connected first and fourth carriers is variably connected to the transmission case via a first brake and is subject to a stopping operation of the first brake.
  • the second carrier is variably connected to the transmission case via a second brake and is subject to a stopping operation of the second brake.
  • first, second, third, and fourth planetary gearsets are disposed in a sequence of the second planetary gearset, the first planetary gearset, the fourth planetary gearset, and the third planetary gearset.
  • first operational element of the first planetary gearset is integrally formed with the tenth operational element of the fourth planetary gearset
  • the second operational element of the first planetary gearset is integrally formed with the eleventh operational element of the fourth planetary gearset, such that the first and fourth planetary gearsets form a compound planetary gearset.
  • arrangement of the input shaft, the output gear, and the first to third clutches may be variously changed.
  • the input shaft is disposed in a same direction of the output gear with respect to the third planetary gearset, one of the first and second clutches is disposed toward the input shaft with respect to the third planetary gearset, and another one of the first and second clutches is disposed opposite of the input shaft with respect to the second planetary gearset.
  • the first clutch may be disposed toward the input shaft with respect to the third planetary gearset, and the second clutch may be disposed opposite of the input shaft with respect to the second planetary gearset.
  • the input shaft is disposed in a same direction of the output gear with respect to the third planetary gearset, and both of the first and second clutches are disposed toward the input shaft with respect to the third planetary gearset.
  • first and second clutches may be disposed in a sequence of the first clutch and the second clutch, in a direction from the third planetary gearset to the input shaft.
  • the first and second clutches may be disposed in a sequence of the second clutch and the first clutch, in a direction from the third planetary gearset to the input shaft.
  • the input shaft is disposed opposite of the output gear with respect to the second planetary gearset, and both of the first and second clutches are disposed toward the input shaft with respect to the second planetary gearset.
  • first and second clutches may be disposed in a sequence of the first clutch and the second clutch, in a direction from the second planetary gearset to the input shaft.
  • a one way clutch disposed in parallel with the first brake may be further included in such an exemplary six-speed powertrain of an automatic transmission.
  • the first and second brakes may be realized as wet-type multi-plate brakes or band brakes.
  • another exemplary six-speed powertrain of an automatic transmission includes: a first planetary gearset having first, second, and third operational elements that occupy sequential positions in a lever diagram; a second planetary gearset having fourth, fifth, and sixth operational elements that occupy sequential positions in a lever diagram; a third planetary gearset having seventh, eighth, and ninth operational elements that occupies sequential positions in a lever diagram; a fourth planetary gearset having tenth, eleventh, and twelfth operational elements that occupy sequential positions in a lever diagram; an input shaft; an output shaft; and a transmission case.
  • the first operational element is fixedly connected to the eighth operational element and the tenth operational element.
  • the second operational element is fixedly connected to the eleventh operational element.
  • the third operational element is fixedly connected to the sixth operational element.
  • the fourth operational element is always stationary by being fixedly connected to the transmission case.
  • the seventh operational element always acts as an input element by being fixedly connected to the input shaft.
  • the eighth operational element always acts as an output element by being fixedly connected to the output gear.
  • the twelfth operational element is variably connected to the input shaft via a first clutch.
  • At least one of the fixedly connected second and eleventh operational elements is variably connected to the input shaft via a second clutch.
  • the fifth operational element is variably connected to the ninth operational element via a third clutch.
  • At least one of the fixedly connected second and eleventh operational elements is variably connected to the transmission case via a first brake and is subject to a stopping operation of the first brake.
  • the fifth operational element is variably connected to the transmission case via a second brake and is subject to a stopping operation of the second brake.
  • first, second, third, and fourth planetary gearsets are disposed in a sequence of the second planetary gearset, the first planetary gearset, the fourth planetary gearset, and the third planetary gearset.
  • first operational element of the first planetary gearset is integrally formed with the tenth operational element of the fourth planetary gearset
  • the second operational element of the first planetary gearset is integrally formed with the eleventh operational element of the fourth planetary gearset, such that the first and fourth planetary gearsets form a compound planetary gearset.
  • arrangement of the input shaft, the output gear, and the first to third clutches may be variously changed.
  • the input shaft is disposed in a same direction of the output gear with respect to the third planetary gearset, one of the first and second clutches is disposed toward the input shaft with respect to the third planetary gearset, and another of the first and second clutches is disposed opposite of the input shaft with respect to the second planetary gearset.
  • the first clutch may be disposed toward the input shaft with respect to the third planetary gearset, and the second clutch may be disposed opposite of the input shaft with respect to the second planetary gearset.
  • the input shaft is disposed in a same direction of the output gear with respect to the third planetary gearset, and both of the first and second clutches are disposed toward the input shaft with respect to the third planetary gearset.
  • the first and second clutches may be disposed in a sequence of the first clutch and the second clutch, in a direction from the third planetary gearset to the input shaft.
  • the first and second clutches may be disposed in a sequence of the second clutch and the first clutch, in a direction from the third planetary gearset to the input shaft.
  • the input shaft is disposed opposite of the output gear with respect to the second planetary gearset, and both of the first and second clutches are disposed toward the input shaft with respect to the second planetary gearset.
  • the first and second clutches may be disposed in a sequence of the first clutch and the second clutch, in a direction from the second planetary gearset to the input shaft.
  • a one way clutch disposed in parallel with the first brake may be further included in such an exemplary six-speed powertrain of an automatic transmission.
  • the first and second brakes may be realized as wet-type multi-plate brakes or band brakes.
  • FIG. 1 illustrates a six-speed powertrain of an automatic transmission, according to a first embodiment of the present invention
  • FIG. 2 illustrates a six-speed powertrain of an automatic transmission, according to a second embodiment of the present invention
  • FIG. 3 illustrates a six-speed powertrain of an automatic transmission, according to a third embodiment of the present invention
  • FIG. 4 illustrates a six-speed powertrain of an automatic transmission, according to a fourth embodiment of the present invention
  • FIG. 5 is an operational chart for a six-speed powertrain of an automatic transmission, according to embodiments of the present invention.
  • FIG. 6 is a lever diagram illustrating operational nodes (N 1 through N 6 ) of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention, in the case that the first planetary gearset PG 1 and the fourth planetary gearset PG 4 have equal ring gear/sun gear tooth ratios;
  • FIG. 7 illustrates a speed diagram for a first forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention
  • FIG. 8 illustrates a speed diagram for a second forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention
  • FIG. 9 illustrates a speed diagram for a third forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention.
  • FIG. 10 illustrates a speed diagram for a fourth forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention
  • FIG. 11 illustrates a speed diagram for a fifth forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention
  • FIG. 12 illustrates a speed diagram for a sixth forward speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention
  • FIG. 13 illustrates a speed diagram for a reverse speed of a six-speed powertrain of an automatic transmission, according to embodiments of the present invention.
  • FIGS. 14A-14F are charts showing operational states obtained when a six-speed powertrain of an automatic transmission, according to embodiments of the present invention operate with specific gear ratios.
  • a six-speed powertrain of an automatic transmission includes four planetary gearsets of first, second, third, and fourth planetary gearsets PG 1 , PG 2 , PG 3 , and PG 3 .
  • the first planetary gearset PG 1 is a single pinion planetary gearset, and includes a first sun gear S 1 , a first carrier PC 1 , and a first ring gear R 1 as operational elements thereof.
  • a first pinion gear P 1 being engaged with both the first ring gear R 1 and the first sun gear S 1 , is connected to and carried by the first carrier PC 1 .
  • the second planetary gearset PG 2 is a single pinion planetary gearset, and includes a second sun gear S 2 , a second carrier PC 2 , and a second ring gear R 2 as operational elements thereof.
  • a second pinion gear P 2 being engaged with both the second ring gear R 2 and the second sun gear S 2 , is connected to and carried by the second carrier PC 2 .
  • the third planetary gearset PG 3 is a single pinion planetary gearset, and includes a third sun gear S 3 , a third carrier PC 3 , and a third ring gear R 3 as operational elements thereof.
  • a third pinion gear P 3 being engaged with both the third ring gear R 3 and the third sun gear S 3 , is connected to and carried by the third carrier PC 3 .
  • the fourth planetary gearset PG 4 is a single pinion planetary gearset, and includes a fourth sun gear S 4 , a fourth carrier PC 4 , and a fourth ring gear R 4 as operational elements thereof.
  • a fourth pinion gear P 4 being engaged with both the fourth ring gear R 4 and the fourth sun gear S 4 , is connected to and carried by the fourth carrier PC 4 .
  • a six-speed powertrain of an automatic transmission further includes an input shaft 100 for receiving torque from an engine (not shown), an output gear 200 for outputting torque from the powertrain, and a transmission case 300 .
  • the first ring gear R 1 is fixedly connected to the third carrier PC 3 , and is also fixedly connected to the fourth ring gear R 4 .
  • the first carrier PC 1 is fixedly connected to the fourth carrier PC 4 .
  • the first sun gear S 1 is fixedly connected to the second sun gear S 2 .
  • the second ring gear R 2 is always stationary by being fixedly connected to the transmission case 300 .
  • the third sun gear S 3 always acts as an input element by being fixedly connected to the input shaft 100 .
  • the third carrier PC 3 always acts as an output element by being fixedly connected to the output gear 200 .
  • the fourth sun gear S 4 is variably connected to the input shaft 100 via a first clutch C 1 .
  • At least one of the fixedly connected first and fourth carriers PC 1 and PC 4 is variably connected to the input shaft 100 via a second clutch C 2 .
  • the second carrier PC 2 is variably connected to the third ring gear R 3 via a third clutch C 3 .
  • At least one of the fixedly connected first and fourth carriers PC 1 and PC 4 is variably connected to the transmission case 300 via a first brake B 1 and is subject to a stopping operation of the first brake B 1 .
  • the second carrier PC 2 is variably connected to the transmission case 300 via a second brake B 2 and is subject to a stopping operation of the second brake B 2 .
  • the first, second, third, and fourth planetary gearsets PG 1 , PG 2 , PG 3 , and PG 4 are disposed in a sequence of the second planetary gearset PG 2 , the first planetary gearset PG 1 , the fourth planetary gearset PG 4 , and the third planetary gearset PG 3 .
  • the first ring gear R 1 of the first planetary gearset PG 1 is integrally formed with the fourth ring gear R 4 of the fourth planetary gearset PG 4 . That is, one common ring gear CR commonly acts as a ring gear for the first and fourth planetary gearsets PG 1 and PG 4 .
  • first carrier PC 1 of the first planetary gearset PG 1 is integrally formed with the fourth carrier PC 4 of the fourth planetary gearset PG 4 . That is, one common pinion carrier CPC commonly acts as a carrier for the first and fourth planetary gearsets PG 1 and PG 4 . That is, first pinion gear P 1 of the first planetary gearset PG 1 and the fourth pinion gear P 4 of the fourth planetary gearset PG 4 are interconnected by one common pinion carrier CPC, and they are under the same operation. Therefore, the first planetary gearset PG 1 and the fourth planetary gearset PG 4 form a compound planetary gearset CPG.
  • the first planetary gearset PG 1 and the fourth planetary gearset PG 4 are supposed to have the same ring gear/sun gear tooth ratio.
  • a supposition better describes the understanding of the spirit of the present invention, and it should not be understood that the scope of the present invention is limited thereto.
  • the first planetary gearset PG 1 may have a different ring gear/sun gear tooth ratio from the fourth planetary gearset PG 4 , and consequences of such a difference will be obvious to a person of ordinary skill in the art from the following description.
  • the input shaft 100 is disposed in a same direction of the output gear 200 with respect to the third planetary gearset PG 3 .
  • first and second clutches C 1 and C 2 are disposed toward the input shaft 100 with respect to the third planetary gearset PG 3 .
  • another one of the first and second clutches C 1 and C 2 is disposed opposite of the input shaft 100 with respect to the second planetary gearset PG 2 .
  • the first clutch C 1 is disposed toward the input shaft 100 with respect to the third planetary gearset PG 3
  • the second clutch C 2 is disposed opposite of the input shaft 100 with respect to the second planetary gearset PG 2 .
  • the input shaft 100 is disposed in a same direction of the output gear 200 with respect to the third planetary gearset PG 3 , and both of the first and second clutches C 1 and C 2 are disposed toward the input shaft 100 with respect to the third planetary gearset PG 3 .
  • the first and second clutches C 1 and C 2 are disposed in a sequence of the first clutch C 1 and the second clutch C 2 , in a direction from the third planetary gearset PG 3 to the input shaft, 100 .
  • the first and second clutches C 1 and C 2 are disposed in a sequence of the second clutch C 2 and the first clutch C 1 , in a direction from the third planetary gearset PG 3 to the input shaft 100 .
  • the input shaft 100 is disposed opposite of the output gear 200 with respect to the second planetary gearset PG 2 , and both of the first and second clutches C 1 and C 2 are disposed toward the input shaft 100 with respect to the second planetary gearset PG 2 .
  • the first and second clutches C 1 and C 2 are disposed in a sequence of the first clutch C 1 and the second clutch C 2 , in a direction from the second planetary gearset PG 2 to the input shaft 100 .
  • a six-speed powertrain of any of the first through fourth embodiment of the present invention further includes a one way clutch OWC disposed in parallel with the first brake B 1 . Due to such a one way clutch OWC, a first forward speed can be realized by operation of the third clutch C 3 without operation of the first brake B 1 .
  • each of the first and second brakes B 1 and B 2 may by realized by a wet-type multi-plate brake or a band brake.
  • a six-speed powertrain of an automatic transmission operates: the third clutch C 3 and the first brake B 1 at a first forward speed D 1 ; the third clutch C 3 and the second brake B 2 at a second forward speed D 2 ; the third clutch C 3 and the first clutch C 1 at a third forward speed D 3 ; the third clutch C 3 and the second clutch C 2 at a fourth forward speed D 4 ; the first clutch C 1 and the second clutch C 2 at a fifth forward speed D 5 ; and the second clutch C 2 and the second brake B 2 at a sixth forward speed D 6 .
  • the first clutch C 1 and the first brake B 1 are operated at a reverse speed R.
  • FIG. 6 is a lever diagram illustrating operational nodes (N 1 through N 6 ) of a six-speed powertrain of an automatic transmission according to embodiments of the present invention, in the case that the first planetary gearset PG 1 and the fourth planetary gearset PG 4 have equal ring gear/sun gear tooth ratios.
  • operational elements of the fourth planetary gearset PG 4 show rotational characteristics equal to operational elements of the first planetary gearset PG 1 . Therefore, they may be represented by operational elements of the first planetary gearset PG 1 and be disregarded hereinafter.
  • the first ring gear R 1 , the first carrier PC 1 , and the first sun gear S 1 of the first planetary gearset PG 1 are sequentially located at operational nodes N 2 , N 4 , and N 6 in the lever diagram.
  • the second ring gear R 2 , the second carrier PC 2 , and the second sun gear S 2 of the second planetary gearset PG 2 are sequentially located at operational nodes N 3 , N 5 , and N 6 in the lever diagram.
  • the third sun gear S 3 , the third carrier PC 3 , and the third ring gear R 3 of the third planetary gearset PG 3 are sequentially located at operational nodes N 1 , N 2 , and N 5 in the lever diagram.
  • the fourth ring gear R 4 , the fourth carrier PC 4 , and the fourth sun gear S 4 of the fourth planetary gearset PG 4 are sequentially located at operational nodes N 2 , N 4 , and N 6 in the lever diagram.
  • the input shaft 100 is variably connected to the fourth sun gear S 4 and the first carrier PC 1 (or equivalently, the fourth carrier PC 4 ) via the first and second clutches C 1 and C 2 , respectively. Therefore, engine rotation input through the input shaft 100 is delivered to the sixth node N 6 or the fourth node N 4 according to an operation of the first and second clutches C 1 and C 2 , respectively.
  • the first carrier PC 1 (or equivalently, the fourth carrier PC 4 ) is variably connected to the transmission case 300 via the first brake B 1 and the one way clutch OWC disposed in parallel. Therefore, the fourth node N 4 of the first carrier PC 1 and the fourth carrier PC 4 may be stopped by an operation of the first brake B 1 and/or the one way clutch OWC.
  • the second carrier PC 2 is variably connected to the transmission case 300 via the second brake B 2 . Therefore, the fifth node N 5 may be stopped by an operation of the second brake B 2 .
  • L 1 denotes a speed line for the first planetary gearset PG 1
  • L 2 denotes a speed line for the second planetary gearset PG 2
  • L 3 denotes a speed line for the third planetary gearset PG 3 .
  • the speed line L 1 of the first planetary gearset PG 1 and the speed line L 2 of the second planetary gearset PG 2 meet at the sixth node N 6 , since the first sun gear S 1 and the second sun gear S 2 are fixedly interconnected.
  • the speed line L 1 of the first planetary gearset PG 1 and the speed line L 3 of the third planetary gearset PG 3 meet at the second node N 2 since the first ring gear R 1 and the third carrier PC 3 are fixedly interconnected.
  • the third node N 3 is always stationary since the second ring gear R 2 is fixedly connected to the transmission case 300 .
  • the third sun gear S 3 always rotates at an input speed since it is fixedly connected to the input shaft.
  • Arrangement of the speed lines L 1 , L 2 , and L 3 of the first, second, and third planetary gearsets PG 1 , PG 2 , and PG 3 are determined by selective operation of the first, second, and third clutches C 1 , C 2 , and C 3 and the first and second brakes B 1 and B 2 under such a condition.
  • the third ring gear R 3 and the second carrier PC 2 on the fifth node N 5 rotate at a synchronized speed since the third clutch C 3 operates.
  • the fourth node N 4 is stationary since the first brake B 1 operates.
  • the speed lines L 1 , L 2 , and L 3 are formed as shown in FIG. 7 . That is, regarding the third, fifth, and sixth nodes N 3 , N 5 , and N 6 of the second planetary gearset PG 2 , the third node N 3 is stationary, and the fifth and sixth nodes N 5 and N 6 rotate at a negative speed, i.e., in reverse.
  • the speed line L 1 is a line connecting the sixth node N 6 that is rotating in reverse and the fourth node N 4 that is stationary. Therefore, the speed line L 3 of the third planetary gearset PG 3 is formed to be declining rightward as shown in FIG. 7 . In this case, an output element of the third carrier PC 3 rotates at a very low speed relative to a rotation of the input shaft 100 .
  • the sixth node N 6 also rotates at the same speed as the input shaft 100 since the first clutch C 1 operates. Therefore in this case, the speed line L 2 of the second planetary gearset PG 2 is formed by the third node N 3 that is stationary and the sixth node N 6 rotating at the input speed.
  • the drive line L 3 of the third planetary gearset PG 3 is determined by the fifth node N 5 on the speed line L 2 of the second planetary gearset PG 2 . Therefore, the speed line L 3 of the third planetary gearset PG 3 becomes slightly rotated counterclockwise, in comparison with the second forward speed. Therefore, the third carrier PC 3 that is an output element rotates at an increased speed in comparison with the second forward speed. At such a third forward speed, the second and third planetary gearsets PG 2 and PG 3 take part in the power transmission.
  • the third ring gear R 3 and the second carrier PC 2 on the fifth node N 5 remain rotating at a synchronized speed since the third clutch C 3 also operates in the fourth forward speed.
  • the fourth node N 4 also rotates at the same speed as the input shaft 100 since the second clutch C 2 operates. Therefore in this case, the speed lines L 1 , L 2 , and L 3 are formed as shown in FIG. 10 . That is, the speed line L 2 of the second planetary gearset PG 2 becomes slightly rotated counterclockwise, in comparison with the third forward speed.
  • the speed line L 3 of the third planetary gearset PG 3 becomes slightly rotated counterclockwise, in comparison with the third forward speed. Therefore, the third carrier PC 3 that is an output element rotates at an increased speed in comparison with the third forward speed. At such a fourth forward speed, all the first, second, and third planetary gearsets PG 1 , PG 2 , and PG 3 take part in the power transmission.
  • the first and second clutches C 1 and C 2 operate. Therefore, as shown in FIG. 11 , the fourth and sixth nodes N 4 and N 6 rotate at the same speed as the input shaft 100 . Therefore, the speed line L 1 of the first planetary gearset PG 1 becomes horizontal at a height of rotation speed of the input shaft 100 . This implies that the first planetary gearset rotates as a whole. Therefore, the second node N 2 also rotates at the input speed, and accordingly, the input speed is directly output without changing. At such a fifth forward speed, none of the first, second, and third planetary gearsets PG 1 , PG 2 , and PG 3 takes part in the power transmission.
  • the fourth node N 4 rotates at the same speed as the input shaft 100 since the second clutch C 2 operates.
  • the second carrier PC 2 of the fifth node N 5 becomes stationary since the second brake B 2 operates.
  • the second planetary gearset PG 2 becomes stationary as a whole since both the second ring gear R 2 and the second carrier PC 2 are stationary. Therefore, the first sun gear S 1 of the sixth node N 6 becomes stationary.
  • the speed line L 1 of the first planetary gearset PG 1 is formed by the sixth node N 6 that is stationary and the fourth node N 4 rotating at the input speed. Therefore, the second node N 2 on the speed line L 1 of the first planetary gearset PG 1 rotates at a speed higher than the input speed. This implies that rotation speed output from the third carrier PC 3 is higher than the input speed. At such a sixth forward speed, only the first planetary gearset PG 1 takes part in the power transmission.
  • the speed line L 1 of the first planetary gearset PG 1 is formed by the fourth node N 4 that is stationary and the sixth node N 6 rotating at the input speed. Therefore, the second node N 2 on the speed line L 1 of the first planetary gearset PG 1 rotates at a negative speed, i.e., rotates reversely, as shown in FIG. 13 . At such a sixth forward speed, only the first planetary gearset PG 1 takes part in the power transmission.
  • FIGS. 14A-14F are charts showing operation states of a power train of an automatic transmission according to a preferred embodiment of the present invention.
  • FIG. 14A shows detailed specifications of the powertrain according to one embodiment, i.e., gear ratios of each planetary gearset.
  • FIG. 14B shows speed ratios in each shift-speed of the powertrain of such an embodiment obtained by the detailed specification of FIG. 14A .
  • FIG. 14C shows rotation speeds of each operational element relative to that of the input element, for each shift-speed.
  • FIG. 14D shows slip speeds of friction elements at each shift-speed.
  • FIG. 14E shows torque loads that each operational element or each friction element undertakes.
  • FIG. 14F shows planetary gearsets that take part in power transmission in each shift-speed.
  • FIG. 14F Details shown in FIG. 14F are apparent from the above description of shifting operation of the powertrain of the present invention, and the numbers shown in FIGS. 14C-14E may be calculated by a person skilled in the art based on the structural features and operational chart of the powertrain of the present embodiment.
  • six forward speeds and one reverse speed are achieved with a minimum number of friction elements such that an automatic transmission becomes lighter and more compact.
  • Durability is increased due to reduction of rotation speeds of operational elements at a shift-speed frequently engaged for acceleration.
  • a further increase of durability and reduction of power loss is also achieved by reduction of slip speeds of friction elements.
  • a shortened route of power transmission also contributes to an increase of durability and reduction of power loss.
  • torque load is dispersed to all operating elements of a planetary gearset, and accordingly the powertrain may endure higher load.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
US11/028,136 2004-09-07 2004-12-30 Six-speed powertrain of an automatic transmission Abandoned US20060052208A1 (en)

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KR10-2004-0071077 2004-09-07
KR1020040071077A KR100610794B1 (ko) 2004-09-07 2004-09-07 자동변속기의 6속 파워 트레인

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US11/221,297 Expired - Fee Related US7291084B2 (en) 2004-09-07 2005-09-07 Six-speed powertrain of an automatic transmission

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US20060063635A1 (en) * 2004-09-07 2006-03-23 Jong Sool Park Six-speed powertrain of an automatic transmission
US20060135310A1 (en) * 2004-12-22 2006-06-22 Shim Hyu T Six-speed powertrain of automatic transmission
US20080261763A1 (en) * 2007-04-19 2008-10-23 Gm Global Technology Operations, Inc. Multi-speed transmission
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KR100610796B1 (ko) * 2004-09-07 2006-08-09 현대자동차주식회사 자동변속기의 6속 파워 트레인
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KR100793887B1 (ko) * 2006-08-14 2008-01-15 현대자동차주식회사 자동변속기의 파워 트레인
US8033947B2 (en) * 2007-06-07 2011-10-11 GM Global Technology Operations LLC Multi-speed transmission
JP5161193B2 (ja) * 2009-11-11 2013-03-13 本田技研工業株式会社 自動変速機
KR101113573B1 (ko) * 2009-11-12 2012-02-22 현대자동차주식회사 하이브리드 차량의 변속기
KR101090812B1 (ko) * 2010-06-30 2011-12-08 현대자동차주식회사 차량용 자동 변속기의 기어 트레인
US8444526B1 (en) * 2012-04-05 2013-05-21 The Gates Corporation Multi-ratio planetary gear transmission
US8617022B1 (en) 2013-01-09 2013-12-31 Toyota Motor Engineering & Manufacturing North America, Inc. Multi-speed automatic transmission
US8529396B1 (en) 2013-01-09 2013-09-10 Toyota Motor Engineering & Manufacturing North America, Inc. Multi-speed automatic transmission
KR101693933B1 (ko) * 2014-11-04 2017-01-06 현대자동차주식회사 차량용 다단 자동변속기
KR101664045B1 (ko) * 2014-12-15 2016-10-10 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인

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DE102004061535B3 (de) 2006-03-09
CN100396963C (zh) 2008-06-25
KR100610794B1 (ko) 2006-08-09
US20060052213A1 (en) 2006-03-09
JP2006077973A (ja) 2006-03-23
CN1746533A (zh) 2006-03-15
JP4671274B2 (ja) 2011-04-13
KR20060022333A (ko) 2006-03-10
US7291084B2 (en) 2007-11-06

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