WO2013129440A1 - Dispositif de transmission automatique - Google Patents

Dispositif de transmission automatique Download PDF

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Publication number
WO2013129440A1
WO2013129440A1 PCT/JP2013/055049 JP2013055049W WO2013129440A1 WO 2013129440 A1 WO2013129440 A1 WO 2013129440A1 JP 2013055049 W JP2013055049 W JP 2013055049W WO 2013129440 A1 WO2013129440 A1 WO 2013129440A1
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WO
WIPO (PCT)
Prior art keywords
clutch
brake
rotating element
planetary gear
automatic transmission
Prior art date
Application number
PCT/JP2013/055049
Other languages
English (en)
Japanese (ja)
Inventor
政弘 大竹
融 左右田
糟谷　悟
宣和 池
加藤　博
慎司 大板
森瀬　勝
Original Assignee
アイシン・エィ・ダブリュ株式会社
トヨタ自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン・エィ・ダブリュ株式会社, トヨタ自動車株式会社 filed Critical アイシン・エィ・ダブリュ株式会社
Publication of WO2013129440A1 publication Critical patent/WO2013129440A1/fr

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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
    • 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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch

Definitions

  • the present invention relates to an automatic transmission apparatus that shifts the power input to an input member and outputs it to an output member.
  • an automatic transmission device when an automatic transmission is configured by three planetary gear mechanisms and a plurality of clutches and brakes, there are many ways to connect the rotating elements of the three planetary gear mechanisms and to attach a plurality of clutches and brakes. There are some that can function as an automatic transmission device and some that cannot function depending on the connection and installation. Further, when clutches and brakes are formed as friction engagement elements, drag at the time of release is unavoidable, so it is desirable that the number of clutches and brakes to be released at each shift stage is as small as possible. Furthermore, when the clutch or brake is formed as a friction engagement element, it is necessary to maintain the hydraulic pressure in order to maintain the engagement of the clutch or the brake. This reduces energy efficiency.
  • the automatic transmission apparatus is mainly intended to propose a new automatic transmission apparatus including three planetary gear mechanisms, five clutches, and two brakes, and reduces drag loss in the automatic transmission apparatus. Another object is to improve the transmission efficiency of the apparatus.
  • the automatic transmission apparatus employs the following means in order to achieve the main object described above.
  • the automatic transmission device of the present invention is An automatic transmission device that shifts the power input to the input member and outputs it to the output member, A first planetary gear mechanism having a first rotating element, a second rotating element, and a third rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A second planetary gear mechanism having a fourth rotating element, a fifth rotating element, and a sixth rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A third planetary gear mechanism having a seventh rotating element, an eighth rotating element, and a ninth rotating element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A first connecting element that connects the second rotating element and the fifth rotating element; A first clutch for engaging and releasing the input member and the first rotating element; A second clutch that engages the first rotating element and the fourth rotating element and releases the engagement; A third clutch for engaging and releasing the sixth rotating element and the seventh rotating element; A fourth clutch for engaging and releasing the seventh rotating element and the first connecting element; A fifth clutch
  • the first planetary element having the first rotating element, the second rotating element, and the third rotating element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram as the three rotating elements.
  • the fifth rotating element is connected by the first connecting element.
  • the input member and the first rotating element are connected via the first clutch, the first rotating element and the fourth rotating element are connected via the second clutch, and the sixth rotating element is connected via the third clutch.
  • the seventh rotating element, the seventh rotating element and the first connecting element are connected via the fourth clutch, the fourth rotating element and the ninth rotating element are connected via the fifth clutch,
  • the first brake is connected to the sixth rotating element, the second brake is connected to the ninth rotating element, the input member is connected to the eighth rotating element, and the output member is connected to the third rotating element.
  • the first forward speed to the ninth forward speed and the reverse speed can be configured as follows.
  • the first forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the first brake and releasing the third clutch, the fifth clutch, and the second brake.
  • the second forward speed is formed by engaging the first clutch, the fourth clutch, the fifth clutch, and the first brake and releasing the second clutch, the third clutch, and the second brake.
  • the third forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the first brake and releasing the second clutch, the fourth clutch, and the second brake.
  • the fourth forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the fifth clutch and releasing the fourth clutch, the first brake, and the second brake.
  • the fifth forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the second brake and releasing the second clutch, the fourth clutch, and the first brake.
  • the sixth forward speed is formed by engaging the second clutch, the third clutch, the fifth clutch, and the second brake and releasing the first clutch, the fourth clutch, and the first brake.
  • the seventh forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the second brake and releasing the fourth clutch, the fifth clutch, and the first brake.
  • the eighth forward speed is formed by engaging the second clutch, the third clutch, the fourth clutch, and the second brake and releasing the first clutch, the fifth clutch, and the first brake.
  • the ninth forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the second brake and releasing the third clutch, the fifth clutch, and the first brake.
  • the reverse gear is formed by engaging the first clutch, the fifth clutch, the first brake, and the second brake and releasing the second clutch, the third clutch, and the fourth clutch.
  • the first brake may be configured as a dog brake.
  • the dog brake is susceptible to shock when engaged and requires synchronous control to synchronize its rotation, but the first brake is engaged continuously from the first forward speed to the third forward speed and moves forward from the fourth forward speed. Since the release continues up to the ninth gear, engagement and release are not repeated frequently, and the frequency of occurrence of synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed. On the other hand, since the dog brake does not need to hold the hydraulic pressure when engaged, energy loss can be suppressed as compared with a hydraulically driven brake that requires holding the hydraulic pressure. As a result, the energy efficiency of the apparatus can be improved.
  • the first planetary gear mechanism and the second planetary gear mechanism are configured as a single pinion type planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements.
  • the third planetary gear mechanism is configured as a double-pinion planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements, and the first rotating element and the second rotating element.
  • the third rotating element is a sun gear, a carrier, and a ring gear
  • the fourth rotating element, the fifth rotating element, and the sixth rotating element are a sun gear, a carrier, and a ring gear
  • the seventh rotating element The eighth rotating element and the ninth rotating element may be a sun gear, a ring gear, and a carrier.
  • the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in this order from the input member. It can also be.
  • FIG. 1 is a configuration diagram showing an outline of a configuration of an automatic transmission device 1 as an embodiment of the present invention. It is an operation
  • FIG. 1 is a block diagram showing an outline of the configuration of an automatic transmission device 1 as an embodiment of the present invention.
  • the automatic transmission device 1 includes two single-pinion planetary gear mechanisms 10 and 20, one double-pinion planetary gear mechanism 30, five clutches C1 to C5, and two brakes B1 and B2.
  • a vehicle for example, front engine front drive type
  • an engine as an internal combustion engine not shown
  • It is configured as a stepped transmission mechanism that is input from an input shaft (input shaft) 3 via a starting device such as a converter and that shifts the input power and outputs it to the output gear 4.
  • the power output to the output gear 4 is output to the left and right drive wheels 7a and 7b via the gear mechanism 5 and the differential gear 6.
  • the gear mechanism 5 includes a counter shaft 5a having a rotation shaft arranged parallel to the rotation shaft of the output gear 4, a counter driven gear 5b that is attached to the counter shaft 5a and meshes with the output gear 4, and a differential that is also attached to the counter shaft 5a.
  • the differential drive gear 5c meshes with the ring gear of the gear 6.
  • the lower side of the input shaft 3 in the drawing mainly shows the connection relationship between the output gear 4 and the gear mechanism 5 in the configuration of the automatic transmission device 1, and the others are omitted.
  • the automatic transmission device 1 of the embodiment includes three planetary gear mechanisms 10, 20, and 30 in order from the input shaft 3 side (right side in FIG. 1) connected to the engine side in order from the first planetary gear.
  • the mechanism 10, the second planetary gear mechanism 20, and the third planetary gear mechanism 30 are arranged.
  • the first planetary gear mechanism 10 includes a sun gear 11 as an external gear, a ring gear 13 as an internal gear disposed concentrically with the sun gear 11, and a plurality of gears meshed with the sun gear 11 and meshed with the ring gear 13.
  • a pinion gear 14 and a carrier 12 that couples and holds the plurality of pinion gears 14 so as to rotate and revolve freely. Since the first planetary gear mechanism 10 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 11, the ring gear 13, and the carrier 12, are spaced at intervals corresponding to the gear ratio in the velocity diagram. ,
  • the gear ratio ⁇ 1 of the first planetary gear mechanism 10 (the number of teeth of the sun gear 11 / the number of teeth of the ring gear 13) is set to 0.25, for example.
  • the second planetary gear mechanism 20 includes a sun gear 21 as an external gear, a ring gear 23 as an internal gear arranged concentrically with the sun gear 21, and a plurality of gears meshed with the sun gear 21 and meshed with the ring gear 23.
  • a pinion gear 24 and a carrier 22 that couples and holds the plurality of pinion gears 24 so as to rotate and revolve freely are provided. Since the second planetary gear mechanism 20 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 21, the ring gear 23, and the carrier 22, are spaced at intervals corresponding to the gear ratio in the velocity diagram. , The sun gear 21, the carrier 22, and the ring gear 23.
  • the gear ratio ⁇ 2 (number of teeth of the sun gear 21 / number of teeth of the ring gear 23) of the second planetary gear mechanism 20 is set to 0.65, for example.
  • the third planetary gear mechanism 30 includes a sun gear 31 as an external gear, a ring gear 32 as an internal gear disposed concentrically with the sun gear 31, and a plurality of first pinion gears 34 that mesh with the sun gear 31.
  • a plurality of second pinion gears 35 meshing with the first pinion gear 34 and meshing with the ring gear 32; and a plurality of first pinion gears 34 and a carrier 33 holding the plurality of second pinion gears 35 so as to rotate and revolve.
  • the third planetary gear mechanism 30 is configured as a double pinion planetary gear mechanism, the three rotating elements, the sun gear 31, the ring gear 32, and the carrier 33, are spaced at intervals corresponding to the gear ratio in the velocity diagram.
  • the sun gear 31, the ring gear 32, and the carrier 33 are set to 0.50, for example.
  • the carrier 12 of the first planetary gear mechanism 10 is connected to the carrier 22 of the second planetary gear mechanism 20 by a first connecting element 51.
  • the input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1.
  • the sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 21 of the second planetary gear mechanism 20 via the clutch C2.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3.
  • the sun gear 31 of the third planetary gear mechanism 30 is connected to the first coupling element 51 via the clutch C4.
  • the sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the case (automatic transmission device case) 2 via the brake B1, and the carrier 33 of the third planetary gear mechanism 30 is connected to the case via the brake B2. 2 is connected.
  • the input shaft 3 is connected to the ring gear 32 of the third planetary gear mechanism 30, and the output gear 4 is connected to the ring gear 13 of the first planetary gear mechanism 10.
  • the five clutches C1 to C5 and the two brakes B1 and B2 are each configured as a hydraulically driven friction clutch or friction brake that is engaged by pressing the friction plate with a piston.
  • the automatic transmission apparatus 1 has a first forward speed to a ninth forward speed by a combination of engagement and release of the five clutches C1 to C5 and engagement and release of the two brakes B1 and B2.
  • the reverse gear can be switched.
  • FIG. 2 shows an operation table of the automatic transmission device 1
  • FIG. 3 shows a speed diagram of the first to third planetary gear mechanisms 10, 20, 30 of the automatic transmission device 1.
  • FIG. 3 shows a velocity diagram of the first planetary gear mechanism 10, a velocity diagram of the second planetary gear mechanism 20, and a velocity diagram of the third planetary gear mechanism 30 in order from the left.
  • the sun gear, the carrier, and the ring gear are arranged in this order from the left.
  • the sun gear, the ring gear, and the carrier are arranged from the left. They are in order.
  • “1st” represents the first forward speed
  • “2nd” represents the second forward speed
  • “3rd” represents the third forward speed
  • “4th” to “9th” represents the fourth forward speed.
  • “Rev” indicates the reverse gear.
  • “ ⁇ 1” to “ ⁇ 3” indicate the gear ratio of each planetary gear mechanism
  • “B1” and “B2” indicate the brakes B1 and B2.
  • “Input” indicates the connection position of the input shaft 3
  • “Output” indicates the connection position of the output gear 4.
  • the first forward speed to the ninth forward speed and the reverse speed are formed as follows.
  • the gear ratio (the number of revolutions of the input shaft 3 / the number of revolutions of the output gear 4) is 0.25, 0,...
  • the case where 65,0.50 was used was shown.
  • the first forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2, and the gear ratio is 4 .125.
  • the second forward speed can be formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2, and the gear ratio is 2 .190.
  • the third forward speed can be formed by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2, and the gear ratio is 1 .361.
  • the fourth forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5 and releasing the clutch C4, the brake B1, and the brake B2, and the gear ratio is 1. .000.
  • the fifth forward speed can be established by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C2, the clutch C4, and the brake B1, and the gear ratio is 0. 790.
  • the sixth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C1, the clutch C4, and the brake B1, and the gear ratio is 0. .660.
  • the seventh forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C3, and the brake B2, and releasing the clutch C4, the clutch C5, and the brake B1, and the gear ratio is 0. .569.
  • the eighth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C5, and the brake B1, and the gear ratio is 0. .500.
  • the ninth forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C3, the clutch C5, and the brake B1, and the gear ratio is 0. .444.
  • the reverse gear can be formed by engaging the clutch C1, the clutch C5, the brake B1, and the brake B2 and releasing the clutch C2, the clutch C3, and the clutch C4, and the gear ratio is ⁇ 4. 000.
  • the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30 0.25, 0.65, 0.50 are used as the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30.
  • the gear ratio of the first forward speed, which is the lowest speed stage is 4.125
  • the gear ratio of the ninth forward speed, which is the highest speed stage is 0.444. 9.291.
  • the automatic transmission device 1 according to the embodiment is configured as a transmission having nine speeds from the first forward speed to the ninth forward speed, it is compared with a transmission having eight or fewer forward speeds.
  • the driving performance can be improved by improving the acceleration performance and the fuel efficiency and reducing the shock at the time of shifting.
  • the five clutches C1 to C5 are configured as friction clutches and the two brakes B1 and B2 are configured as friction brakes.
  • the number of clutches and brakes to be released is three at any shift speed, drag loss due to the release of clutches and brakes is greater than that of four or more clutches or brakes to be released. Can be suppressed.
  • the single-pinion type first planetary gear mechanism 10 the single-pinion type second planetary gear mechanism 20, and the double-pinion-type third planetary gear.
  • a mechanism 30, five clutches C 1 to C 5, and two brakes B 1 and B 2 are provided, and the carrier 12 of the first planetary gear mechanism 10 is transferred to the carrier 22 of the second planetary gear mechanism 20 by the first connecting element 51.
  • the input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1, and the sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 11 of the second planetary gear mechanism 20 via the clutch C2.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3, and the sun gear 31 of the third planetary gear mechanism 30 is connected. Is connected to the first coupling element 51 via the clutch C4, and the sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5.
  • the ring gear 23 of the planetary gear mechanism 20 is connected to the case 2 via the brake B1, the carrier 33 of the third planetary gear mechanism 30 is connected to the case 2 via the brake B2, and the ring gear of the third planetary gear mechanism 30 is connected.
  • the first forward speed is achieved by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2.
  • the second forward speed is formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1 and releasing the clutch C2, the clutch C3, and the brake B2, and the third forward speed is defined as the clutch C1. It is formed by engaging the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2.
  • the fourth forward speed is established by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5.
  • the 9th forward speed is shifted between clutch C1, clutch C2, and clutch C4.
  • the clutch B3 is engaged and the clutch C3, the clutch C5, and the brake B1 are released, and the reverse gear is engaged with the clutch C1, the clutch C5, the brake B1, and the brake B2, and the clutch C2 and the clutch C3.
  • the number of clutches and brakes to be released can be reduced to three at any shift stage, and the number of clutches and brakes to be released should be four or more. In comparison, loss due to dragging of the clutch or brake to be released can be reduced, and transmission efficiency of the entire apparatus can be improved. Further, since nine shift stages from the first forward speed to the ninth forward speed are formed, the driving performance can be improved as compared with the one that forms eight or less speed stages.
  • FIG. 4 shows a modified automatic transmission device 101 in which the brake B1 is configured as a dog brake.
  • the operation table and speed diagram of the automatic transmission device 101 of the modification are the same as those in FIGS.
  • the dog brake is easily shocked when engaged, and synchronous control is required to synchronize the rotation.
  • the brake B1 is continuously engaged from the first forward speed to the third forward speed, and from the fourth forward speed to the forward 9 speed.
  • the engine is mounted on a vehicle (for example, a front engine front drive type) in which the engine is disposed horizontally (in the left-right direction of the vehicle). It may be mounted on a vehicle of a type (for example, front engine rear drive type) arranged in the vehicle front-rear direction.
  • the first planetary gear mechanism 10 the second planetary gear mechanism 20, and the third planetary gear of the automatic transmission device 1 of FIG.
  • the input shaft 3 extends to the opposite side (left side in FIGS. 1 and 5) and the ring gear of the first planetary gear mechanism 10
  • a hollow rotating shaft 4a for transmitting the rotation to the output shaft 4b on the opposite side (right side in FIGS. 1 and 5) from the input shaft 3 may be connected to 13.
  • 0.25, 0.65, 0.50 are used as the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30.
  • the ratios ⁇ 1, ⁇ 2, and ⁇ 3 are not limited to these values.
  • the first planetary gear mechanism 10 and the second planetary gear mechanism 20 are configured as a single pinion type planetary gear mechanism
  • the third planetary gear mechanism 30 is configured as a double pinion type.
  • the first to third planetary gear mechanisms 10, 20, 30 may be configured as all single type planetary gear mechanisms, or the first to third planetary gear mechanisms 10, 20. 30, 30 as a double pinion planetary gear mechanism, or a part of the first to third planetary gear mechanisms 10, 20, 30 is configured as a single pinion planetary gear and the remaining portion It may be configured as a double pinion type planetary gear mechanism.
  • the automatic transmission device 1 In the automatic transmission device 1 according to the embodiment, four of the five clutches C1 to C5 and the two brakes B1 and B2 are engaged and the other three are released, thereby moving forward from the first forward speed 9
  • the automatic transmission apparatus may be capable of selecting a shift of a reverse speed and a reverse speed that is less than the 7th speed.
  • the input shaft (input shaft) 3 corresponds to an “input member”
  • the output gear 4 corresponds to an “output member”
  • the first planetary gear mechanism 10 corresponds to a “first planetary gear mechanism”.
  • the sun gear 11 corresponds to the “first rotating element”
  • the carrier 12 corresponds to the “second rotating element”
  • the ring gear 13 corresponds to the “third rotating element”
  • the second planetary gear mechanism 20 corresponds to “ It corresponds to the “second planetary gear mechanism”
  • the sun gear 21 corresponds to the “fourth rotating element”
  • the carrier 22 corresponds to the “fifth rotating element”
  • the ring gear 23 corresponds to the “sixth rotating element”
  • the third planetary gear mechanism 30 corresponds to a “third planetary gear mechanism”
  • the sun gear 31 corresponds to a “seventh rotating element”
  • the ring gear 32 corresponds to an “eighth rotating element”
  • the carrier 33 corresponds to “
  • the first connecting element 51 corresponds to the “ninth rotating element” and the “first connecting element”
  • the clutch C1 corresponds to the “first clutch”
  • the clutch C2 corresponds to the “second clutch”
  • the clutch C3 corresponds to the “third clutch”
  • the clutch C5 corresponds to the “fifth clutch”
  • the brake B1 corresponds to the “first brake”
  • the brake B2 corresponds to the “second brake”.
  • the present invention can be used in the manufacturing industry of automatic transmission devices.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

La présente invention est pourvue de trois mécanismes à engrenage planétaire (10, 20, 30), de cinq embrayages (C1 à C5), et de deux freins (B1, B2), le support (12) du premier mécanisme à engrenage planétaire (10) étant connecté au support (22) du deuxième mécanisme à engrenage planétaire (20) au moyen d'un premier élément de connexion (51). Un arbre d'entrée (3) est connecté à la couronne planétaire (32) du troisième mécanisme à engrenage planétaire (30), un engrenage de sortie (4) est connecté à la couronne planétaire (13) du premier mécanisme à engrenage planétaire (10), et des engrenages 1 à 9 et un pignon de marche arrière sont formés en mettant en prise quatre et en libérant trois embrayages (C1 à C5) et les freins (B1, B2).
PCT/JP2013/055049 2012-02-29 2013-02-27 Dispositif de transmission automatique WO2013129440A1 (fr)

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JP2012044706 2012-02-29
JP2012-044706 2012-02-29

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Citations (3)

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Publication number Priority date Publication date Assignee Title
JP3102050B2 (ja) * 1991-03-28 2000-10-23 日産自動車株式会社 自動変速機の遊星歯車列
JP2011231897A (ja) * 2010-04-28 2011-11-17 Honda Motor Co Ltd 自動変速機
JP2012013209A (ja) * 2010-07-05 2012-01-19 Jatco Ltd 自動変速機

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