WO2015152067A1 - Transmission multiétagée - Google Patents

Transmission multiétagée Download PDF

Info

Publication number
WO2015152067A1
WO2015152067A1 PCT/JP2015/059694 JP2015059694W WO2015152067A1 WO 2015152067 A1 WO2015152067 A1 WO 2015152067A1 JP 2015059694 W JP2015059694 W JP 2015059694W WO 2015152067 A1 WO2015152067 A1 WO 2015152067A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
engagement
planetary gear
engagement element
rotating
Prior art date
Application number
PCT/JP2015/059694
Other languages
English (en)
Japanese (ja)
Inventor
貴義 加藤
森本　隆
青木　敏彦
加藤　博
宮崎　光史
森瀬　勝
慎司 大板
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 WO2015152067A1 publication Critical patent/WO2015152067A1/fr

Links

Images

Classifications

    • 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
    • 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
    • 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
    • F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
    • 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
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Definitions

  • the invention of the present disclosure relates to a multi-stage transmission that shifts power transmitted from a motor of a vehicle to an input member and transmits the power to an output member.
  • this type of multi-speed transmission includes four single pinion planetary gears, four clutches, and two brakes, and includes forward and reverse speeds from the first speed to the tenth speed.
  • What is provided is known (see, for example, Patent Document 1).
  • drivability that is, acceleration performance of the vehicle can be further improved.
  • the main object of the present disclosure is to improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of a vehicle equipped with a multi-stage transmission.
  • the multi-stage transmission of the present disclosure is a multi-stage transmission that shifts power transmitted to the input member and transmits the power to the output member.
  • the first, second, third and fourth rotating elements of the first, second, third and fourth planetary gears are connected to other rotating elements or stationary members, respectively, and the connection between them is released.
  • the first planetary gear and the third planetary gear are arranged in order corresponding to the gear ratio of the first and third planetary gears, the first rotation element, the second rotation element, the third rotation element, and the fourth Constructing a compound planetary gear mechanism having a rotating element
  • the second planetary gear has a fifth rotating element, a sixth rotating element, and a seventh rotating element arranged in order corresponding to the gear ratio
  • the fourth planetary gear has an eighth rotation element, a ninth rotation element, and a tenth rotation element arranged in order corresponding to the gear ratio
  • the sixth rotating element of the second planetary gear is always connected to the input member;
  • the ninth rotating element of the fourth planetary gear is always connected to the output member;
  • the first rotating element of the compound planetary gear mechanism and the eighth rotating element of the fourth planetary gear are always connected,
  • the second rotating element of the compound planetary gear mechanism and the sixth rotating element of the second planetary gear are always connected,
  • the first engaging element connects the third rotating element of the compound planetary gear mechanism and
  • the second engaging element connects the fourth rotating element of the compound planetary gear mechanism and the fifth rotating element of the second planetary gear to each other, and releases the connection between them.
  • the third engaging element connects the seventh rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear to each other, and releases the connection between them.
  • the fourth engaging element includes the first rotating element of the compound planetary gear mechanism, the eighth rotating element of the fourth planetary gear, and the seventh rotating element of the second planetary gear that are always connected.
  • the fifth engaging element connects the fifth rotating element of the second planetary gear to the stationary member and fixes the non-rotatable, and releases the connection between the two
  • the sixth engaging element is configured to connect the tenth rotating element of the fourth planetary gear to the stationary member so as to be non-rotatable and to release the connection therebetween.
  • the first, second, third, fourth, fifth and sixth engaging elements are selectively engaged with each other by first engaging them. It is possible to form a forward gear and a reverse gear from the first gear to the ninth gear or the tenth gear. As a result, the spread can be further increased, so that the speed ratio of the low speed stage is increased and the speed ratio of the high speed stage is further reduced to improve the fuel efficiency of the vehicle on which the multi-stage transmission is mounted, and to the driver That is, the acceleration performance of the vehicle can be further improved.
  • this multi-stage transmission when planetary gears including ring gears are used as the first, second, third, and fourth planetary gears, the forward travel from the first speed to the ninth speed or the tenth speed is performed. It is possible to prevent an increase in inertia during the rotation of the ring gear by preventing the ring gear having a particularly large diameter from rotating at a high rotational speed when forming the step and the reverse step. As a result, the time required for engaging the engaging element is shortened, the occurrence of shock at the time of shifting accompanied by the engagement of the engaging element is suppressed, and the durability of the friction material of the engaging element is improved. Can be secured. As a result, in the multi-stage transmission according to the present disclosure, it is possible to further improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of the vehicle in which the multi-stage transmission is mounted.
  • FIG. 1 is a schematic configuration diagram of a power transmission device including a multi-stage transmission according to an embodiment of the present disclosure.
  • FIG. 2 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed in the multi-stage transmission of FIG. 1.
  • FIG. 2 is an operation table showing the relationship between each shift stage and the operation states of clutches and brakes in the multi-stage transmission of FIG.
  • FIG. 5 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed in the multi-stage transmission of FIG. 4. It is a schematic block diagram of the power transmission device containing the multi-stage transmission which concerns on other embodiment of this indication.
  • FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 as a multi-stage transmission according to an embodiment of the present disclosure.
  • a power transmission device 10 shown in these drawings is connected to a crankshaft of an engine (internal combustion engine) (not shown) as a drive source mounted horizontally in a front portion of a front-wheel drive vehicle and power (torque) from the engine. Can be transmitted to left and right front wheels (drive wheels) (not shown).
  • the power transmission device 10 shifts the power transmitted from the engine to the input shaft 20i and transmits it to a counter drive gear 41 as an output member, in addition to a transmission case (stationary member). 11, a starting device (fluid transmission device) 12, an oil pump 17, and the like.
  • the starting device 12 includes an input-side pump impeller 14p connected to the drive source as described above, an output-side turbine runner 14t connected to the input shaft (input member) 20i of the automatic transmission 20, a pump impeller 14p, A stator 14s that is disposed inside the turbine runner 14t and rectifies the flow of hydraulic oil from the turbine runner 14t to the pump impeller 14p. A one-way clutch that is supported by a stator shaft (not shown) and restricts the rotational direction of the stator 14s in one direction. Including a torque converter having 14o and the like.
  • the starting device 12 connects the front cover connected to the crankshaft of the engine and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the front cover and the automatic transmission. And a damper mechanism 16 that damps vibration between the input shaft 20 i of the machine 20.
  • the starting device 12 may include a fluid coupling that does not have the stator 14s.
  • the oil pump 17 includes a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 14p of the starting device 12, an internal gear (outer rotor) meshed with the external gear, and the like. It is comprised as a gear pump having.
  • the oil pump 17 is driven by power from the engine, sucks hydraulic oil (ATF) stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown).
  • ATF hydraulic oil
  • the automatic transmission 20 is configured as a 10-speed transmission, and as shown in FIG. 1, in addition to the input shaft 20i, a counter drive gear 41 as an output member, and an automatic transmission 20 (input shaft 20i) a compound planetary gear mechanism 25 configured by combining a single pinion type first planetary gear 21 and a single pinion type third planetary gear 23 arranged side by side in the axial direction, and a single pinion type second planetary gear.
  • a gear 22 and a single pinion type fourth planetary gear 24 are included.
  • the automatic transmission 20 includes a clutch C1 as a first engagement element for changing a power transmission path from the input shaft 20i to the counter drive gear 41 as an output member, a clutch C2 as a second engagement element, A clutch C3 as a third engagement element, a clutch C4 as a fourth engagement element, a brake B1 as a fifth engagement element, and a brake B2 as a sixth engagement element are included.
  • the power (torque) transmitted from the automatic transmission 20 to the counter drive gear 41 is transmitted to the counter driven gear 42 via the counter drive gear 41 and the counter driven gear 42 meshing with the counter drive gear 41 and the counter shaft 43.
  • the drive pinion gear (final drive gear) 44, the gear train 40 having a differential ring gear (final driven gear) 45 meshing with the drive pinion gear 44, the differential gear 50 connected to the differential ring gear 45, and the drive shaft 51 are connected. Is transmitted to the left and right front wheels.
  • the compound planetary gear mechanism 25, the second planetary gear 22, and the fourth planetary gear 24 are supplied from the starting device 12, that is, from the engine side (the right side in FIG. 1), to the second planetary gear 22 and the fourth planetary gear 24.
  • the compound planetary gear mechanism 25, that is, the second planetary gear 22, the fourth planetary gear 24, the first planetary gear 21 constituting the compound planetary gear mechanism 25, and the third planetary gear 23 constituting the compound planetary gear mechanism 25. are arranged in the transmission case 11 so as to line up.
  • the clutch C1 is disposed between, for example, the first planetary gear 21 and the fourth planetary gear 24, and the clutch C2 is disposed on the opposite side of the starting device 12 with respect to the third planetary gear 23, for example.
  • C3 and C4 are disposed, for example, between the second planetary gear 22 and the fourth planetary gear 24, and the brake B1 is disposed, for example, on the opposite side of the starting device 12 with respect to the third planetary gear 24, and the brake B2 Is arranged outside the fourth planetary gear 24 or the clutches C3 and C4, for example.
  • the first planetary gear 21 constituting the compound planetary gear mechanism 25 includes a first sun gear 21s that is an external gear, a first ring gear 21r that is an internal gear arranged concentrically with the first sun gear 21s, respectively.
  • the third planetary gear 23 constituting the compound planetary gear mechanism 25 includes a third sun gear 23s that is an external gear, a third ring gear 23r that is an internal gear arranged concentrically with the third sun gear 23s, respectively.
  • the first carrier 21c of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23 are always connected via a connecting member, and always rotate integrally (and coaxially). Or stop.
  • the first ring gear 21r of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23 are always connected via a connecting member, and always rotate or stop integrally (and coaxially).
  • the compound planetary gear mechanism 25 is always connected to the first sun gear 21s of the first planetary gear 21, the first carrier 21c of the first planetary gear 21 that is always connected, and the third ring gear 23r of the third planetary gear 23.
  • the first planetary gear 21 has four rotation elements, that is, the first ring gear 21r, the third planetary gear 23, the third carrier 23c, and the third planetary gear 23, the third sun gear 23s.
  • the second planetary gear 22 includes a second sun gear 22s that is an external gear, a second ring gear 22r that is an internal gear disposed concentrically with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r, respectively. And a second carrier 22c that holds the plurality of second pinion gears 22p so that they can rotate (rotate) and revolve freely.
  • the second carrier 22c of the second planetary gear 22 is always connected to the input shaft 20i.
  • the second carrier 22c is always connected to the first carrier 21c of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23, which are always connected, via a connecting member, and the first carrier 21c. And it always rotates or stops integrally (and coaxially) with the third ring gear 23r.
  • the fourth planetary gear 24 includes a fourth sun gear 24s that is an external gear, a fourth ring gear 24r that is an internal gear disposed concentrically with the fourth sun gear 24s, and a fourth sun gear 24s and a fourth ring gear 24r, respectively. And a fourth carrier 24c that holds the plurality of fourth pinion gears 24p so as to freely rotate (rotate) and revolve.
  • the fourth carrier 24c of the fourth planetary gear 24 is always connected to a counter drive gear 41 as an output member.
  • the fourth sun gear 24s of the fourth planetary gear 24 is always connected to the first sun gear 21s of the first planetary gear 21 via a connecting member, and always rotates or coaxially with the first sun gear 21s. Stop.
  • the clutch C1 connects the first ring gear 21r of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23, and the fourth carrier 24c of the fourth planetary gear 24, which are always coupled, Disconnect the connection.
  • the clutch C2 connects the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23 to each other and releases the connection between them.
  • the clutch C3 connects and disconnects the second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 from each other.
  • the clutch C4 connects the first sun gear 21s of the first planetary gear 21 and the fourth sun gear 24s of the fourth planetary gear 24, and the second ring gear 22r of the second planetary gear 22 that are always connected to each other. Disconnect the connection.
  • the brake B1 fixes (connects) the second sun gear 22s of the second planetary gear 22 to the transmission case 11 as a stationary member so as not to rotate, and releases the second sun gear 22s to the transmission case 11 so as to be rotatable.
  • the brake B2 fixes (connects) the fourth ring gear 24r of the fourth planetary gear 24 to the transmission case 11 as a stationary member in a non-rotatable manner and releases the fourth ring gear 24r so as to be rotatable with respect to the transmission case 11. To do.
  • a piston a plurality of friction engagement plates (for example, a friction plate formed by sticking a friction material on both surfaces of an annular member, and an annular member formed smoothly on both surfaces)
  • a multi-plate friction type hydraulic clutch having a hydraulic servo composed of a separator plate), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal oil pressure cancellation chamber, and the like are employed.
  • a multi-plate friction hydraulic brake having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like. Is adopted.
  • the clutches C1 to C4 and the brakes B1 and B2 operate by receiving and supplying hydraulic oil from a hydraulic control device (not shown).
  • FIG. 2 is a velocity diagram showing the ratio of the rotational speed of each rotary element to the rotational speed (input rotational speed) of the input shaft 20i in the automatic transmission 20 (however, the input shaft 20i, that is, the second carrier 22c, the first carrier 22c).
  • the rotational speeds of the carrier 21c and the third ring gear 23r are set to a value of 1.
  • FIG. 3 is an operation table showing the relationship between each gear position of the automatic transmission 20 and the operation states of the clutches C1 to C4 and the brakes B1 and B2.
  • the four rotating elements of the compound planetary gear mechanism 25 that is, the first sun gear 21 s of the first planetary gear 21, the first carrier 21 c of the first planetary gear 21 that is always connected, and the third planetary gear. 23, the first ring gear 21r of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23, and the third sun gear 23s of the third planetary gear 23 are sequentially shown in this order.
  • the first sun gear 21s is the first rotating element of the automatic transmission 20
  • the first carrier 21c and the third ring gear 23r are the second rotating elements of the automatic transmission 20
  • the first ring gear 21r and the third carrier 23c are the third rotating element of the automatic transmission 20
  • the third sun gear 23s is the fourth rotating element of the automatic transmission 20.
  • the compound planetary gear mechanism 25 includes the first rotation element, the second rotation element, the third rotation element, and the first rotation element of the automatic transmission 20 that are sequentially arranged at intervals corresponding to the gear ratios ⁇ 1 and ⁇ 3 on the velocity diagram. It has 4 rotating elements.
  • the three rotating elements constituting the single pinion type second planetary gear 22, that is, the second sun gear 22 s, the second ring gear 22 r, and the second carrier 22 c, are velocity diagrams of the second planetary gear 22 (in FIG. 2).
  • the second sun gear 22s, the second carrier 22c, and the second ring gear 22r are arranged in this order from the left side in the drawing at intervals corresponding to the gear ratio ⁇ 2.
  • the second sun gear 22s is the fifth rotating element of the automatic transmission
  • the second carrier 22c is the sixth rotating element of the automatic transmission 20
  • the second ring gear is used.
  • 22r is a seventh rotating element of the automatic transmission 20. Therefore, the second planetary gear 22 has the fifth rotation element, the sixth rotation element, and the seventh rotation element of the automatic transmission 20 that are arranged in order at intervals corresponding to the gear ratio ⁇ 2 on the velocity diagram.
  • the three rotating elements constituting the single pinion type fourth planetary gear 24, that is, the fourth sun gear 24s, the fourth ring gear 24r, and the fourth carrier 24c are speed diagrams of the fourth planetary gear 24 (in FIG. 2).
  • the fourth sun gear 24s, the fourth carrier 24c, and the fourth ring gear 24r are arranged in this order from the left side in the figure at an interval corresponding to the gear ratio ⁇ 4.
  • the fourth sun gear 24s is the eighth rotating element of the automatic transmission
  • the fourth carrier 24c is the ninth rotating element of the automatic transmission 20
  • 24 r is a tenth rotation element of the automatic transmission 20.
  • the fourth planetary gear 24 has the eighth rotation element, the ninth rotation element, and the tenth rotation element of the automatic transmission 20 arranged in order at intervals corresponding to the gear ratio ⁇ 4 on the velocity diagram.
  • the clutches C1 to C4 and the brakes B1 and B2 are engaged or released as shown in FIG. 3 to change the connection relationship of the first to tenth rotating elements, thereby changing the input shaft.
  • the forward first speed is formed by engaging the clutches C2 and C4 and the brake B2 and releasing the remaining clutches C1 and C3 and the brake B1. That is, when the first forward speed is established, the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the compound planetary gear mechanism 25 (third planetary gear 23) are connected to each other by the clutch C2.
  • the clutch C4 connects the first sun gear 21s of the compound planetary gear mechanism 25 (first planetary gear 21), the fourth sun gear 24s of the fourth planetary gear 24, and the second ring gear 22r of the second planetary gear 22, and further.
  • the fourth ring gear 24r of the fourth planetary gear 24 is fixed to the transmission case 11 so as not to rotate by the brake B2.
  • the second forward speed is formed by engaging the clutch C4 and the brakes B1 and B2 and releasing the remaining clutches C1, C2, and C3. That is, when the forward second speed is formed, the clutch C4 causes the first sun gear 21s of the compound planetary gear mechanism 25 (first planetary gear 21), the fourth sun gear 24s of the fourth planetary gear 24, and the second planetary gear 22 to move.
  • the second ring gear 22r is connected to each other, and the second sun gear 22s of the second planetary gear 22 is non-rotatably fixed to the transmission case 11 by the brake B1, and the fourth planetary gear 24 of the fourth planetary gear 24 is fixed by the brake B2.
  • the four ring gear 24r is fixed to the transmission case 11 so as not to rotate.
  • the third forward speed is formed by engaging the clutch C2 and the brakes B1 and B2 and releasing the remaining clutches C1, C3, and C4. That is, when forming the third forward speed, the clutch C2 connects the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the compound planetary gear mechanism 25 (third planetary gear 23) to each other, and The second sun gear 22s of the second planetary gear 22 is non-rotatably fixed to the transmission case 11 by the brake B1, and the fourth ring gear 24r of the fourth planetary gear 24 is rotated by the brake B2 with respect to the transmission case 11. Fixed to impossible.
  • the forward fourth speed is formed by engaging the clutch C1 and the brakes B1 and B2 and releasing the remaining clutches C2, C3, and C4. That is, when the fourth forward speed is established, the first ring gear 21r and the third carrier 23c of the compound planetary gear mechanism 25 and the fourth carrier 24c of the fourth planetary gear 24 are connected to each other by the clutch C1.
  • the second sun gear 22s of the second planetary gear 22 is non-rotatably fixed to the transmission case 11 by B1, and the fourth ring gear 24r of the fourth planetary gear 24 is non-rotatable to the transmission case 11 by the brake B2. Fixed.
  • the forward fifth speed is formed by engaging the clutches C1 and C2 and the brake B1 and releasing the remaining clutches C3 and C4 and the brake B2. That is, when the fifth forward speed is established, the first ring gear 21r and the third carrier 23c of the compound planetary gear mechanism 25 and the fourth carrier 24c of the fourth planetary gear 24 are connected to each other by the clutch C1. The second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the compound planetary gear mechanism 25 (third planetary gear 23) are connected to each other by C2, and further, the second sun gear of the second planetary gear 22 is connected by the brake B1. 22s is fixed to the transmission case 11 so as not to rotate.
  • the forward sixth speed is formed by engaging the clutches C1 and C4 and the brake B1 and releasing the remaining clutches C2 and C3 and the brake B2.
  • the first ring gear 21r and the third carrier 23c of the compound planetary gear mechanism 25 and the fourth carrier 24c of the fourth planetary gear 24 are connected to each other by the clutch C1.
  • the first sun gear 21s of the compound planetary gear mechanism 25 (first planetary gear 21), the fourth sun gear 24s of the fourth planetary gear 24, and the second ring gear 22r of the second planetary gear 22 are connected to each other by C4, and further the brake
  • the second sun gear 22s of the second planetary gear 22 is fixed to the transmission case 11 so as not to rotate by B1.
  • the seventh forward speed is formed by engaging the clutches C1, C3, and C4 and releasing the remaining clutch C2 and the brakes B1 and B2. That is, when forming the seventh forward speed, the clutch C1 connects the first ring gear 21r and the third carrier 23c of the compound planetary gear mechanism 25 to the fourth carrier 24c of the fourth planetary gear 24, and the clutch C4.
  • the first sun gear 21s of the compound planetary gear mechanism 25 (first planetary gear 21), the fourth sun gear 24s of the fourth planetary gear 24, and the second ring gear 22r of the second planetary gear 22 are connected to each other, and further by the clutch C3.
  • the second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other.
  • the forward eighth speed is formed by engaging the clutches C1 and C3 and the brake B1 and releasing the remaining clutches C2 and C4 and the brake B2. That is, when the eighth forward speed is established, the first ring gear 21r and the third carrier 23c of the compound planetary gear mechanism 25 and the fourth carrier 24c of the fourth planetary gear 24 are connected to each other by the clutch C1. The second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other by C3, and the second sun gear 22s of the second planetary gear 22 is connected to the transmission case 11 by the brake B1. And fixed so that it cannot rotate.
  • the ninth forward speed is established by engaging the clutches C3 and C4 and the brake B1 and releasing the remaining clutches C1 and C2 and the brake B2. That is, when the ninth forward speed is established, the second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other by the clutch C3, and the compound planetary gear is connected by the clutch C4.
  • the first sun gear 21s of the mechanism 25 (first planetary gear 21), the fourth sun gear 24s of the fourth planetary gear 24, and the second ring gear 22r of the second planetary gear 22 are connected to each other, and further, the second planetary gear by the brake B1.
  • the second sun gear 22 s of the gear 22 is fixed to the transmission case 11 so as not to rotate.
  • the 10th forward speed is formed by engaging the clutches C2 and C3 and the brake B1 and releasing the remaining clutches C1 and C4 and the brake B2. That is, at the time of forming the tenth forward speed, the clutch C2 connects the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the compound planetary gear mechanism 25 (third planetary gear 23) to each other.
  • the second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other by the clutch C3, and the second sun gear 22s of the second planetary gear 22 is further connected to the transmission case 11 by the brake B1. It is fixed so that it cannot rotate.
  • the reverse gear is formed by engaging the clutches C2 and C3 and the brake B2 and releasing the remaining clutches C1 and C4 and the brake B1. That is, when the reverse gear is formed, the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s of the compound planetary gear mechanism 25 (third planetary gear 23) are connected to each other by the clutch C2, and the clutch C3. As a result, the second ring gear 22r of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other, and the fourth ring gear 24r of the fourth planetary gear 24 is connected to the transmission case 11 by the brake B2. Fixed non-rotatable.
  • the step ratio between the first forward speed and the reverse speed is
  • 0.974.
  • the forward speed and the reverse speed from the first speed to the tenth speed can be provided by engaging / disengaging the clutches C1 to C4 and the brakes B1 and B2.
  • the speed ratio of the low speed stage and the speed ratio of the high speed stage are further reduced, It is possible to improve the fuel efficiency of the vehicle on which the automatic transmission 20 is mounted and further improve the acceleration performance of the vehicle. Therefore, according to the automatic transmission 20, it is possible to satisfactorily improve both the fuel consumption of the vehicle on which the automatic transmission 20 is mounted and the drivability, that is, the acceleration performance of the vehicle, the shift feeling, and the like.
  • the first forward speed is achieved by engaging any three of the six engaging elements, that is, the clutches C1 to C4 and the brakes B1 and B2 and releasing the remaining three.
  • the first forward speed is achieved by engaging any three of the six engaging elements, that is, the clutches C1 to C4 and the brakes B1 and B2 and releasing the remaining three.
  • the first forward speed is achieved by engaging any three of the six engaging elements, that is, the clutches C1 to C4 and the brakes B1 and B2 and releasing the remaining three.
  • planetary gears including the first, second, third, or fourth ring gears 21r to 24r are used as the first to fourth planetary gears 21 to 24.
  • the first to fourth ring gears 21r to 24r are prevented from rotating at a high rotational speed so that the first to fourth ring gears 21r to 24r do not rotate at the time of forming the forward gear and the reverse gear from the first gear to the tenth gear.
  • An increase in inertia during rotation (equivalent inertia with respect to the input shaft 20i) can be suppressed.
  • the automatic transmission An increase in size of 20 can be suppressed.
  • the speed change performance and durability of the clutches C1 to C4 and the brakes B1 and B2 can be further improved, and the entire device can be reduced in weight and size.
  • the power transmission efficiency in the automatic transmission 20 that is, the fuel efficiency of the vehicle is further improved. It is possible to further improve the assemblability while reducing the number of parts and suppressing the weight increase of the automatic transmission 20.
  • the fourth forward speed may be formed by engaging the clutches C1, C2 and the brake B2 instead of engaging the clutch C1 and the brakes B1 and B2.
  • the ninth forward speed may be formed by engaging the clutches C2, C3 and the brake B1, instead of engaging the clutches C3, C4 and the brake B1, In this case, the formation of the tenth forward speed may be omitted.
  • FIG. 4 is a schematic configuration diagram of a power transmission device 10B including an automatic transmission 20B as a multi-stage transmission according to another embodiment of the invention of the present disclosure
  • FIG. 5 is a diagram of an input shaft 20i in the automatic transmission 20B. It is a speed diagram which shows ratio of the rotational speed of each rotation element with respect to a rotational speed (input rotational speed).
  • the automatic transmission 20B of the power transmission device 10B shown in FIG. 4 is the same as the automatic transmission 20 described above, in which the compound planetary gear mechanism 25 is composed of a single pinion type first planetary gear 21 and a double pinion type third planetary gear 23B. This corresponds to a so-called CC-RR type compound planetary gear mechanism 25B configured.
  • the third planetary gear 23B includes a third sun gear 23s, a third ring gear 23r, a plurality of pinion gears 231p that mesh with the third sun gear 23s, and a plurality of pinion gears 231p and a third ring gear 23r that respectively mesh with the third sun gear 23s.
  • Pinion gear 232p and a third carrier 23c that holds a plurality of pairs of pinion gears 231p and 232p so as to rotate and revolve freely.
  • the first carrier 21c of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23B are always connected via a connecting member. Rotate or stop as one (and coaxial).
  • the first ring gear 21r of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23B are always connected via a connecting member, and always rotate or stop integrally (and coaxially).
  • the compound planetary gear mechanism 25B is always connected to the first sun gear 21s of the first planetary gear 21, the first carrier 21c of the first planetary gear 21 that is always connected, and the third carrier 23c of the third planetary gear 23B.
  • the first planetary gear 21 has four rotation elements, that is, the first ring gear 21r, the third planetary gear 23B, the third ring gear 23r, and the third planetary gear 23B, the third sun gear 23s.
  • the first carrier 21c and the third carrier 23c which are always connected to the compound planetary gear mechanism 25B, are always connected to the second carrier 22c of the second planetary gear 22 via a connecting member, and the second carrier 22c. Rotate or stop at once (and coaxial).
  • the clutch C1 connects the first ring gear 21r and the third ring gear 23r of the compound planetary gear mechanism 25B and the fourth carrier 24c of the fourth planetary gear 24 to each other and connects the two. It is a thing to cancel.
  • the four rotating elements of the compound planetary gear mechanism 25B that is, the first sun gear 21s of the first planetary gear 21, the first carrier 21c of the first planetary gear 21 always connected, and the third planetary gear.
  • the third carrier 23c of 23B, the first ring gear 21r of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23B, and the third sun gear 23s of the third planetary gear 23B are always connected in this order.
  • 5 is a velocity diagram of the compound planetary gear mechanism 25B at intervals corresponding to the gear ratio ⁇ 1 of the first planetary gear 21 of the single pinion type and the gear ratio ⁇ 3 of the third planetary gear 23B of the double pinion type from the left side in FIG.
  • the first sun gear 21s is the first rotating element of the automatic transmission 20B
  • the first carrier 21c and the third carrier 23c are the second rotating elements of the automatic transmission 20B
  • the first ring gear 21r and the third ring gear 23r are the third rotating element of the automatic transmission 20B
  • the third sun gear 23s is the fourth rotating element of the automatic transmission 20B.
  • the compound planetary gear mechanism 25B includes the first rotation element, the second rotation element, the third rotation element, and the first rotation element of the automatic transmission 20B that are sequentially arranged at intervals corresponding to the gear ratios ⁇ 1 and ⁇ 3 on the velocity diagram. It has 4 rotating elements.
  • the fourth forward speed may be formed by engaging the clutches C1, C2 and the brake B2 instead of engaging the clutch C1, the brakes B1 and B2.
  • the ninth forward speed may be formed by engaging the clutches C2, C3 and the brake B1, instead of engaging the clutches C3, C4 and the brake B1, In this case, the formation of the forward tenth speed may be omitted.
  • FIG. 6 is a schematic configuration diagram of a power transmission device 10C including an automatic transmission 20C as a multi-stage transmission according to another embodiment of the invention of the present disclosure.
  • the automatic transmission 20C of the power transmission device 10C shown in FIG. 6 is the same as the automatic transmission 20 described above, in which the compound planetary gear mechanism 25 is overlapped with the single pinion type first and third planetary gears 21, 23 in the radial direction. This is equivalent to the one replaced by the compound planetary gear mechanism 25C arranged as described above.
  • the third planetary gear 23 can be disposed so as to surround the first planetary gear 21, so that the axial length of the automatic transmission 20C and thus the power transmission device 10C can be increased. It becomes possible to shorten more. Further, even if the compound planetary gear mechanism 25C is employed, it is possible to further improve the assembling performance while reducing the number of parts and suppressing the increase in the weight of the automatic transmission 20C.
  • the first carrier 21c of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23 are integrated with each other or via a connecting member. Are always connected, and always rotate or stop integrally (and coaxial). Further, the first ring gear 21r of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 are formed integrally with each other such that the third sun gear 23s surrounds the first ring gear 21r, or It is always connected (integrated) via the connecting member, and always rotates or stops integrally (and coaxially).
  • the compound planetary gear mechanism 25C includes the first sun gear 21s of the first planetary gear 21, the third ring gear 23r of the third planetary gear 23, the first carrier 21c of the first planetary gear 21 and the third planetary gear that are always connected.
  • the third carrier 23c of the gear 23, the first ring gear 21r of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 that are always connected, have four rotating elements.
  • the compound planetary gear mechanism 25C is arranged such that the first pinion gear 21p and the third pinion gear at least partially overlap in the axial direction as viewed from the radial direction.
  • the third ring gear 23r of the compound planetary gear mechanism 25C is always connected to the second carrier 22c of the second planetary gear 22 via a connecting member, and is always rotated or coaxially with the second carrier 22c. Stop.
  • the clutch C1 includes the first carrier 21c of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23, and the fourth carrier 24c of the fourth planetary gear 24, which are always connected. Are connected to each other and the connection between the two is released.
  • the clutch C2 connects the first ring gear 21r of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 and the second sun gear 22s of the second planetary gear 22 that are always connected to each other, The connection between the two is canceled.
  • the first sun gear 21s is the first rotating element of the automatic transmission 20C
  • the third ring gear 23r is the second rotating element of the automatic transmission 20C
  • the first carrier 21c and the third carrier 23c are the third rotating elements of the automatic transmission 20C
  • the first ring gear 21r and the third sun gear 23s are the fourth rotating elements of the automatic transmission 20C.
  • the compound planetary gear mechanism 25C has a first rotation element, a second rotation element, a third rotation element, and a second rotation element of the automatic transmission 20C that are sequentially arranged at intervals corresponding to the gear ratios ⁇ 1 and ⁇ 3 on the velocity diagram. It has 4 rotating elements.
  • the fourth forward speed may be formed by engaging the clutches C1, C2 and the brake B2 instead of engaging the clutch C1 and the brakes B1 and B2.
  • the ninth forward speed may be formed by engaging the clutches C2, C3 and the brake B1, instead of engaging the clutches C3, C4 and the brake B1, In this case, the formation of the forward tenth speed may be omitted.
  • At least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch or a dog brake.
  • the clutch C3 that is engaged in the seventh forward speed to the tenth forward speed and the reverse speed may be a dog clutch, and the first forward speed to the fourth forward speed.
  • the brake B2 engaged at the stage and the reverse stage may be a dog brake.
  • the gear ratios ⁇ 1 to ⁇ 4 in the first to fourth planetary gears 21, 22, 23 or 23B, 24 are not limited to those exemplified in the above description.
  • At least one of the first, second, and fourth planetary gears 21, 22, and 24 may be a double pinion type planetary gear
  • the compound planetary gear mechanism 25 may be a Simpson type, for example, It may be replaced with another compound planetary gear mechanism such as Ravigneaux type.
  • the multi-stage transmission of the present disclosure is a multi-stage transmission that shifts the power transmitted to the input member and transmits the power to the output member.
  • the first, second, third and fourth rotating elements of the first, second, third and fourth planetary gears are connected to other rotating elements or stationary members, respectively, and the connection between them is released.
  • the first planetary gear and the third planetary gear are arranged in order corresponding to the gear ratio of the first and third planetary gears, the first rotation element, the second rotation element, the third rotation element, and the fourth Constructing a compound planetary gear mechanism having a rotating element
  • the second planetary gear has a fifth rotating element, a sixth rotating element, and a seventh rotating element arranged in order corresponding to the gear ratio
  • the fourth planetary gear has an eighth rotation element, a ninth rotation element, and a tenth rotation element arranged in order corresponding to the gear ratio
  • the sixth rotating element of the second planetary gear is always connected to the input member;
  • the ninth rotating element of the fourth planetary gear is always connected to the output member;
  • the first rotating element of the compound planetary gear mechanism and the eighth rotating element of the fourth planetary gear are always connected,
  • the second rotating element of the compound planetary gear mechanism and the sixth rotating element of the second planetary gear are always connected,
  • the first engaging element connects the third rotating element of the compound planetary gear mechanism and
  • the second engaging element connects the fourth rotating element of the compound planetary gear mechanism and the fifth rotating element of the second planetary gear to each other, and releases the connection between them.
  • the third engaging element connects the seventh rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear to each other, and releases the connection between them.
  • the fourth engaging element includes the first rotating element of the compound planetary gear mechanism, the eighth rotating element of the fourth planetary gear, and the seventh rotating element of the second planetary gear that are always connected.
  • the fifth engaging element connects the fifth rotating element of the second planetary gear to the stationary member and fixes the non-rotatable, and releases the connection between the two
  • the sixth engaging element is configured to connect the tenth rotating element of the fourth planetary gear to the stationary member so as to be non-rotatable and to release the connection therebetween.
  • the first, second, third, fourth, fifth and sixth engaging elements are selectively engaged with each other by first engaging them. It is possible to form a forward gear and a reverse gear from the first gear to the ninth gear or the tenth gear. As a result, the spread can be further increased, so that the speed ratio of the low speed stage is increased and the speed ratio of the high speed stage is further reduced to improve the fuel efficiency of the vehicle on which the multi-stage transmission is mounted, and to the driver That is, the acceleration performance of the vehicle can be further improved.
  • this multi-stage transmission when planetary gears including ring gears are used as the first, second, third, and fourth planetary gears, the forward travel from the first speed to the ninth speed or the tenth speed is performed. It is possible to prevent an increase in inertia during the rotation of the ring gear by preventing the ring gear having a particularly large diameter from rotating at a high rotational speed when forming the step and the reverse step. As a result, the time required for engaging the engaging element is shortened, the occurrence of shock at the time of shifting accompanied by the engagement of the engaging element is suppressed, and the durability of the friction material of the engaging element is improved. Can be secured. As a result, in the multi-stage transmission according to the present disclosure, it is possible to further improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of the vehicle in which the multi-stage transmission is mounted.
  • the forward speed and the reverse speed from the first speed to the tenth speed are formed by engaging the first to sixth engaging elements as follows. Can do. That is, the forward first speed is formed by engaging the second engagement element, the fourth engagement element, and the sixth engagement element.
  • the second forward speed is formed by engaging the fourth engagement element, the fifth engagement element, and the sixth engagement element.
  • the third forward speed is formed by engaging the second engagement element, the fifth engagement element, and the sixth engagement element.
  • the first engagement element, the fifth engagement element, and the sixth engagement element are engaged, or the first engagement element, the second engagement element, and the sixth engagement element are engaged. It is formed by combining.
  • the fifth forward speed is formed by engaging the first engagement element, the second engagement element, and the fifth engagement element.
  • the sixth forward speed is formed by engaging the first engagement element, the fourth engagement element, and the fifth engagement element.
  • the seventh forward speed is formed by engaging the first engagement element, the third engagement element, and the fourth engagement element.
  • the eighth forward speed is formed by engaging the first engagement element, the third engagement element, and the fifth engagement element.
  • the ninth forward speed is formed by engaging the third engagement element, the fourth engagement element, and the fifth engagement element.
  • the tenth forward speed is formed by engaging the second engagement element, the third engagement element, and the fifth engagement element.
  • the reverse gear is formed by engaging the second engagement element, the third engagement element, and the sixth engagement element.
  • the forward speed and the reverse speed from the first speed to the ninth speed are formed by engaging the first to sixth engaging elements as follows. Can do. That is, the forward first speed is formed by engaging the second engagement element, the fourth engagement element, and the sixth engagement element. The second forward speed is formed by engaging the fourth engagement element, the fifth engagement element, and the sixth engagement element. The third forward speed is formed by engaging the second engagement element, the fifth engagement element, and the sixth engagement element. In the fourth forward speed, the first engagement element, the fifth engagement element, and the sixth engagement element are engaged, or the first engagement element, the second engagement element, and the sixth engagement element are engaged. It is formed by combining.
  • the fifth forward speed is formed by engaging the first engagement element, the second engagement element, and the fifth engagement element.
  • the sixth forward speed is formed by engaging the first engagement element, the fourth engagement element, and the fifth engagement element.
  • the seventh forward speed is formed by engaging the first engagement element, the third engagement element, and the fourth engagement element.
  • the eighth forward speed is formed by engaging the first engagement element, the third engagement element, and the fifth engagement element.
  • the ninth forward speed is for engaging the engagement of the third engagement element, the fourth engagement element, and the fifth engagement element, or for the second engagement element, the third engagement element, and the fifth engagement. Formed by engaging elements.
  • the reverse gear is formed by engaging the second engagement element, the third engagement element, and the sixth engagement element.
  • any three of the first to sixth engaging elements are engaged and the remaining three are released to advance the first forward speed to the ninth forward speed.
  • the forward gear and the reverse gear up to the tenth speed are formed. Accordingly, for example, compared with a transmission that forms a plurality of shift stages by engaging two of the six engagement elements and releasing the remaining four, the release is performed with the formation of the shift stage.
  • the number of engaging elements can be reduced. As a result, drag loss in the engagement element released with the formation of the shift stage can be reduced, and the power transmission efficiency in the multi-stage transmission, that is, the fuel consumption of the vehicle can be further improved.
  • the second planetary gear includes a second sun gear, a second ring gear, and a second carrier that holds a plurality of second pinion gears that mesh with the second sun gear and the second ring gear, respectively, in a freely rotating and revolving manner.
  • the fourth planetary gear may include a fourth sun gear, a fourth ring gear, and a plurality of fourth pinion gears that mesh with the fourth sun gear and the fourth ring gear, respectively. It may be a single pinion planetary gear having a fourth carrier that is rotatably and revolved, the fifth rotating element may be the second sun gear, and the sixth rotating element is The second carrier may be used, the seventh rotating element may be the second ring gear, and the eighth rotating element may be the fourth sun gear. May even, the ninth rotary elements may be the fourth carrier, the tenth rotary element may be a fourth ring gear.
  • the meshing loss between the rotating elements in the second and fourth planetary gears is reduced, and the power transmission efficiency in the multi-stage transmission, that is, As well as improving the fuel efficiency of the vehicle, it is possible to further improve the assemblability while suppressing the weight increase of the multi-stage transmission by reducing the number of parts.
  • the compound planetary gear mechanism includes a first sun gear, a first ring gear, and a first carrier that holds a plurality of first pinion gears that mesh with the first sun gear and the first ring gear, respectively, so as to be rotatable and revolved.
  • a single pinion type first planetary gear having a third pinion gear, a third sun gear, a third ring gear, and a plurality of third pinion gears meshed with the third sun gear and the third ring gear, respectively, are rotatably and reciprocally held.
  • the third planetary gear of a single pinion type having a third carrier, the first rotating element may be the first sun gear, and the second rotating element is always connected.
  • the third carrier may be the first carrier and the third ring gear, and the third rotating element is connected to the first ring gear and the constantly connected first ring gear. It may be a fine third carrier, the fourth rotating element may be the third sun gear.
  • the compound planetary gear mechanism includes a first sun gear, a first ring gear, and a first carrier that rotatably and reciprocally holds a plurality of first pinion gears that mesh with the first sun gear and the first ring gear, respectively.
  • a single pinion type first planetary gear having a first pinion gear, a third sun gear, a third ring gear, and a pair of two pinion gears that mesh with each other and one meshes with the third sun gear and the other meshes with the third ring gear.
  • the third planetary gear of a double pinion type having a third carrier that holds a plurality of freely and revolving freely, the first rotating element may be the first sun gear,
  • the two rotation element may be the first carrier and the third carrier that are always connected, and the third rotation element is always connected May be a serial first ring gear and the third ring gear, the fourth rotating element may be the third sun gear.
  • the compound planetary gear mechanism includes a first sun gear, a first ring gear, and a first carrier that holds a plurality of first pinion gears that mesh with the first sun gear and the first ring gear, respectively, so as to be rotatable and revolved.
  • a single pinion type first planetary gear having a third pinion gear, a third sun gear, a third ring gear, and a plurality of third pinion gears meshed with the third sun gear and the third ring gear, respectively, are rotatably and reciprocally held.
  • the third rotating element may be the first carrier and the third carrier that are always connected, and the fourth rotation Elements may be constantly connected to said first ring gear and said third sun gear.
  • the first ring gear and the third sun gear may be integrated, and the compound planetary gear mechanism is configured such that the first pinion gear and the third pinion gear are at least partially in the axial direction as viewed from the radial direction. May be arranged so as to overlap each other.
  • the output member may be a counter drive gear included in a gear train that transmits power to a differential gear connected to a front wheel of the vehicle. That is, the multistage transmission of the present disclosure may be configured as a transmission that is mounted on a front-wheel drive vehicle.
  • the invention of the present disclosure can be used in the manufacturing industry of multi-stage transmissions.

Landscapes

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

Abstract

L'invention concerne une transmission automatique (20) comprenant un mécanisme d'engrenages planétaires (25) composé formé par combinaison d'un premier engrenage planétaire (21) à pignon unique et d'un troisième engrenage planétaire (23) à pignon unique; un deuxième engrenage planétaire (22) à pignon unique; un quatrième engrenage planétaire (24) à pignon unique; des embrayages (C1 à C4); et des freins (B1, B2). La mise en prise de trois embrayages quelconques parmi les embrayages (C1-C4) et des freins (B1, B2) permet la formation de neuf ou dix vitesses avant et d'une marche arrière.
PCT/JP2015/059694 2014-04-01 2015-03-27 Transmission multiétagée WO2015152067A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014075342 2014-04-01
JP2014-075342 2014-04-01

Publications (1)

Publication Number Publication Date
WO2015152067A1 true WO2015152067A1 (fr) 2015-10-08

Family

ID=54240392

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/059694 WO2015152067A1 (fr) 2014-04-01 2015-03-27 Transmission multiétagée

Country Status (1)

Country Link
WO (1) WO2015152067A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215393A (ja) * 2007-02-28 2008-09-18 Aisin Aw Co Ltd 自動変速機
US20100069195A1 (en) * 2008-09-15 2010-03-18 Reid Alan Baldwin Multiple Speed Transmission
US20100190600A1 (en) * 2009-01-26 2010-07-29 Gm Global Technology Operations, Inc. Multi-speed transmissions
US20110111914A1 (en) * 2009-11-06 2011-05-12 Gm Global Technology Operations, Inc. Transmission having at least eight speeds

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215393A (ja) * 2007-02-28 2008-09-18 Aisin Aw Co Ltd 自動変速機
US20100069195A1 (en) * 2008-09-15 2010-03-18 Reid Alan Baldwin Multiple Speed Transmission
US20100190600A1 (en) * 2009-01-26 2010-07-29 Gm Global Technology Operations, Inc. Multi-speed transmissions
US20110111914A1 (en) * 2009-11-06 2011-05-12 Gm Global Technology Operations, Inc. Transmission having at least eight speeds

Similar Documents

Publication Publication Date Title
JP6219145B2 (ja) 多段変速機
WO2015108028A1 (fr) Transmission à étages multiples
JP6183187B2 (ja) 多段変速機
WO2015108006A1 (fr) Transmission à plusieurs étages
JP6184365B2 (ja) 多段変速機
JP2015155719A (ja) 多段変速機
JP2015197207A (ja) 多段変速機
JP2015155721A (ja) 多段変速機
JP2015194196A (ja) 多段変速機
JP6191419B2 (ja) 多段変速機
JP2015194234A (ja) 多段変速機
JP6215138B2 (ja) 多段変速機
JP6215775B2 (ja) 多段変速機
WO2016175287A1 (fr) Dispositif de transmission
JP2015183793A (ja) 多段変速機
JP2015132332A (ja) 多段変速機
JP6215139B2 (ja) 多段変速機
JP6377825B2 (ja) 多段変速機
JP2015132327A (ja) 多段変速機
JP6184364B2 (ja) 多段変速機
WO2015156166A1 (fr) Transmission à rapports multiples
WO2018179598A1 (fr) Transmission à vitesses multiples
WO2015152067A1 (fr) Transmission multiétagée
JP6219234B2 (ja) 多段変速機
JP2015132326A (ja) 多段変速機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15772448

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15772448

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP